fjass / cTe^/ fV 
 
E. D. MEIER, THEO. C. MEIER, S. D. MERTON, 
 
 PRES'T AND CHIEF ENGINEER. V .- P. AN D T REAS. SECRETARY. 
 
 THE HEINE SAFETY 
 BOILER CO. 
 
 MANUFACTURERS OF 
 
 WATER TUBE STEAM BOILERS 
 
 FOR ALL 
 PRESSURES, DUTIES AND FUELS. 
 
 MAIN OFFICE: 
 
 ROOMS 703 TO 708 BANK OF COMMERCE BUILDING, NO. 421 OLIVE STREET, 
 
 ST. LOUIS, MO. 
 
 BRANCH OFFICES: 
 
 NEW YORK, N. Y., PHILADELPHIA, PA., CHICAGO, ILL., 
 
 120 LIBERTY ST. 669 THE BOURSE. 1521 MONADNOCK BLDG. 
 
 BOSTON, MASS., PITTSBURG, PA.. 
 
 104 EQUITABLE BLDG. 1212 CARNEGIE BLDG. 
 
 REPRESENTATIVES: 
 
 Denver, Colo., Montreal, can., san Francisco, Cal., 
 
 stearns-roger mfg. co. geo. brush, risdon iron and loco, works, 
 
 34 king st. howard and beal sts. 
 
 TORONTO, ONT., LOUISVILLE, KY., 
 
 CANADIAN R. M. CUNNINGHAM, 
 
 HEINE SAFETY BOILER CO. 612 COLUMBIA BLDG. 
 
 St. LOUIS, MO., AUGUST 1, 1897. 
 
 Shallcross-McCallum Co., St. Lours. 
 
Preface to Second Edition. 
 
 TN presenting to the engineering and steam-using world this second 
 and larger edition of "HELIOS," following so closely after the first 
 publication, we wish to express our warm appreciation of the many kind 
 expressions which the first volume has elicited. 
 
 The cordial reception given the first edition is in the nature of most 
 distinct and encouraging confirmation of our belief that, in the long run, the 
 best boiler that money can malce will find the greatest favor with the greatest 
 number of discriminating steam users. 
 
 We submit this second edition to the careful consideration of all who 
 are concerned with the subject of modern boiler practice. 
 
 ^o -*c^ 
 
 Preface to FoartI) Edition. 
 
 "55' 
 
 Y\/ ^ TAKE great pleasure in announcing our fourth edition. We have 
 added an article on "Bagasse" as a boiler fuel, and have entirely 
 rewritten and enlarged our article on "Chimneys and Draft." 
 
 We call attention also to seven new and valuable tables, published for 
 the first time in this edition. 
 
 HEINE SAFETY BOILER CO. 
 January i, 1895. 
 
 ^^> ^^ix 
 
 Preface to FiftI) Edition. 
 
 TN this edition we desire to call special attention to the revised table 
 of American Coals. The proximate analyses have been omitted, retain- 
 ing only the heat values and theoretical evaporative powers. The number 
 of tests of coals has been considerably increased. 
 
 The article on Fuel Oil has also been considerably enlarged. 
 
 July 4, 1896. 
 
 I'?'^9f07 
 
" I tliink ' HELIOS ' is immense." 
 
 J. J. DEKINDER, 
 
 Con. Eng. Pennsylvania R. R. Co. 
 
 "An invaluable addition to the literature of our profession." 
 
 JOHN L. D. BORTHWICK, 
 
 Chief Engineer U. S. N. 
 
 " ' HELIOS ' throws a brilliant light on many dark subjects." 
 
 JOHN E. CODMAN, C. E. & M. E. 
 
 Philadelphia Water Works. 
 
 It easily takes the lead, even in this age of magnificent catalogues." 
 
 EDWARD K. HILL, 
 
 Prest. Wheelock Engine Co. 
 
 " It is a most excellent hand-book, and contains much valuable information." 
 
 R. FORSYTH, 
 
 Eng. Illinois Steel Co. 
 
 '•' ' HELIOS,' the most complete book of its kind 1 have ever seen." 
 
 JOS. H. SPRINGER, 
 
 Gen'l Supt. Frazer & Chalmers. 
 
 " I consider ' HELIOS ' an excellent addition to my technical library." 
 
 D. ASHWORTH, 
 
 Consulting Engineer. 
 
 " It is altogether, to my mind, one of the best publications of its kind that has come 
 out." A. J. CALDWELL, 
 
 Hydraulic Engineer. 
 
 " It is very well arranged, has a good index, is remarkably free from errors, and is, 
 in fact, just such a book as every engineer should have at hand." 
 
 F. H. BAILEY, 
 
 Chief Engineer U. S. N. 
 
 " The data being the result of recent experiment and experience, furnishes a fund of 
 information not found in other text books, and is a valuable addition to mechanical litera- 
 ture." F. S. ALLEN, 
 
 Chief Inspector, Hartford Steam Boiler Insp. & Ins. Co. 
 
 " Your beautiful contribution to the technical literature of the day was on my desk 
 on my return from Chicago. It is one of the handsomest bits of its kind that has yet ap- 
 peared, and you are to be heartily congratulated on your success." 
 
 R. H. THURSTON, 
 
 Prof. Mech. Engr. Cornell University. 
 
HELIOS. 
 
 Source of All Power! Fountain of Light and Warmth II 
 
 Adored by the ancient husbandman as the God who blessed his 
 labors with a harvest of golden grain ; revered by the early sage as 
 the great visible means of the divine creative force ; pictured by the 
 inspired artist as the tireless charioteer who drives his four fiery 
 steeds daily across the heavens, his head circled by a crown of rays 
 his chariot wheel the disk of the sun itself. 
 
 When primeval man began to think, the sun seemed to him the 
 ■cause of all those wonders in nature which ministered to his simple 
 wants, or taught his soul to hope. His crude feelings of awe and 
 gratitude blossomed into worship, and we find the sun as central figure 
 in all early religions. He was the Suraya of the Hindoos, the Baal 
 of the Phoenicians, the Odin of the Norsemen, and his temples arose 
 alike in ancient Mexico and Peru. As Mithras of the Parsees, he was 
 adored as the symbol of the Supreme Deity, his messenger and agent 
 for all good. As Osiris he received the worship and offerings of the 
 Egyptians, whose priests, early adepts in the rudiments of science, 
 saw in him the cause of the annual fructifying overflow of the Nile. 
 
 Modern knowledge, with its vast array of facts and figures, can 
 but verify and seal the faith of these ancient observers. What they 
 dimly discerned as probable is now the central fact of physical science. 
 From him are derived all the forces of nature which have been yoked 
 into the service of man. All animal and plant life draws its daily 
 sustenance from the warmth and light of the sun, and it is but his 
 transmuted energy we expend, when, with muscle of man or horse, we 
 load our truck or roll it along the highway. Do we irrigate the soil 
 from the pumps of a myriad windmills ? His rays, on plains far inland, 
 supply the energy for the breeze which turns their vanes ! 
 
 Does a lumbering wheel drive a dozen stamps and a primitive 
 arastra in some Mexican canyon ? Do mighty turbines whirl a million 
 flying spindles and shake thousands of clattering looms on the banks 
 of some New England stream ? From the bosom of the ocean and the 
 swamps of the tropics, Helios lifted those vapory Titans whose lifeblood 
 courses in the mountain torrent and the river of the plain ! 
 
 ~1 — 
 
Do a hundred cars rattle up the steep streets or the smiling city 
 by the Golden Gate ? Are massive ingots of steel forged to shape 
 and size by the giant hammers of Bethlehem ? The fuel which 
 gives them motion was stored for us, ages before man was evolved, 
 by the rays which flash from his chariot wheels ! "The heat now 
 radiating from our fire places has at some time previously been trans- 
 mitted to the earth from the sun. If it be wood that we are burning, 
 then we are using the sunbeams that have shone on the earth within 
 a few decades. If it be coal, then we are transforming to heat the 
 solar energy which arrived at the earth millions of years ago." 
 
 Professor Langley remarks that "the great coal fields of Pennsyl- 
 vania contain enough of the precious mineral to supply the wants of 
 the United States for a thousand years. If all that tremendous 
 accumulation of fuel were to be extracted and burned in one vast 
 conflagration, the total quantity of heat that would be produced would, 
 no doubt, be stupendous, and yet," says this authority, who has taught 
 us so much about the sun, "all the heat developed by that terrific 
 coal fire would not be equal to that which the sun pours forth in 
 the thousandth part of each single second." 
 
 The almost limitless stores of petroleum which are found in 
 America and in Asia, and the smaller, though still vast supplies of 
 natural gas which some favored localities are now exploiting, represent 
 but so much sun-energy transmuted through forests of prehistoric 
 vegetation. 
 
 Another authority tells us that the total amount of living force 
 "which the sun pours out yearly upon every acre of the earth's 
 surface, chiefly in the form of heat is 800,000 horse-power." And 
 he estimates that a flourishing crop utilizes only j\ of 1 per cent of 
 this power. 
 
 Remembering, then, that this sun-energy reaches us only one-half 
 of each day, we may, whenever we learn how, pick up on every acre 
 an average of 175 horse-power during each hour of daylight, as a 
 surplus which nature does not require for her work of food production. 
 
 Attempts to utilize this daily waste have been made, and future 
 inventors may fire their boilers directly with the radiant heat of the 
 sun. But whether we depend on what he garnered for us ages ago, 
 or quite recently, or on the stores he will lavish on us in the future, 
 it is clear that man's continued existence on earth is directly dependent 
 on Helios, 
 
 In olden times the various trades or guilds chose as their patron 
 saint some prominent person who was thought to have embodied in 
 his life-work the special means and m.ethods of their craft. By that 
 
token we claim Helios as our own. He has always carried the record 
 for evaporative efficiency. He provides hoth the fuel and the water 
 for our boilers. He teaches us perfect circulation, upward as mingled 
 vapor and water by the action of heat, and down again by gravity 
 as rain and river in solid water. It is therefore fit tliat the boiler in 
 which this perfect and unobstructed circulation is made the leading 
 feature of construction should have HELIOS as its emblem ! 
 
 In the following pages we give some account of the fuels used 
 in the practical arts, of the water which becomes the vehicle for 
 transmitting their energy into mechanical power, and of the limitations 
 imposed by their varying conditions. These must all be taken into 
 account in estimating how much we may expect of certain combina- 
 tions of machinery. Much of the text and many of the tables are 
 taken from Mr. David Kinnear Clark's admirable book on the steam 
 engine, for which his consent and that of his publishers, Messrs. 
 Blackie & Son, was courteously given. We also, by permission, 
 quote freely from such authorities as Mr. Emerson McMillin, Prof. Wm. 
 B. Potter, Prof. R. H. Thurston, Mr. J. M. Whitham, Prof. D. S. 
 Jacobus, Prof. Ordway and others. Thanks are also due for valuable 
 matter to Messrs. Henry R. Worthington, The B. F. Sturtevant Co., 
 Mr. Alfred R. Wolff, Mr. C. W. Owston and Messrs. Hunt & Clapp. 
 In most instances we indicate the scource by initials. 
 
 We trust that the tables and data may be found convenient for 
 ready reference alike by professional men, by manufacturers, and by 
 that growing class of practical steam engineers who realize that true 
 theory, consonant with collective experience, is within the reach of 
 every thoughtful man who pulls the throttle. 
 
 E. D. M. 
 
HEAT. 
 
 Heat is the form in which we receive most of the sun-energy. In the 
 various fuels it exists in a potential form requiring combustion, /. <?. , combi- 
 nation of the active elements of the fuel with the oxygen of the air, to 
 reappear in its active form. 
 
 "Heat as a Form of Energy is subject to the general laws which gov- 
 ern every form of energy and control all matter in motion, whether that 
 motion be molecular or the movement of masses. 
 
 "That heat is the motion of the molecules of bodies was first shown by 
 experiment by Benjamin Thompson, Count Rumford, then in the service of 
 the Bavarian Government, who in 1798 presented a paper to the Royal 
 Society of Great Britain, describing his work, and reciting the results and 
 his conclusion that heat is not substance, but a form of energy. 
 
 "This paper is of very great historical interest, as the now accepted 
 doctrine of the persistence of energy is a generalization which arose out of a 
 series of investigations, the most important of which are those which resulted 
 in the determination of the existence of a definite quantivalent relation be- 
 tween these two forms of energy and a measurement of its value, now known 
 as the 'mechanical equivalent of heat.' The experiment consisted in the de- 
 termination of the quantity of heat produced by the boring of a cannon at the 
 arsenal at Munich." 
 
 Work in the same direction was done by Sir Humphrey Davy, Sadi 
 Carnot, Dr. Mayer and Mr. Colding. But Dr. Joule, from 1843 to 1849, 
 made a series of experiments by various methods, the results of which 
 have been generally accepted as satisfactory. 
 
 Quantities of heat are measured, in English units, by what is termed 
 the British Thermal Unit, or for brevity, B. T. U. The B. T. U. is the 
 quantity of heat required to raise 1 lb. of pure water from a temperature of 
 62° F. to 63° F., and has an equivalent in mechanical units of work. This is 
 frequently called simply a Heat Unit or designated by H. U. 
 
 The mechanical unit of work is the foot-found^ or the work required 
 to raise 1 pound, 1 foot high. Joule's experiments, and those of later investi- 
 gators, show 778 ft. lbs. to be equivalent to one B. T. U. This number, 
 778, is known as Joule's equivalent or symbolically J. 33000 ft. lbs. per 
 min. was called a horse power by Watt, and is used as such to-day, it being 
 the unit for large powers. 
 
 The electrical unit of power is the Watt, which is the product of 1 ampere 
 XI volt. 746 Watts are equivalent to IH. P. or 33000 ft. lbs. HencetheWatt 
 has an equivalent in heat units also. 
 
 Water power is measured in terms of the height of fall or velocity of flow, 
 and the quantity or weight of water passing, the result, however, being in 
 mechanical units. Hence P=HxWxV, where P = ft. lbs. per sec, H== 
 height of fall in ft., W= weight per cu. ft. of water, V= cubic feet of 
 water falling per second. 
 
Since V^ == 2 gH. we have P = f^ x V X W where P, V, and W, are the 
 same as before and v the velocity of flow of the water in ft. per sec. and 
 g=32.2. 
 
 Owing to the frictional losses and the inefficiency of all kinds of water 
 motors, more than 80 per cent, of this theoretical power is rarely ever realized. 
 The best types of water motors give only 80 to 90 per cent, efficiency. 
 
 The following table shows the relation of the various units t 
 
 Table No. l. 
 Equivalents of Work and Heat. 
 
 B. T. Ll. Ft. lbs. Watts. 
 
 1 = 778 == 17.59 
 
 42.41 = 33000 = 746 =1 H. P. 
 
 In the French or metric system of units, a Heat Unit or Calorie is the 
 quantity of heat required to raise 1 Kilogram of pure water 1° Cent, at or 
 about 4° C. 
 
 The following tabular statement shows the relation of the French and 
 English units : 
 
 Table No. 2. 
 
 French and English Units Compared. 
 
 1 Calorie 3.968 B. T. U. 
 
 0.252 Calorie 1 B. T. U. 
 
 French Mechanical Equivalent, ) g^^, ., ,. 
 
 425.0 Kilogram-metres, ) 
 
 107.7 Kilogram-metres J, or 778 ft. lbs. 
 
 For convenience in translating French or German results in to English 
 or American we have the following compound units : 
 
 Table No. 3. 
 Equivalent Compound Units. 
 
 1 Calorie per square metre 0.369 B. T. U. p. square ft. 
 
 1 B. T. U. or 1 H. U. p. square ft 2.713 Cal. p. square metre. 
 
 1 Calorie p. Kilogram 1.800 H. U. per pound. 
 
 1 H. U. p. pound 0.556 Cal. p. Kilogram. 
 
 "Heat Transformations may take place, through the action of physi- 
 cal and chemical forces, into any other known form of energy, and another 
 form of energy may be transmuted into heat. Nearly all physical pheno- 
 mena, in fact, involve heat-transformation in one form or another, and in a 
 greater or less degree, under the laws of energetics. According to the first 
 of those laws, such changes must always occur by a definite quantivalence, 
 and when heat disappears in known quantity it is always certain that 
 energy of calculable amount will appear as its equivalent ; the reverse is as 
 invariably the case when heat is produced ; it always represents and meas- 
 ures an equivalent amount of mechanical, electrical, chemical, or other 
 energy. 
 
 - 6 - 
 
"Heat and Mechanical Energy are thus evidently subject to the general 
 laws of transformation of energy, and the transmutation of the one into the 
 other must always be capable of treatment mathematically. The relations 
 of these two forms of energy are taken as the subject of a division of ener- 
 getics known as the science of thermodynamics, and a vast amount of 
 study and research has been given by the ablest mathematical physicists of 
 modern times to the investigation of its laws and their applications, and to 
 the building up of that science. 
 
 "The conversion of water into steam in the steam boiler and the utiliza- 
 tion of the heat-energy thus made available, or in heated air and other 
 gases, in steam or other heat-engines, constitute at once the most familiar 
 and the most important of known illustrations of thermodynamic phenomena 
 and their useful application. The process of making steam is one of pro- 
 duction of heat by transformation from the potential form of energy through 
 the action of chemical forces, and its storage in sensible form for later use 
 in the steam-engine, where it is changed into equivalent mechanical energy. 
 The pure science of the steam-engine is thus the science of thermodynamics, 
 the first applications of which are made in the operations carried on in the 
 steam-boiler. 
 
 "Sensible and Latent Heats must be carefully distinguished in study- 
 ing the action of heat on matter. The term 'Sensible Heat' scarcely re- 
 quires definition ; but it may be said that sensible and latent heats represent 
 latent and sensible work ; that the former is actual, kinetic, heat-energy, 
 capable of transformation into mechanical energy, or vis viva of masses, 
 and into mechanical work ; while the latter form is not heat, but is the 
 equivalent of heat transformed to produce a visible effect in the performance 
 of molecular, or internal as well as external, work, and visible alteration of 
 volume and other physical conditions. 
 
 "It is seen that heat may become 'latent' through any transformation 
 which results in a definite and defined physical change, produced by expan- 
 sion of any substance in consequence of such transmutation into internal and 
 external work ; whether it be simple increase of volume or such increase 
 with change of physical state. 
 
 "The Latent Heat of Expansion is a name for that heat which is 
 demanded to produce an increase of volume, as distinguished from that un- 
 transformed heat which is absorbed by the substance to produce elevation of 
 temperature. The latent heat of expansion may, by its absorption and 
 transformation, and the resulting performance of internal and external work, 
 cause no other effect than change of volume, as e. g., when air is heated , 
 or it may at the same time produce an alteration of the solid to the fluid, or 
 of the liquid to the vaporous state, as in the melting of ice or the boiling of 
 water, in which latter cases, as it happens, no elevation of temperature 
 occurs, all heat received being at once transformed. In the expansion of 
 air, and in other cases in which no such change of state occurs, a part of 
 the heat absorbed remains unchanged, producing elevation of temperature ; 
 while aftother part is transformed into latent heat of expansion." 
 
 R. H. T. 
 
 — 7 — 
 
We give below tables of the boiling and melting points of various 
 substances, and the linear expansion of various solids. 
 
 Table No. 4. 
 Boiling Points of Various Substances. 
 
 At Atmospheric Pressure at Sea Level. 
 
 SUBSTANCE. 
 
 Alcohol 
 
 -Ammonia 
 
 Benzine 
 
 Coal Tar 
 
 Linseed Oil 
 
 Mercury 
 
 Naptha 
 
 Nitric Acid, s. g. 1.42 
 Nitric Acid, s. g. 1.5_ 
 Petroleum Rectified — 
 
 Degrees 
 Fahr. 
 
 173 
 
 140 
 176 
 325 
 597 
 648 
 186 
 248 
 210 
 316 
 
 SUBSTANCE. 
 
 Sulphur 
 
 Sulphuric Acid, s. g. 1.848 
 Sulphuric Acid, s. g. 1.3-- 
 
 Sulphuric Ether 
 
 Turpentine 
 
 Water 
 
 Water, Sea 
 
 Water, Saturated Brine 
 
 Wood Spirit 
 
 Degrees 
 Fahr. 
 
 570 
 590 
 
 240 
 
 100 
 
 315 
 
 212 
 
 213.2: 
 
 226 
 
 150 
 
 Table No. 5. 
 
 Melting Points of Metals. 
 
 From D. K. C. 
 
 METAL. 
 
 Aluminum 
 
 Antimony 
 
 Bismuth 
 
 Bronze 
 
 Copper 
 
 Gold, Standard — 
 
 Gold, Pure 
 
 Iron, Cast, Gray- 
 Iron, Cast, White 
 
 Iron, Wrought 
 
 Lead 
 
 Mercury 
 
 Silver 
 
 Steel 
 
 Tin 
 
 Zinc 
 
 Degrees 
 Fahr. 
 
 Full Red 
 Heat. 
 
 1150 
 507 
 
 1690 
 1996 
 2156 
 
 2282 
 2012 
 rl922 
 < to 
 
 12012 
 
 2912 
 
 617 
 
 —39 
 
 1873 
 
 r2372 
 
 to 
 
 2552 
 442 
 
 773 
 
 i 
 
 Melting Points of Various Solids. 
 
 From D. K. C. and H. 
 
 SUBSTANCE. 
 
 Carbonic Acid. 
 
 Glass 
 
 Ice 
 
 Lard 
 
 Nitro-Glycerine 
 
 Phosphorus 
 
 Pitch 
 
 Saltpetre 
 
 Spermaceti 
 
 Stearine 
 
 Sulphu,- _ 
 
 Tallow 
 
 Turpentine 
 
 Wax, Rough--- 
 Wax, Bleached 
 
 Degree^ 
 Fahr. 
 
 —108 
 
 2377 
 
 32 
 
 95 
 
 45 
 
 112 
 
 91 
 
 606 
 
 120' 
 
 rl09 
 
 i to 
 
 1 120' 
 
 239- 
 
 92 
 
 14 
 
 142- 
 
 154 
 
 Melting Points of Fusible Plugs. 
 
 From D. K. C. 
 
 2 Tin, 2 Lead. 
 2 Tin, 6 Lead. 
 
 Softens at , Melts ,.at 
 
 365 
 372 
 
 372 
 
 383 
 
 2 Tin, 7 Lead. 
 2 Tin, 8 Lead. 
 
 Softens at Melts at 
 
 377J 
 395^ 
 
 388 
 408 
 
 - -8- 
 
Table No. 6. 
 
 Expansion of Solids at Ordinary Temperatures. 
 
 D. K. c. 
 
 SUBSTANCE. 
 
 Aluminum (Cast) 
 
 Antimony (Crystallized) 
 
 Brass (Cast) 
 
 Brass (English Plate) 
 
 Brass (Sheet) 
 
 Brick (Best Stock) 
 
 Brick in Cement Mortar (Headers) 
 Brick in Cement Mortar (Stretchers) 
 
 Bronze 
 
 Cement (Roman, Dry) 
 
 Cement (Portland, Neat) 
 
 Cement (Portland, with Sand)--- 
 
 Copper 
 
 Glass (Flint) 
 
 Glass (White, Free from Lead)-- 
 
 Glass (Blown) 
 
 Glass (Thermometer) 
 
 Glass (Hard) 
 
 Granite (Gray, Dry) 
 
 Granite (Red, Dry) 
 
 Gold (Pure) 
 
 Iron (Wrought) 
 
 Iron (Swedish) 
 
 Iron (Cast) 
 
 Iron (Soft) 
 
 Lead 
 
 Marble (Ordinary, Dry) 
 
 Marble (Ordinary, Moist) 
 
 Mercury (Cubic Expansion) 
 
 Nickel 
 
 Plaster (White) 
 
 Platinum 
 
 Silver (Pure) 
 
 Slate 
 
 Steel (Cast) 
 
 Steel (Tempered) 
 
 Stone (Sand, Dry) 
 
 Tin 
 
 Wood (Pine) 
 
 Zinc 
 
 Zinc 8, Tin 1 
 
 Coefficient 
 
 Total Expansion between 
 
 32° Fahr. an 
 
 d 212" Fahr. 
 
 for 
 
 Coeff 
 
 cient. 
 
 In Length of 10 Feet. 
 
 1" Fahr. 
 
 Decimal. 
 
 Fraction. 
 
 
 
 
 Feet. 
 
 Inches. 
 
 .00001234 
 
 .002221 
 
 V450 
 
 .02221 
 
 .2664 
 
 .00000627 
 
 .001129 
 
 Vssa 
 
 .01129 
 
 .1336 
 
 .00000957 
 
 .001723 
 
 Vssi 
 
 .01723 
 
 .2067 
 
 .00001052 
 
 .001894 
 
 V529 
 
 .01894 
 
 .2273 
 
 .00001040 
 
 .001872 
 
 V535 
 
 .01872 
 
 .2246 
 
 .00000306 
 
 .000550 
 
 ^/l818 
 
 .00550 
 
 .0660 
 
 .00000494 
 
 .000890 
 
 Vn23 
 
 .00890 
 
 .1068 
 
 .00000256 
 
 .000460 
 
 V2174 
 
 .00460 
 
 .0552 
 
 .00000975 
 
 .001755 
 
 V568 
 
 .01755 
 
 .210ft 
 
 .00000797 
 
 .001435 
 
 V694 
 
 .01435 
 
 .1722 
 
 .00000594 
 
 .001070 
 
 V935 
 
 .01070 
 
 .1284 
 
 .00000656 
 
 .001180 
 
 V847 
 
 .01180 
 
 .1416 
 
 .00000887 
 
 .001596 
 
 1/625 
 
 .01596 
 
 .1915 
 
 .00000451 
 
 .000812 
 
 V1234 
 
 .00812 
 
 .0974 
 
 .00000492 
 
 .000886 
 
 Vll30 
 
 .00886 
 
 .1063 
 
 .00000498 
 
 .000896 
 
 Villi 
 
 .00896 
 
 .1075 
 
 .00000499 
 
 .000897 
 
 Vim 
 
 .00897 
 
 .1076 
 
 .00000397 
 
 .000714 
 
 Vl400 
 
 .00714 
 
 .0857 
 
 .00000438 
 
 .000789 
 
 1/1266 
 
 .00789 
 
 .0947 
 
 .00000498 
 
 .000897 
 
 Vim 
 
 .00897 
 
 .1076 
 
 .00000786 
 
 .001415 
 
 V707 
 
 .01415 
 
 .1698 
 
 .00000648 
 
 .001166 
 
 1/866 
 
 .01166 
 
 .1399 
 
 .00000636 
 
 .001145 
 
 1/873 
 
 .01145 
 
 .1374 
 
 .00000556 
 
 .001001 
 
 1/1000 
 
 .01001 
 
 .1201 
 
 .OOC 00626 
 
 .001126 
 
 1/897 
 
 .01126 
 
 .1351 
 
 .00001571 
 
 .002828 
 
 1/353 
 
 .02828 
 
 .3394 
 
 .00000363 
 
 .000654 
 
 l/l5S0 
 
 .00654 
 
 .0785 
 
 .00000663 
 
 .001193 
 
 1/838 
 
 .01193 
 
 .1432 
 
 .00009984 
 
 .017971 
 
 1/56 
 
 .17971 
 
 2.1565 
 
 .00000695 
 
 .001251 
 
 1/800 
 
 .01251 
 
 .1501 
 
 .00000922 
 
 .001660 
 
 1/602 
 
 .01660 
 
 .1992 
 
 .00000479 
 
 .000863 
 
 1/1159 
 
 .00863 
 
 .1036 
 
 .00001079 
 
 .001943 
 
 1/5U 
 
 .01943 
 
 .2334 
 
 .00000577 
 
 .001038 
 
 1/967 
 
 .01038 
 
 .1246 
 
 .00000636 
 
 .001144 
 
 1/874 
 
 .01144 
 
 .1373 
 
 .00000689 
 
 .001240 
 
 1/806 
 
 .01240 
 
 .1488 
 
 .00000652 
 
 .001174 
 
 1/852 
 
 .01174 
 
 .1409 
 
 .00001163 
 
 .002094 
 
 1/477 
 
 .02094 
 
 .2513 
 
 .00000276 
 
 .000496 
 
 I/2OI6 
 
 .00496 
 
 .0595 
 
 .00001407 
 
 .002532 
 
 1/395 
 
 .02532 
 
 .3038 
 
 .00001496 
 
 .002692 
 
 1/372 
 
 .02692 
 
 .3230 
 
 — 10 — 
 
an 
 
 The Specific Heat of a body signifies its capacity for heat or the quan- 
 tity of heat required to raise the temperature of tlie body one decree 
 Fahrenheit, compared witli tliat required to raise the temperature of 
 equal weiglit of water one degree. 
 
 TABLE No. 7. 
 
 Specific Heats. 
 
 D. K. C. 
 
 SUBSTANCE. 
 
 Ice 
 
 Water at 32° F 
 
 Gaseous Steam 
 
 Saturated Steam.. 
 
 Mercury 
 
 Sulphuric Ether, 
 
 Density .715 
 
 Alcohol 
 
 Lead 
 
 Gold 
 
 Tin 
 
 Silver 
 
 Brass 
 
 Copper 
 
 Zinc 
 
 Nickel 
 
 Wrought Iron 
 
 Steel 
 
 Cast Iron 
 
 Brickwork and Ma 
 
 sonry 
 
 Coal 
 
 SPECIFIC HEAT. 
 
 0.504 
 1.000 
 0.475 
 0.305 
 0.0333 
 
 0.5200 
 
 0.6588 
 
 0.0314 
 
 0.0324 
 
 0.0566 
 
 0.0570 
 
 0.0939 
 
 0.0951 
 
 0.0956 
 
 0.1086 
 0.1138 to 0.1255 
 0.1165 to 0.1185 
 
 0.1298 
 
 0.200 
 0.2411 
 
 SUBSTANCE. 
 
 Anthracite 
 
 Oak Wood 
 
 Fir Wood 
 
 Oxygen (Equal 
 Weights; Con- 
 stant Volume) 
 
 Air ( at Constant 
 Pressure) 
 
 Air (Equal Weights 
 Constant Vol.) 
 
 Nitrogen (Equal 
 Wgts ; Constant 
 Volume) 
 
 Hydrogen (Equal 
 Wgts ; Constant 
 Volume) 
 
 Carbonic Oxide 
 (Equal Weights; 
 Constant Vol.) .. 
 
 Carbonic Acid 
 (Equal Weights; 
 Constant Vol.) .. 
 
 SPECIFIC HEAT. 
 
 0.2017 
 
 0.570 
 
 0.650 
 
 0.1559 
 0.2377 
 0.1688 
 
 0.1740 
 
 2.4096 
 
 0.1768 
 
 0.1714 
 
 Boiler Plant of Lannett Cotton Mills, 
 
 WEST POINT, GA. 
 
 900 H. P. Heine Boilers. 
 
 11 — 
 
COMBUSTION. 
 
 Combustion or Burning is the chemical combination of the constituents 
 of the fuel, mostly carbon and hydrogen, with the oxygen of the air. The 
 nitrogen remains inert and causes loss of useful effect to the extent of the 
 heat it carries off through the chimney. 
 
 The hydrogen combines with enough oxygen to form water which 
 passes off as steam. 
 
 The carbon combines with enough oxygen to form carbonic acid or car- 
 bon dioxide gas (perfect combustion) or with only enough to form carbonic 
 oxide or carbon monoxide gas (imperfect combustion). 
 
 The following table gives the quantities of air, the heat evolved and the 
 resulting temperature from the combustion of constituent parts of fuel, under 
 the supposition that the chemical requirements are exactly fulfilled : 
 
 TABLE No. 8. 
 
 Combustion Data. 
 
 O. H. L. 
 
 Conditions for the Complete Combustion of Fuel in Furnaces. 
 
 For insuring completeness of combustion, the first condition is a sufficient 
 supply of air ; the next is that the air and the fuel, solid and gaseous, should 
 be thoroughly mixed ; and the third is that the elements — air and combusti- 
 ble gases — should be brought together and maintained at a sufficiently high 
 temperature. The hotter the elements the greater is the facility for good 
 combustion. 
 
 Rule 1. To find the quantity of air atQI" F., urider one atmosphere, 
 chemically coiisumed in the complete combustion of one pound of fuel of a given 
 composition. Let the constituent carbon, hydrogen, and oxygen be expressed 
 as percentages of the total weight of the fuel. To the carbon add three 
 times the hydrogen, and from the sum deduct four-tenths of the oxygen. 
 Multiply the remainder by 1.52. The product is the quantity of air at 62° F. 
 in cubic feet. 
 
 Formula:— A == 1.52(C + 3 H — .40) (1) 
 — 13 — 
 
To find the weight of the air chemically consumed, divide the volume 
 found as above by 13.14 ; the quotient is the weight of the air in pounds. 
 
 Rule 2. To find the total weight of the gaseous products of the complete 
 combustion of one poti7id of a fuel, multiply the percentage of constitutent 
 carbon in the fuel by 0.126, and that of hydrogen by 0.358. The sum of 
 these products is the total weight of the gases in pounds. 
 
 Formula:— W = 0.126 C + 0.358 H (2) 
 
 Rule 3. To find the total volume, at 62° F. , of the gaseous products of 
 the complete combustio7i of one pound of fuel , multiply the constituent percent- 
 age of carbon in the fuel by 1.52, and that of hydrogen by 5.52. The sum 
 of these products is the total volume in cubic feet. 
 
 Formula:— V = 1.52 C + 5.52 H (3) 
 
 The corresponding volume of the gases at other temperatures is given 
 by the formula — 
 
 V=V^- (4) 
 
 In which V is the volume at 62° F., t' is the other temperature and V the 
 corresponding volume. That is to say, the volume at any other temperature 
 t' is found by multiplying the volume at 62° by (f plus 461), and dividing 
 by 523. 
 
 Rule 4. To find approximately the total heating power of one pou7id of 
 a combustible, of which the percentages of the co7istituent carbon and hydrogeji 
 are given. To the carbon add 4.28 times the hydrogen, and multiply the 
 sum by 145. The product is the heating power in British units. 
 
 Formula:— h = 145 (C -^ 4.28 H) (5) 
 
 Rule 5. To find the total evaporative power, at1Yl° F., of one pound 
 of combustible, of which the percentages of the coiistituent carbon and hydro- 
 gen are given. To the carbon add 4.28 times the hydrogen, and multiply 
 the sum by 0.13 when the water is supplied at 62° F., or by 0.15 when the 
 water is supplied at 212° F, The product is the total evaporative power of 
 one pound of the combustible, in pounds of water evaporated at 212° F. 
 
 Formula :— (Water supplied at 212°), E = 0.15 (C + 4.28 H) (6) 
 
 in most cases an additional or surplus quantity of air is required to 
 facilitate the completion of the combustion of fuel beyond that which is 
 chemically consumed; but the proportio7i of surpbis air required appears to 
 dim,inish as the rate of combustion and the general tcTuperature in the furnace 
 are increased. For instance, for the most perfectly managed furnaces of 
 boilers in Cornwall, Mr. Hunt found that there was as much free oxygen in 
 the gaseous products in the chimney as was chemically consumed in combus- 
 tion. Again, Messrs. Delabeche and Playfair found that the surplus oxygen 
 varied from a fourth to a half ; and from the statements of Mr. Longridge 
 with regard to experimental trials at Newcastle with Hartley coal, it appears 
 that the surplus air amounted to only 9 per cent. These proportional surplus 
 
quantities, observed under very different circumstances, are found to diminish 
 as the rates of combustion increase, thus : 
 
 Coal Consumed per Square Foot 
 
 of Grate per Hour. Surplus Air. 
 
 Cornish Boilers 2 lbs. to 4 lbs 100 per cent. 
 
 Delabeche and Playfair-.IO lbs. to 1(> lbs 25 to 50 per cent. 
 
 Longridge 20 lbs. and upwards-- 9^4 per cent. 
 
 These results are roughly indicative of the law of the e.xcess of air. In 
 the instance of Hartley coal, above quoted, on the authority of Mr. Longridge, 
 the composition of the sample under trial was as follows: 
 
 Carbon 81.5 per cent. 
 
 Hydrogen 5.2 per cent. 
 
 Nitrogen 1.5 per cent. 
 
 Oxygen 6.2 per cent. 
 
 Sulphur 1.1 per cent. 
 
 Ash 4.5 per cent. 
 
 100.0 
 The quantity of air chemically consumed in the combustion of one pound 
 
 of this fuel by formula (1), is 144 cubic feet at 62°, The actual quantity of 
 air that was admitted below and about the fire was, according to Mr. Long- 
 ridge, 158 cubic feet, being 14 cubic feet, or 9f per cent, in excess, when 
 smoke was entirely prevented. He mentions, at the same time, that with the 
 ordinary system of stoking, when dense smoke was given off, the quantity 
 of air that passed through the furnace, exclusively through the grate, was 
 only at the rate of 100 cubic feet per pound of coal. This was little more 
 than equal to what was sufficient to burn the fixed portion of the coal. 
 
 Below we give a table giving the conditions and results of perfect com- 
 bustion for the fuels in common use. 
 
 As this table is from English sources the heat of combustion and equiva- 
 lent evaporative power of the coal is much higher than our American coals 
 warrant, as the tables of American coals, p. 20 will show. In applying the 
 table to practical cases, the surplus air which reduces the efficiency must 
 be taken into account. It is good practice to get in actual evaporation 60 per 
 cent, of the theoretical evaporative power for the poorer, and 70 per cent. 
 
 for the better kinds of coal : 
 
 Table No. 9. 
 
 Total Heat Evolved by Various Fuels and their Equivalent 
 
 Evaporative Power, with the Weight of Oxygen and 
 
 Volume of Air Chemically Consumed. 
 
 D. K. C. 
 
 Fuel, 
 
 Making Car- 
 bonic Acid. 
 
 Hydrogen -- 
 Carbon--- 1 
 
 Sulphur 
 
 Coal, average dessicated- 
 Coke, " 
 
 Lignite, perfect 
 
 Asphalt 
 
 Wood, dessicated 
 
 ' ' 25 pe" cent, moisture 
 Straw, 15^< per ct. moist. 
 
 Petroleum 
 
 Petroleum Oils 
 
 Weight of 
 Oxygen Con- 
 sumed per lb. 
 of Fuel. 
 
 Quantity of Air 
 
 Consumed per lb. 
 
 of Fuel. 
 
 Lbs. 
 
 8.0 
 
 2.66 
 
 1.00 
 2.45 
 2.49 
 2.04 
 2.74 
 1.40 
 1.05 
 0.98 
 3.29 
 4.12 
 
 Lbs. 
 
 34.8 
 
 11.6 
 
 4.35 
 
 10.7 
 
 10.81 
 
 8.85 
 
 11.85 
 
 6.09 
 
 4.57 
 
 4.26 
 
 14.33 
 
 17.93 
 
 Cu. ft. at 62°. 
 
 457 
 
 152 
 
 57 
 
 140 
 
 142 
 
 116 
 
 156 
 
 80 
 
 60 
 
 56 
 
 188 
 
 235 
 
 Total Heat of 
 
 Combustion 
 
 of 1 lb. of Fuel. 
 
 B.T. U. 
 
 62000 
 
 14500 
 
 4000 
 14700 
 13548 
 13108 
 17040 
 10974 
 7951 
 8144 
 20411 
 27531 
 
 Equivalent 
 
 Evaporative 
 
 Power of 1 lb. of 
 
 Fuel from and 
 
 at 212°. 
 
 Lbs. 
 
 62.40 
 
 15.0 
 
 4.17 
 15.22 
 14.02 
 13.57 
 17.64 
 11.36 
 8.20 
 8.43 
 21.13 
 28.50 
 
 — 15 
 
For average Amerkan coals the following table gives good approximate 
 results for the temperature and volume of gases, in the furnace, under the 
 varying conditions of practice. In applying it the actual quantities of air 
 used should be measured by an anemometer : 
 
 Table No. lO. 
 
 Temperature of Combustion and Volumes of Products. 
 
 J. M. w. 
 
 Temperature of 
 
 Supply of Air in lbs. per lb. of Fuel. 
 
 
 
 
 Gas, 
 
 12 lbs. 
 
 18 lbs. 
 
 24 lbs. 
 
 Fahrenheit. 
 
 
 
 
 
 Volume of Air 
 
 3r Gases in Cubic Feet at Each Temperature. 
 
 32 
 
 150 
 
 225 
 
 300 
 
 68 
 
 161 
 
 241 
 
 322 
 
 104 
 
 172 
 
 258 
 
 344 
 
 212 
 
 205 
 
 307 
 
 409 
 
 392 
 
 259 
 
 389 
 
 519 
 
 572 
 
 314 
 
 471 
 
 628 
 
 752 
 
 369 
 
 553 
 
 738 
 
 1112 
 
 479 
 
 718 
 
 957 
 
 1472 
 
 588 
 
 882 
 
 1176 
 
 1832 
 
 697 
 
 1046 
 
 1395 
 
 2500 
 
 906 
 
 1359 
 
 1812 
 
 3275 
 
 1136 
 
 1704 
 
 
 4640 
 
 1551 
 
 
 
 Brown Palace Hotel, Denver, Colo. 
 Heat and Power from 520 H. P. of Heine Boilers. 
 
 16 
 
COAL. 
 
 Coal is by far the most important fuel in use. The cases where wood 
 is used are exceptional, and becoming more so as population increases and 
 timber becomes scarce and more in demand for structural purposes. Very 
 favorable local conditions are necessary before fuel oils or gases can compete 
 with coal. It is interesting to trace the gradual increase in the demand for 
 coal. 
 
 In England coal was first used in the twelfth century, and was then and 
 long after known as sea-coal to distinguish it from char-coal. This name 
 was given it from the fact that it was first believed to be a marine product, 
 being gathered among the seaweed and other wreckage cast up by the waves 
 on Northumbrian beaches. Later on the name was given to coal brought 
 from over the sea. 
 
 About the year 1200 the English began to dig coal systematically for the 
 use of their smiths and lime burners. In 1281 the entire coal trade of New- 
 ■castle on Tyne amounted to about $500 a year. In 1307 the brewers, 
 dyers, etc., of London had so generally adopted coal in their works that a 
 ■commission to abate the smoke nuisance was instituted. Its powers and 
 methods were far less restricted than those of similar commissions now being 
 very generally instituted in American cities. 
 
 In dwellings coal was not used till the middle of the fourteenth century, 
 since chimneys had first to be invented, but early in the fifteenth century we 
 find Falstaff sitting "at the round table, by a sea-coal fire." 
 
 In 1577 a writer says in regard to the coal mines, "Theyr greatest trade 
 beginneth now to grow from the forge into the kitchin and hall," When 
 the Stuarts came to the English throne they made the use of coal fashiona- 
 ble, so that in 1612 a writer states that it had become "the generale fuell of 
 this Britaine Island." "Coking" coal (originally "cooking" it) came in 
 vogue about 1640, and in 1656 an English knight anticipated the St. Louis 
 Smoke Committee of 1892 in attempting to introduce coke for domestic pur- 
 poses. But as late as 1686 sea-coal and pit-coal were considered "not use- 
 ful to metals," and char-coal still held the field in smelting furnaces. But 
 ■during the next fifty years, lead, tin and finally iron furnaces began to use 
 ^oal. Soon after the gradual development of steam power began. In 1800 
 the total production of coal in Great Britain had reached ten million tons. In 
 1891 the records show 185,479,126 tons of which about 1-6 was exported, 
 1-6 was for domestic use, and the other 2-3 was consumed in the arts and 
 manufactures. 
 
 In the United States up to 1860 the use of: wood as fuel, for dwellings, 
 for factories, steamboats and locomotives was quite general, except in the 
 anthrarite coal districts. But since then the use of bituminous coal has in- 
 creased rapidly and steadily for all purposes. 
 
 — 17 — 
 
The following table gives the amounts of coal produced during the last 
 twelve years : 
 
 Table No. ii. 
 
 Amount of Coal, in Tons of 2000 lbs., Mined in the United States 
 
 Since 1880. 
 
 YEAR. 
 
 ANTHRACITE. 
 
 ALL OTHERS. 
 
 TOTAL. 
 
 1880 
 
 26,249,711 
 
 47,398,286 
 
 73,647,997 
 
 1881 
 
 31,920,018 
 
 56,327,412 
 
 88,247,430 
 
 1882 
 
 32,614,507 
 
 65,588,241 
 
 98,202,748 
 
 1883 
 
 35,418,353 
 
 72,663,765 
 
 108,082,118 
 
 1884 
 
 36,558,478 
 
 73,836,730 
 
 110,395,208 
 
 1885 
 
 38,335,973 
 
 74,273,838 
 
 112,609,811 
 
 1886 
 
 39,035,446 
 
 75,624,846 
 
 114,660,292 
 
 1887 
 
 42,088,196 
 
 88,887,109 
 
 130,975,305 
 
 1888 
 
 46,619,564 
 
 98,850,642 
 
 145,470,206 
 
 1889 
 
 39,656,635 
 
 98,460,065 
 
 138,116,702 
 
 1890 
 
 46,468,640 
 
 109,604,971 
 
 156,073,611 
 
 1891 
 
 50,665,431 
 
 118,878,517 
 
 169,543,948 
 
 1892 
 
 49,735,744 
 
 122,033,611 
 
 171,769,355 
 
 1893 
 
 47,354,563 
 
 128,823,364 
 
 176,177,927 
 
 1894 
 
 52,010,433 
 
 117,950,348 
 
 169,960,781 
 
 1895 
 
 51,785,122 
 
 135,118,193 
 
 186,903,315 
 
 1896 
 
 48,010,616 
 
 137,640,276 
 
 185,650,892 
 
 In the United States a long ton of coal is 2240 lbs. 
 In the United States a short ton of coal is 2000 lbs. 
 In Illinois, Kentucky and Missouri 80 lbs. of bituminous coal make a 
 bushel. 
 
 In Pennsylvania, 76 lbs. of bituminous coal make a bushel. 
 
 In Indiana 70 lbs. of bituminous coal make a bushel. 
 
 A cubic foot of solid anthracite coal weighs 93.5 lbs. 
 
 Forty-two cubic feet of prepared anthracite coal weigh one long ton. 
 
 Coal may be arranged in five classes : 
 
 1st. Anthracite, or blind coal, consisting almost entirely of free carbon. 
 
 Dry bituminous coal, having from 70 to 80 per cent, of carbon. 
 
 Bituminous caking coal, having from 50 to 60 per cent, of carbon. 
 Long flaming or cannel coal, having from 70 to 85 per cent, of 
 
 Lignite, or brown coal, containing from 56 to 76 per cent, of 
 
 2d. 
 
 3d. 
 
 4th. 
 carbon. 
 
 5th. 
 carbon. 
 
 In the United States the anthracites are found mainly in the eastern 
 portion of the Allegheny Mountains and the Rocky Mountains of Colorado ; 
 the dry bituminous coals in Maryland and Virginia ; the caking coals in the 
 great Mississippi Valley ; the cannel coals in Pennsylvania, Indiana and 
 Missouri ; the lignites in Colorado, Texas and Washington. The second and 
 third classes furnish the best steam coal. 
 
 The following table, compiled from a number of analyses of coals 
 bought in the open market may prove of value, bearing in mind what we 
 said of the difference between theoretical and practical heating powers. 
 (See p. 15.) 
 
 We will add what a noted Germ.an engineer, Mr. F. Bode, says on this 
 point: " The calculation of the calorific value of a given coal from a7i elenie7itary 
 analysis is unreliable, and often gives results greatly at variance with an 
 actii.al calorinietric test. ' ' 
 
 — 19 — 
 
TABLE No. 12. 
 
 Table of American Coals. 
 
 Heating and Evaporative Power. 
 
 COAL. 
 
 Name or Locality. 
 
 ^ o 2 
 
 H£ 
 
 ^- CI. !r 
 
 ^ .> nj C 
 
 COAL. 
 
 Name or Locality. 
 
 
 ARKANSAS. 
 
 Coal Hill, Johnson Co 
 
 Huntington Co 
 
 Huntington Co 
 
 Huntington Co 
 
 ILLINOIS. 
 
 Big Muddy, Jackson Co .... 
 Big Muddy, Jackson Co .... 
 Big Muddy, Jackson Co .... 
 Big Muddy, Jackson Co .. 
 
 Carterville 
 
 Carterville 
 
 Carterville 
 
 Carterville 
 
 Carterville 
 
 Carterville 
 
 Carterville 
 
 Colchester 
 
 Colchester Slack 
 
 Collinsville, Madison Co.... 
 
 Dumferline Slack 
 
 Duquoin, Jupiter 
 
 Glen Carbon 
 
 Glen Carbon 
 
 Gillespie, Macoupin Co 
 
 Girard, Macoupin Co 
 
 Girard, Macoupin Co 
 
 Heitz Bluff, St. Clair Co.... 
 Heitz Bluff, St. Clair Co.... 
 
 Hurricane 
 
 Muddy Valley 
 
 Oakland, St. Clair Co 
 
 Paradise 
 
 St. Bernard 
 
 St. Clair 
 
 St. Clair 
 
 St. Clair 
 
 St. John, Perry Co 
 
 St. John, Perry Co 
 
 Streator, LaSalle Co 
 
 Trenton, Clinton Co 
 
 Trenton, Clinton Co 
 
 Turkey Hill 
 
 Turkey Hill 
 
 Vulcan 
 
 Vulcan 
 
 INDIANA. 
 Block 
 
 INDIAN TERRITORY 
 
 Atoka 
 
 Choctaw Nation 
 
 McAllister 
 
 McAllister 
 
 11812 
 
 12.22 
 
 11757 
 
 12.16 
 
 11906 
 
 12.32 
 
 12537 
 
 12.97 
 
 11466 
 
 11.87 
 
 11529 
 
 11.93 
 
 31781 
 
 12.19 
 
 11200 
 
 11.60 
 
 11481 
 
 11.89 
 
 12383 
 
 12.71 
 
 11498 
 
 11.90 
 
 11407 
 
 11.81 
 
 11337 
 
 11.73 
 
 11700 
 
 12.12 
 
 11400 
 
 11.80 
 
 9848 
 
 10.19 
 
 9035 
 
 9.35 
 
 10143 
 
 10.50 
 
 9401 
 
 9.73 
 
 10710 
 
 11.08 
 
 9675 
 
 10.01 
 
 9804 
 
 10.14 
 
 9739 
 
 10.09 
 
 9954 
 
 10.30 
 
 10269 
 
 10.63 
 
 10332 
 
 10.69 
 
 10576 
 
 10.95 
 
 11868 
 
 12.28 
 
 11718 
 
 12.14 
 
 10395 
 
 10.76 
 
 11340 
 
 11.73 
 
 10080 
 
 10.44 
 
 9261 
 
 9.58 
 
 10294 
 
 10.65 
 
 10647 
 
 11.02 
 
 9765 
 
 10.10 
 
 9828 
 
 10.18 
 
 11403 
 
 11.80 
 
 10584 
 
 10.96 
 
 11245 
 
 11.63 
 
 11255 
 
 11.64 
 
 11260 
 
 11.65 
 
 9450 
 
 9.78 
 
 10626 
 
 11.00 
 
 10407 
 
 10.77 
 
 11088 
 
 11.47 
 
 12789 
 
 13.23 
 
 13287 
 
 13.75 
 
 12800 
 
 13.25 
 
 IOWA. 
 
 Milwaukee Pea 
 
 Thornburgh 
 
 Muchikinock 
 
 Good Cheer 
 
 KENTUCKY. 
 
 Kanawah 
 
 Kanawah 
 
 MARYLAND. 
 
 George's Creek Cumberland 
 George's Creek Cumberland 
 George's Creek Cumberland 
 
 MISSOURI. 
 
 Bevier 
 
 Cannel 
 
 Carter 
 
 Elston 
 
 Freeburg 
 
 Henry 
 
 Keene 
 
 K. T 
 
 Lump 
 
 NEW MEXICO. 
 
 Coal 
 
 OHIO. 
 
 Hocking Valley 
 
 Jackson Co 
 
 Jackson Co 
 
 PENNSYLVANIA. 
 
 Clearfield 
 
 Pittsburgh 
 
 Pittsburgh Gas 
 
 Pittsburgh Slack 
 
 Reynoldsville 
 
 Wilkesbarre 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Youghiogheny 
 
 Oil (Crude) 
 
 Oil (Crude) 
 
 10240 
 
 10690 
 
 11370 
 
 8702 
 
 12689 
 13345 
 
 13700 
 13400 
 12800 
 
 9890 
 11832 
 10880 
 12656 
 11436 
 10466 
 10956 
 10448 
 
 9414 
 
 11756 
 
 13309 
 12343 
 11600 
 
 14000 
 13104 
 13035 
 11739 
 12981 
 13563 
 12936 
 12600 
 13480 
 13287 
 12909 
 13222 
 12278 
 13305 
 12600 
 13ill 
 12487 
 12600 
 13309 
 13158 
 17268 
 16801 
 
 20 — 
 
Table of American Coals — Continued. 
 
 COAL. 
 
 Name or Locality. 
 
 w 
 
 
 ex . 
 
 .T) 
 
 2 r- ° " 
 
 •-.E.fe " 
 
 
 
 h£ 
 
 2 aS « 
 
 
 
 CQ 
 
 £WS§ 
 
 COAL. 
 
 Name or Locality. 
 
 VI 
 
 TENNESSEE 
 
 Glen Mary, Scott Co... 
 
 Lump 
 
 Lump 
 
 TEXAS. 
 
 Ft. Worth 
 
 Ft. Worth 
 
 VIRGINIA. 
 
 Pocohontas 
 
 Pocohontas 
 
 13167 
 
 13.63 
 
 12600 
 
 13.04 
 
 12215 
 
 12.65 
 
 9450 
 
 9.78 
 
 11803 
 
 12 22 
 
 13363 
 
 13.83 
 
 13029 
 
 13.49 
 
 WASHINGTON. 
 
 Carbon Hill 
 
 Carbon Hill 
 
 Carbon Hill 
 
 WEST VIRGINIA 
 
 New River 
 
 New River 
 
 New River 
 
 New River 
 
 12316 
 12085 
 12866 
 
 13374 
 12806 
 12800 
 12962 
 
 12.75 
 12.51 
 13.32 
 
 13.84 
 13.26 
 13.25 
 13.52 
 
 The average proximate analysis of a few of the commonest coals are given in the fol- 
 lowing table: 
 
 Ordinary Illinois 
 
 Best Illinois 
 
 Pennsylvania Bituminous 
 Pennsylvania Anthracite . 
 New River, W. Va 
 
 Moisture. 
 
 9.90 
 6.40 
 1.70 
 2.00 
 .85 
 
 Volatile 
 Matter. 
 
 33.40 
 30.60 
 31.80 
 6.40 
 18.40 
 
 Fixed 
 Carbon. 
 
 43.80 
 54.60 
 60.10 
 78.40 
 77.60 
 
 Ash. 
 
 12.80 
 8.30 
 6.40 
 
 13.20 
 2.90 
 
 Sulphur. 
 
 3.35 
 
 1.78 
 
 .84 
 
 0.26 
 
 
 Boiler Plant of the Orleans Street Ry. Co. 
 NEW ORLEANS, LA. 
 500 H. P. Heine Boilers, 
 
 21 — 
 
As foreign results in the work of both boilers and engines are frequently- 
 brought to our notice by the professional press, it will be convenient to have 
 some tables of English, French and other foreign coals, for purposes of com- 
 parison, and they are here given : 
 
 c 
 .2 
 
 CO 
 
 S 
 o 
 U 
 
 CQ 
 
 
 <D 
 
 
 s: 
 
 d) 
 
 
 ->—> 
 
 ^ 
 
 CO 
 
 X 
 
 O 
 
 
 +- > 
 
 Oh 
 
 o 
 z 
 
 ^ 
 
 CD 
 > 
 
 w 
 
 CO 
 
 -t— I 
 
 CO 
 
 od 
 
 
 < 
 
 O 
 
 o 
 
 H 
 
 U 
 
 01 
 
 
 a 
 
 > 
 
 
 b£ PJ 
 
 
 CD 
 
 'TIS 
 
 
 o 
 
 c 
 
 
 uu 
 
 ^ 
 
 
 ^ 
 
 
 
 c 
 
 
 
 03 
 
 
 
 rC 
 
 
 
 c/) 
 
 
 CQ 
 
 .2 
 
 o 
 ex 
 
 B 
 o 
 U 
 
 <D 
 03 
 
 > 
 
 }B pUB lUOiJ. |B03 qi 
 
 lO ■>— I GO -^ O 
 
 O O lO Oi tr- 
 
 Oi 00 t^ t- t^ 
 
 »i5 o 
 
 00 <>J 
 
 
 juaiBAinbg 
 
 •JB3H JOSJjUn; •£ 
 
 1^1 -^ CO c<i as 
 
 i:D t^ T— ( 1— I CO 
 
 >0 to lO >-0 lO 
 
 CO CO CO ->] 00 
 CM O ^ O CD 
 ■,-( (>q CD <X> 00 
 »it) lO '^ ^ ^ 
 
 O 
 
 Oi 1-" 
 
 CD 
 00 
 
 T-i CD 
 CO t^ 
 
 O T-t 
 
 CO K2 
 
 •|B03 
 
 CO th as 00 ""^ 
 t— CO lo lo lo 
 
 O • 
 
 OS ^ 
 
 1— I !>• »0 00 CO 
 
 as t^ CO oo o 
 
 TjH Co' <m" '^' Tl^" 
 
 lo as oo CO oti 
 
 ■r-( CO (M O CO 
 
 ■^ lO o as as 
 
 CO -^ T-l -rjl T-l 
 
 ■* (M O -^ i-H 
 
 00 iC tH o o 
 as CO "^ CO o 
 
 O T— I T-H 1— I ■"— I 
 
 O^ -rH ^ C^ T-l 
 
 r^ CO ati CO CD 
 
 Tji LO '^ lO lO 
 
 OO (M; 00 O CO 
 
 r— 1— 1 CD as lo 
 
 CO c<j as t--' 00 
 00 00 t^ t^ t^ 
 
 O CO 
 
 00 as 
 o ^ 
 
 :a5 
 
 
 ZD CO 
 
 CO oo 
 CM O 
 
 as 
 1—1 
 
 o t- 
 
 CO OS 
 
 o 
 
 '*. 
 o 
 
 00 
 
 CO O 
 
 o -^^ 
 
 O CO 
 
 00 00 
 
 •padBSj-i 
 uox I JO >iina 
 
 t- CO -* (M O 
 
 3<] lO t^ >^ Ol 
 
 ^1 ^^ ^^ "^^ ^^ 
 
 
 lO ^ 
 CO CO 
 
 ■padBSH •» •n3i 
 
 T-l 00 CM I>- O 
 
 CO as t^ OS o 
 lO -* ^ '^i ic. 
 
 ■p!los -ii -no I 
 
 O CO CO ^ CO 
 
 cm' 00 O OS 00 
 00 !>• 00 t- !>• 
 
 o 
 
 <M ^ 
 
 •O CD 
 
 as 
 
 OS CO 
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 r- CO 00 
 
 CM* CO* CD 
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 T-I lo CO 
 
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 lO -^ CM 
 
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 — 22 — 
 
Steel Framing of the Carnegie Building, 
 
 PITTSBURGH, PA., 
 
 Completed building contains 505 H. P. Heine Boilers. 
 
TABLE NO. 14. 
 
 Composition and Heating Power of French Coals. 
 
 D. K. C. 
 
 Coal. 
 
 RONCHAMP. 
 
 No. 1 
 
 No. 2 
 
 No. 3 
 
 No. 4 
 
 Average 
 
 SARREBRUCK.* 
 
 Dudweiler 
 
 Altenwald 
 
 Heinitz 
 
 Friedrichsthal 
 
 Louisenthal 
 
 Sulzbach 
 
 Von der Heyt 
 
 BLANZY. 
 
 Montceau 
 
 Anthracitic - 
 
 Creuzot, Anthracite. 
 
 COMPOSITION. 
 
 Per 
 Cent. 
 
 76.5 
 68.6 
 76.2 
 73.1 
 73.6 
 
 71.3 
 69.3 
 70.3 
 67.8 
 64.7 
 73.3 
 70.6 
 
 66.1 
 67.0 
 
 87.4 
 
 Per 
 Cent. 
 
 4.4 
 4.0 
 4.1 
 
 3.8 
 4.1 
 
 4.1 
 4.3 
 4.3 
 4.2 
 3.9 
 4.6 
 4.5 
 
 4.4 
 3.6 
 3.5 
 
 Per 
 Cent. 
 
 3.0 
 
 4.7 
 5.9 
 4.9 
 4.6 
 
 9.2 
 9.9 
 
 n.5 
 
 13 8 
 
 15.0 
 
 9.6 
 
 11.2 
 
 13.2 
 5.9 
 3.2 
 
 Per 
 Cent. 
 
 1.1 
 1.1 
 1.0 
 1.0 
 1.5 
 
 0.5 
 0.5 
 0.5 
 0.5 
 0.5 
 0.5 
 0.5 
 
 0.5 
 0.5 
 0.5 
 
 Per 
 
 Cent. 
 
 0.8 
 
 1.8 
 2.5 
 1.8 
 1.0 
 3.6 
 1.6 
 2.7 
 
 10.3 
 
 21.0 
 
 3.6 
 
 Per 
 Cent. 
 
 15.0 
 20.8 
 12.8 
 16.2 
 16.2 
 
 13.1 
 13.5 
 11.6 
 12.7 
 12.3 
 10.4 
 10.5 
 
 5.0 
 2.0 
 1.8 
 
 Per 
 Cent. 
 
 61.7 
 55.6 
 62.3 
 62.4 
 60.5 
 
 53.5 
 52.9 
 53.7 
 50.2 
 47.3 
 
 Per 
 Cent. 
 
 23.3 
 23.6 
 24.9 
 21.4 
 23.3 
 
 33.4 
 33.6 
 34.7 
 37.1 
 40.4 
 
 Heating 
 Power of l 
 lb. OF Coal. 
 
 14357 
 13743 
 14085 
 13995 
 14045 
 
 13833 
 13320 
 13548 
 13647 
 12665 
 13608 
 13866 
 
 12720 
 12825 
 16108 
 
 B.T. U. 
 
 13820 
 12430 
 13590 
 12960 
 13220 
 
 12880 
 12720 
 12860 
 12440 
 11800 
 13480 
 13030 
 
 Pounds 
 
 of 
 Water. 
 14.86 
 14.23 
 14.59 
 14.49 
 14.54 
 
 14.32 
 13.79 
 14.03 
 14.13 
 13.11 
 14.09 
 14.36 
 
 123901 13.17 
 11950J 13.28 
 US'^OI 16.68 
 
 Combustion of Coal. 
 
 "When coal is exposed to heat in a furnace, a portion of the carbon and 
 hydrogen, associated in various chemical unions, as hydro-carbons, are vol- 
 atilized and passed off. At the lowest temperature, naphthaline, resins, and 
 fluids with high boiling points are disengaged ; next, at a higher tempera- 
 ture, volatile fluids are disengaged ; -and still higher, olefiant gas, followed by 
 common gas, light carburetted hydrogen, which continues to be given off 
 after the coal has reached a low red heat. What remains after the distilla- 
 tory process is over, is coke, which is the fixed or solid carbon of coal, with 
 earthy matter, the ash of the coal. 
 
 Taking the fixed carbon, or coke remaining in the furnace after the vol- 
 atile elements are distilled off, for round numbers at 60 per cent., the follow- 
 ing is an approximate summary of the condition of the elements of average 
 coal, after having been decomposed, and prior to entering into combustion : 
 100 POUNDS OF AVERAGE COAL IN THE FURNACE. 
 
 Composition. 
 r Fixed 
 
 Lbs. 
 
 60 
 
 Carbon | Volatilized 20 
 
 Hydrogen 5 
 
 Sulphur. 
 Oxygen - 
 Nitrogen 
 Ash -— 
 
 11-4 
 8 
 
 1 1-5 
 4 
 
 Decomposition. Lbs, 
 
 Fixed Carbon 60 
 
 Hydrocarbons 24 
 
 Sulphur 1 1-4 
 
 Water or Steam 9 
 
 Nitrogen 1 1-5 
 
 Ash 4 
 
 100 
 
 About 100 
 
 showing a total useful combustible of 86^ per cent, of which 26^ per cent. 
 is volatilized. While the decomposition proceeds, combustion proceeds, and 
 the 26^ per cent, of volatilized portions, and the 60 per cent, of fixed car- 
 bon, successively, are burned. 
 
 * Tbftse are now German Coals. 
 
 24 — 
 
The sulphur and a portion of the nitrogen are disengaged in combina- 
 tion with hydrogen, as sulphuretted hydrogen and ammonia. But these com- 
 pounds are small in quantity, and, for the sake of simplicity, they have not 
 been indicated in the above synopsis. 
 
 There are three modes of supplying coal to ordinary furnaces by hand 
 firing, namely : spreading, alternate, and coking firing. In spreading firing 
 the charge of coal is scattered evenly over the whole surface of the grate, 
 commencing generally at the bridge, and working forward to the door. In 
 alternate firing the charge of coal is laid evenly along half the width of the 
 grate at a time, from back to front, each side alternately. In coking firing 
 the charge of coal is thrown on to the dead plate and the front part of the 
 bars and left there for a time, in order that the mass may become coked 
 through, and when that is done the mass is pushed back towards the bridge, 
 and another charge is thrown on to the front of the fire in its place. In this 
 way the gases are gradually evolved from the coal at the front, while a bright 
 fire is maintained at the back. 
 
 It is thought advantageous, in slowly burning furnaces having long flues, 
 that the fuel should be slightly moist, and that the ash pits should be sup- 
 plied with water, from which steam may be generated by the heat radiated 
 downwards from the fire, and passed through the firegrate. The access of 
 water to the fuel lessens the "glow fire" or flameless incandescence of the 
 fixed carbon on the grate, and increases the quantity of flame by forming 
 carbonic oxide and hydrogen gases in its decomposition into its elements, 
 oxygen and hydrogen, and the reduction, by the oxygen, of the carbonic 
 acid already formed in the furnace. The newly made gases are afterwards 
 burned in the flues. The presence of moisture, even in coke, gives rise tO' 
 flame in the flues, and reduces the intensity of the heat in the glow fire. 
 The combustion, in fact, is deferred, or distributed ; and -it is on this princi- 
 ple that moist bituminous coals are most effective in furnaces having long 
 flues, as in Cornish boilers. 
 
 That two coals of identical composition may possess very different heat- 
 ing powers is evidenced by comparing the bituminous coals of Creuzot and 
 Ronchamp, which have the following nearly identical compositions, reckon- 
 ing the coal as dry and pure, or free from ash : 
 
 Carbon, 
 Per cent. 
 
 Hydrogen, 
 F-er cent. 
 
 Oxygen, 
 Per cent. 
 
 Heating 
 Power. 
 
 88.48 
 
 4.41 
 
 7.11 
 
 17320 
 
 88.32 
 
 4.78 
 
 6.89 
 
 16339 
 
 Creuzot 88.48 
 
 Ronchamp 88.32 
 
 while there is a difference of six per cent, in the actual heating powers.- 
 Correspondingly, the Creuzot coal had only 19.6 per cent, of volatile matters^, 
 while the Ronchamp coal yielded 27 per cent. 
 
 Lignite and Asphalt. 
 
 Brown lignite is sometimes of a woody texture, sometimes earthy. 
 Black lignite is either of a woody texture, or it is homogeneous, with a 
 resinous fracture. Some lignites, more fully developed, are of a schistose 
 character, with pyrites in their composition. The coke produced from 
 various lignites is either pulverulent, like that of anthracite, or it retains the 
 forms of the original fibres. Lignite is less dense than coal. 
 
 — 25 — 
 
Asphalt, like lignite, has a large proportion of hydrogen. It has less 
 than 9 per cent, of oxygen and nitrogen, and thus leaves 8J per cent, of 
 free hydrogen, and it accordingly yields a porous coke. 
 
 The average composition of perfect lignite and of asphalt may be taken 
 in whole numbers as follows : 
 
 Lignite. Asphalt. ' 
 
 Carbon- 69 per cent. 79 per cent. 
 
 Hydrogen 5 " 9 " 
 
 Oxygen and Nitrogen 20 " 9 " 
 
 Ash 6 " 3 " 
 
 100 100 
 
 Coke, by laboratory analysis 47 " 9 " 
 
 The lignites are distinguished from coal by the large proportion of oxygen 
 in their composition — from 13 to 29 per cent. 
 
 The heating powers of lignite and asphalt are respectively measured 
 by 13,108 units, and 17,040 units. 
 
 WOOD. 
 
 Wood, as a combustible, is divisible into two classes : 1st. The hard, 
 compact, and comparatively heavy woods, as oak, beech, elm, ash; 2d. The 
 light-colored, soft, and comparatively light woods, as pine, birch, poplar. 
 
 In the forests of Central Europe, wood cut down in winter holds, at the 
 end of the following summer, more than 40 per cent, of water. Wood kept 
 for several years in a dry place retains from 15 to 20 per cent, of water. 
 Wood which has been thoroughly desiccated will, when exposed to air under 
 ordinary circumstances, absorb 5 per cent of water in the first three days; 
 and will continue to absorb it until it reaches from 14 to 16 per cent., as a 
 normal standard. The amount fluctuates above and below this standard, 
 according to the state of the atmosphere. Ordinary firewood cor tains, by 
 analysis, from 27 to 80 per cent, of hygrometric moisture. 
 
 The woods of various trees are nearly identical in chemical composition, 
 which is practically as follows, showing the composition of perfectly dry 
 wood, and of ordinary firewood holding hygroscopic moisture : 
 
 TABLE No. 15. 
 
 Desiccated Wood. Ordinary Firewood. 
 
 Carbon 50 per cent 37.5 percent. 
 
 Hydrogen 6 per cent 4.5 percent. 
 
 Oxygen 41 per cent 30.75 per cent. 
 
 Nitrogen 1 per cent 0.75 per cent. 
 
 Ash 2 per cent 1.5 percent. 
 
 100 rjcv cent. 75.0 per cent. 
 
 Hygrometric water 25.0 per cent. 
 
 100.0 
 
 The quantity of intersticial space in a closely packed pile of wood, con- 
 sisting of round uncloven stems, is 30 per cent, of the gross bulk ; for cloven 
 stems, the intersticial space amounts to from 40 to 50 per cent. 
 
 English oak — a hard wood — weighs 58 lbs. per solid cubic foot ; its 
 specific gravity is .93. Yellow pine — a soft wood — weighs 41 lbs. per solid 
 cubic foot ; its specific gravity is .QQ. 
 
o H ^ 
 
 X O 5- 
 
 • %) Cl. 
 
 ■ O <^ 
 
 2. r~ <^ 
 
 ro U n 
 
 CO 
 
 o 
 
 a, 
 
A cord of pine wood — that is, of pine wood cut up and piled — in the 
 United States, measures 4 feet by 4 feet by 8 feet,- and has a volume of 128 
 cubic feet. Its weight in ordinary condition averages 2700 lbs.; or 21 lbs. 
 per cubic foot. 
 
 The quantity of air chemically consumed in the complete combustion of 
 
 one pound of perfectly dry wood, by rule 1, page 13, is 80 cubic feet at 62° 
 
 F., or 6.09 lbs. of air. The quantity of burnt gases for 1 lb. of perfectly 
 
 dry wood are 
 
 Table No. 16. 
 
 By Weight. By Volume. 
 
 Lbs. Per cent. Cu. ft. at 62°F. Per cent. 
 
 Carbonic acid 1.83 21.7 15.75 14.4 
 
 Steam 0.54 6.4 11.40 10.4 
 
 Nitrogen 6.08 71.9 82.01 75.2 
 
 Totals 8.45 100.0 109.16 100.0 
 
 showing that there are 8J lbs., or 109 cubic feet, at 62° F., of burnt gases 
 per pound of wood, 13 cubic feet to the pound. 
 
 The total heat of combustion of perfectly dry wood, by rule 4, page 14, 
 is 10974 units, which is 75 per cent, of that of coal, and is equivalent, by 
 rule 5, to the evaporation of 11.36 lbs. of water from and at 212° F. 
 
 When the wood holds 25 per cent, of water, there is only 75 per cent. 
 or three-quarter pound of wood substance in one pound ; and the total heat 
 of combustion is 75 per cent, of 10974 units, or 8230 units, which is only 
 56i per cent, of that of average coal. Similarly, the equivalent evaporative 
 power is reduced to 8.52 lbs. of water from and at 212°, of which the equiva- 
 lent of a quarter of a ppund is appropriated to the vaporizing of the con- 
 tained moisture — ^that is to say, for evaporating one-quarter pound of water, 
 supplied at 62° F., the quantity of heat is 1116°— 4=279 units, and the net 
 available heat for service is 8230 — 279=^7951 units per pound of fuel holding 
 25 per cent of water.* 
 
 In order to obtain the maximum heating power from wood as fuel, it is 
 the practice, in some works on the continent of Europe, — as glass works and 
 porcelain works, — where intensity of heat is required, to dry the wood fuel 
 thoroughly, even using stoves for the purpose, before using it." 
 
 D. K. C. 
 
 The American Society of Mechanical Engineers in their Rules for Boiler 
 Tests allow 1 lb. of wood =: 0.4 lb. of coal ; or 2.J lbs. of wood = 1 lb. of 
 coal. Other authorities estimate 2^ lbs. of dry wood = 1 lb. of good coal. 
 One pound of wood is practically equivalent to one pound of any other kind 
 of wood equally dry. 
 
 Table no. 17. 
 
 1 cord of hickory or hard maple weighs 4500 lbs. and = 2000 lbs. coal. 
 
 1 cord of white oak weighs 3850 lbs. and = 1711 lbs. coal. 
 
 1 cord of beech, red oak, or black oak weighs 3250 lbs. and = 1145 lbs. coal. 
 
 1 cord of poplar, chestnut, or elm weighs 2350 lbs. and = 1044 lbs. coal. 
 
 1 cord of average pine weighs 2000 lbs. and = 890 lbs. coal. 
 
 * This figure may be used for a close approximation in comparing a certain kind of 
 wood to a known coal. Suppose the calculated heat in a pound of the coal to be 18025 
 B. T.U.,andan actual boiler test showed an evaporation of seven poundsof water per pound 
 of coal. Then 13025:7951::7:4.28, /. <?., you may expect to evaporate about 4.28 lbs. of 
 water per pound of the wood in the same boiler. 
 
 — 28 — 
 
In substituting any kind of wood for coal under a boiler, the dimensions 
 of the furnace must be increased, preferably mainly in the height, so that 
 by carrying a greater depth of fuel nearly as much by weight may be present 
 in the furnace as was usual or necessary with the coal. 
 
 " BAGASSE." 
 
 Bagasse is the fibrous portion of the cane left after the juice has been 
 extracted from it in the mill. There is a great difference in the chemical 
 composition of bagasse ; that from tropical canes shows a greater proportion 
 of combustibles. 
 
 Prof. L. A. Becnel, in an address to the Louisana Sugar Chemists Asso- 
 ciation, said: " The judicious use of bagasse as fuel is perhaps one of the 
 most important questions with which we have to deal, and which has a direct 
 bearing on the reduction of cost of manufacture," He then quotes from Mr, 
 N. Lubbock that 4,83 lbs, of bagasse from a double mill making 72 per cent 
 extraction, or 5.98 lbs, of single mill bagasse of 66 per cent extraction, will 
 produce about as much heat as one pound of Scotch coal. 
 
 Mr, L. Metesser, as the result of a number of tests in Cuba and Mexico, 
 reports from 4.25 to 5 lbs, of 70 per cent bagasse as. equal to- one pound of 
 good coal. 
 
 Tropical cane and the bagasse remaining after mill extraction are of 
 about the following composition : 
 
 Cane. 66% Bagasse. 70% Bagasse. 72% Bagasse. 
 
 Woody Fibre 12,5 37 40 45 
 
 Water 7:i.4 53 50 46 
 
 Combustible Salts • 14.1 10 10 9 
 
 100 lbs. 100 lbs. 100 lbs. lOolbsT" 
 
 Taking these figures as a basis, and remembering that the water in the 
 bagasse has to be first brought up from an average temperature of say 86° F., 
 to steam under atmospheric pressure, requiring 1060 H, U., and that this 
 steam has to be raised to the average stack temperature say 300° higher, and 
 taking the specific heat of gaseous steam at 0.475, which would give say 142 
 H. U. more, therefore a total of 1200 H. U. per pound of water. Mr, Lub- 
 bock found 51 per cent of carbon in the woody fibre, and 42,1 per cent of car- 
 bon in the combustible salts. Since a pound of carbon in perfect combustion 
 will liberate 14500 H. U,, we will have i.n 100 lbs, of 66 per cent bagasse, 
 334660 H. U., from which we must deduct 63600 H. U. as absorbed by the 
 water, leaving 271060 H, U, available as fuel. In like manner, we have in the 
 72 per cent bagasse 387730 H, U.,from which we must deduct 55200 absorbed 
 by the water, leaving 332530 H, U, available. 
 
 In comparing this with good Youghiogheny coal of say 13000 H, U,, and 
 good Scotch coal of 148G0 H, U. calorific value, we find- the. fuel value of the 
 66 per cent bagasse to be : 
 
 5 lbs. bagasse equals one pound Youghiogheny coal, 
 5.52 " " " " " Scotch coal, 
 
 and -that of the 72 per cent bagasse to be 
 
 3.85 lbs. bagasse equals one pound Youghiogheny coal, 
 4.35 " " " " " Scotch coal. 
 
 — 29 — 
 
It will probably require considerably more of the Louisiana bagasse than 
 of the tropical bagasse, since it has about 25 per cent less woody fibre than 
 the latter. 
 
 Mr. Becnel, estimates with 75 per cent Louisiana bagasse as a basis, that 
 " To manufacture one ton of cane into sugar and molasses, it will take from 
 145 to 190 lbs. additional coal by the open evaporation process ; from 85 to 
 112 lbs. additional coal with a double effect," and with triple effect it appears 
 the bagasse alone would do the work, and have enough steam to spare to 
 run engines, grind cane, etc. " If this has not yet been accomplished in 
 Louisiana, may it not be due more to imperfect boiler and evaporating plants 
 than to a deficiency in heat producing properties of the bagasse?" 
 
 The above of course can only be taken as approximately correct. The 
 results will vary greatly according to the kind of boilers and furnaces used. 
 From the nature of this fuel, it follows that it should be fed continuously into 
 a very hot fire brick chamber, and that plenty of room must be left in the 
 furnace and boiler setting to accommodate the large volume of gas and steam 
 produced by the bagasse. 
 
 Bridge Mill Power Co., 
 
 PAWTUCKET, R. L 
 
 Contains 6io H. P. of Heine Boilers. 
 
 30 — 
 
The hii^'aer the per cent of extraction the mure fuel value the bagasse 
 will have, and as it will necessarily contain less moisture, the larger pro- 
 portion of this enhanced fuel value becomes available in the boiler furnace. 
 The improvement in boiler plants will thus naturally go hand in hand with 
 improved methods of extraction. 
 
 TAN AND STRAW. 
 
 Tan. 
 
 "Tan, or oak bark, after having been used in the process of tanning, is 
 burned as fuel. The spent tan consists of the fibrous portion of the bark. 
 According to M. Peclet, five parts of oak bark produce four parts of dry tan ; 
 and the heating power of perfectly dry tan, containing 15 per cent of ash, is 
 6100 English units, while that of tan in an ordinary state of dryness, con- 
 taining 30 per cent of water, is only 4284 English .units. The weight of 
 water evaporated at 212° by one pound of tan, equivalent to these heating 
 powers, is as follows : 
 
 With 30% of 
 Perfectly Dry. Moisture. 
 
 Water supplied at 62^ 5.46 lbs. 3.84 lbs. 
 
 Water supplied at 212° - 6.31 lbs. 4.44 lbs. 
 
 (See cote under Wood.) 
 
 Straw. 
 
 The composition of straw, in its ordinary air-dried condition, is given by 
 Mr. John Head, as follows: 
 
 TABLE NO. 18. 
 
 Wheat Straw, Barley Straw, Mean, 
 
 per cent. per cent. per cent. 
 
 Carbon 35.86 36.27 36. 
 
 Hydrogen 5.01 6.07 5. 
 
 Oxygen 37.68 38.26 38. 
 
 Nitrogen .45 .40 .425 
 
 Ash 5.00 4.50 4.75 
 
 Water 16.00 15.50 15.75 
 
 100.00 100.00 100.00 
 
 The weight of pressed straw is from 6 lbs. to 8 lbs. per cubic foot. 
 
 Heat of Combustion of Straw. 
 
 For straw of mean composition, the total heat generated is, by rule 4, 
 equal to 145 [36 -f (4.28X5)] = 8323 units of heat, or the evaporation of 
 7.46 lbs. of water from and at 212° F. Deducting the heat absorbed in 
 evaporating the constituent water, 15f per cent, or .161b., equal to 1 116 X • 16= 
 179 units, the available heat is 8323 — 179 = 8144 units, equivalent to the 
 evaporation of 7.30 lbs. of water from and at 212°. 
 
 (See note under Wood.) 
 
 LIQUID FUELS. 
 
 Petroleum is a- hydrocarbon liquid which is found in abundance in 
 America and Europe. According to the analysis of M. Sainte-Claire Deville, 
 the composition of fifteen petroleums from different sources was found to be 
 practically the same. The average specific gravity was .870. The extreme 
 and the average elementary compositions were as follows: 
 
 — SI — 
 
TABLE NO. 19. 
 
 Chemical Composition of Petroleum. 
 
 Carbon 82.0 to 87.1 per cent. Average, 84.7 per cent. 
 
 Hydrogen 11.2 to 14.8 per cent. Average, 13.1 per cent. 
 
 Oxygen 0.5 to 5.7 per cent. Average, 2.2 per cent. 
 
 100.0 
 
 The total heating and evaporative powers of one pound of petroleum 
 aiaving this average composition are, by rules 4 and 5, as follows : 
 
 Total heating power = 145 [84.7 -f (4.28X13.1)] = 20411 units. 
 
 Evaporative power : evaporating at 212°, water supplied at 62° = 18.29 lbs. 
 Evaporative power : evaporating at 212°, water supplied at 212° = 21.13 lbs. 
 
 Petroleum oils are obtained in great variety by distillation from petroleum. 
 They are compounds of carbon and hydrogen, ranging from Cio H24 to 
 >*C32 H64 ; or, in weight ; 
 
 Table no. 20. 
 
 Chemical Composition of Petroleum Oils. 
 
 Mean. 
 
 cv^^ / 71.42 Carbon \ ./ 73.77 Carbon 72.60 
 
 rrom 1 28,58 Hydrogen i^*^ 126.23 Hydrogen 27.40 
 
 100.00 100.00 100.00 
 
 The specific gravity ranges from .628 to .792. The boiling point ranges 
 -from 86° to 495° F. The total heating power ranges from 28087 to 26975 
 units of heat ; equivalent to the evaporation, at 212°, of from 25.17 to 24.17 
 lbs. of water supplied at 62°, or from 29.08 lbs. to 27.92 lbs. of water supplied 
 ,at 212°. 
 
 D. K. C. 
 
 Oil as a Fuel. 
 
 "Inasmuch as the use of oil as a fuel is now engaging the serious atten- 
 tion of many of our principal engineers and manufacturers, we beg leave to 
 submit for your consideration the following advantages which are claimed 
 for oil as against coke, coal or wood as a fuel. 
 
 1st. A petroleum fire can be held in perfect control by one man of 
 ■ordinary intelligence, by the mere turning of a valve. He can increase or 
 decrease the fire at will, and can maintain steam or heat at any desired 
 point. When the fire is properly regulated to produce the heat required, it 
 -can be kept at that point with but slight attention, so slight, indeed, that one 
 man can fire and care for a battery of from eight to ten 100-horse-power 
 boilers without difficulty. By turning a valve you can instantly extinguish 
 the fire, if occasion does not require its continuous use, and it can be again 
 started with almost the same rapidity with a few shavings or sticks of wood. 
 There is no waste, as with coal, when the work is done. 
 
 2d. The heat generated with petroleum fire is much more uniform than 
 ■that produced with coal or wood. The fire is not as sensitive to the fluctua- 
 tion of the weather as other fires. A great advantage is gained in running 
 machinery where regularity af speed is desirable. A constant supply of 
 steam may be furnished, and there is no reduction of steam pressure in con- 
 isequence of the replenishing of fires. 
 
 — 32 — 
 
H 
 o 
 
 ^ S ^ 
 
 5- O c 
 vj H <^' 
 
 8 of 
 
 ^ z g. 
 
 2. 0§ 
 ^ >5- 
 
 ■^ s .^ 
 2 i> — 
 
 c/) • Bt 
 P 
 aq 
 
Sd. Economy of Boiler Capacity. — It has been demonstrated that one 
 pound of oil will evaporate the water of more than two pounds of coal. The 
 heat units of crude petroleum have been erroneously stated to be 27531. 
 The fact is, that the correct figure, 20240 heat units, has been repeatedly 
 arrived at of late, after many tests with the best instruments to be obtained 
 for that purpose. In comparing the calorific properties of petroleum it must 
 be borne in mind that with coal there is an enormous waste of matter, such 
 as sulphur, slate and earthy substances v/hich are practically incombustible, 
 and which do not add in the generation of heat. While coal theoreti- 
 cally contains about 14300 heat units, that figure is, by reason of these 
 impurities, reduced to about 8000. Pure carbon — charcoal, for instance — 
 contains 14500 heat units. Considering, therefore, the imperceptible waste 
 in the burning of oil, and the excessive waste in the burning of coal, the 
 conclusion is reached that while theoretically the relative proportion of heat 
 evolved in the combustion of oil compared with coal is as 20.2 is to 14.3, the 
 proportion practically considered, is in favor of oil as 19 is to 8, or 8.5 at the 
 furthest. We may quite safely assume, then, that the heating capacity of 
 oil is considerably more than twice that of coal as far as now shown. With 
 a clean boiler, properly attended, and with the best of coal fuel, well stoked 
 night and day — with every care to insure combustion and to avoid waste, 
 the evaporation obtained in some isolated cases specially recorded has been 
 as high as 9-^ pounds. In our every day experience, however, we find 
 that eighty out of a hundred boilers will not vaporize more than from 7 to 
 7 J pounds of water per pound of fuel. On the other hand, oil tests, which, 
 while sufficiently conclusive for the present, have not, by any means, been 
 carried to the furthest limit, show the evaporation from 17.56 to 18.5 pounds 
 of water per pound of oil consumed, from and at 212° Fahrenheit. 
 
 4th. Economy in labor, cleanliness and safety are secured, as in 
 burning oil complete combustion may be obtained. There is no shoveling of 
 ashes, and consequently there is a great saving in labor. The absence of 
 sparks and cinders and the ability to extinguish the fire instantly in case of 
 danger, makes it very desirable when considered with a view to safety. 
 
 5th. There being no necessity for opening doors for the introduction of 
 fuel, there is no fluctuation of heat, and no sudden chilling of the flues and 
 boiler. The absence of sulphur in the fuel makes its action on the metal of 
 the boiler and the flues much less destructive than coal, and the flues remain 
 cleaner and in better condition to absorb the heat. 
 
 6th. Oil or Residuum, is without doubt, the coming fuel on locomotives 
 and ocean steamers, and by its use a great annoyance to passengers in the 
 emission of cinders and smoke will not only be entirely avoided, but less 
 than one-half the room formerly used for coal will be required to store the 
 oil for fuel, and only one-third the weight will be carried, thus saving a great 
 deal of room in storage, which will enable ship owners to carry an additional 
 quantity of freight, or to increase speed to the same amount of power. Be- 
 sides this, where 70 stokers are now required to unload coal on ocean 
 steamers, at least 60 could be dispensed with, and the work be done without 
 the labor of shoveling coal and the great discomfort from heat and dust. 
 
 7th. Regarding the proper construction of furnaces for the consumption 
 of oil, it may be said that there is no occasion for having the combustion 
 chamber as large as when burning coal. The latter article, being solid 
 
 — 34 — 
 

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matter, requires more time for decomposition, and the elimination of the 
 products and supporters of combustion. Coal fuel requires a large fire chamber 
 and the means for the introduction of air beneath the grate-bars to aid com- 
 bustion. Compared with oil, the combustion of coal is tardy and requires 
 some aid by way '. f a strong draft. Oil having no ash or refuse, when prop- 
 erly burned, requires much less space for combustion for the reason that, 
 being a liquid, and the compound of gases that are highly inflammable when 
 united in proper proportions, it gives off heat with the utmost rapidity, and 
 at the point of ignition is all ready for consumption. The changes required 
 to burn oil in a coal furnace may be made at a nominal cost, so that even in 
 this respect no additional expense is necessary for a change for the better. 
 
 8th. Three barrels of oil, each of 42 gallons, equal and slightly exceed 
 the heating capacity of one ton of coal. The oil weighs 913.5 pounds, and 
 may be purchased and delivered in tank cars at any point in the United 
 States at a very low figure. It should be remembered that oil need not be 
 shoveled from the cars to the furnace, it needs no stoking nor poking, it 
 leaves neither cinders nor ashes to be carted away, and it makes no smoke. 
 With an oil furnace, one man may attend to a dozen boilers without any 
 further assistance. 
 
 9th. The fact of being able to produce with oil a perfectly clear, white fire, 
 free from ashes, smoke, dust and soot, which can be kept under control and 
 regulated to any degree of heat required, makes its use invaluable in electric 
 plants, in the manufacture of glass, steel, crockery, stoneware, sewer pipe, 
 brick, lime, and in fact almost any business where such a fire is required." 
 
 c. w. o. 
 
 In November, 1894, the Baldwin Locomotive Works, of Philadelphia, 
 equipped an engine for burning fuel oil and obtained the results stated 
 below: 
 
 TESTS OF OIL FUEL ON LOCOMOTIVE. 
 
 DATE, 1894. 
 
 Weight of train, approximate, lbs 
 
 Number of cars 
 
 Length of run, miles 
 
 Time of run 
 
 Running time 
 
 Average steam pressure, lbs . 
 
 Oil consumption, total lbs.... 
 
 Total gallons 
 
 Per hour 
 
 Per square foot of grate 
 
 Per square foot of grate per hour 
 
 Per square foot of heating surface 
 
 Per square foot of heating surface per hour, 
 
 Water evaporated: total lbs 
 
 Total from and at 212° F 
 
 Per hour 
 
 Per hour from and at 212° F 
 
 Per lb. of oil 
 
 Per lb. of oil from and at 212° F.* 
 
 Per square foot of heating surface 
 
 Per square foot of heating surface per hour, 
 
 Per square foot of heating surface per hour 
 
 from and at 212*' F 
 
 No. I. 
 November 13. 
 
 1,308,160 
 25 and 20 
 
 89.7 
 
 h. m. s. 
 
 6 27 00 
 
 5 14 48 
 
 6,637 
 905 
 lbs. 
 1,003.2 
 237 
 38.3 
 3.13 
 0.49 
 70,933 
 85,622 
 10,998 
 13,280 
 10.69 
 12.90 
 83.47 
 5 19 
 
 No. 2. 
 November 18. 
 
 1,216,120 
 
 30 
 
 54.9 
 
 h. m. s. 
 
 2 56 41 
 
 2 23 26 
 
 171 
 3,200.7 
 
 lbs! ' 
 1,086.9 
 114.32 
 
 38.82 
 
 34,151.7 
 41,465.1 
 
 14,082.2 
 10.67 
 12.95 
 16.12 
 
 5.48 
 
 6.64 
 
 No. 3. 
 November 25. 
 
 1,480,640 
 26 
 52.3 
 h. m. s. 
 3 20 
 2 48 9 
 
 170 
 3,703 
 
 Ibsr" 
 
 1,110.9 
 132.25 
 39.68 
 
 39,169.2 
 46,291.6 
 
 13,887.5 
 
 10.58 
 
 12.50 
 
 18.48 
 
 5.54 
 
 6.55 
 
 ♦Without deducting the steam consumed for vaporizing the oil, or the entrainment. 
 
 — 36 — 
 
The report on the experiments points out that oil has several advantages 
 over coal: 1, no smoke if the firing is properly done; 2, no sparks; 3, no 
 terminal labor in cleaning fires, hauling away ashes and loading coal, which 
 labor is said to amount sometimes to 50 cents per ton of coal consumed ; 
 4, the engine is always ready for service; 5, the fire is always clean and 
 there is no danger of its being torn up by a heavy exhaust or by the engine 
 slipping. Tests of the oil used showed 84 gravity, 140 flash and 190 fire. 
 In conclusion, it is stated that to determine the value of oil, it is necessary 
 to know the evaporative power of the boiler for each pound of fuel burned, 
 which depends greatly upon the ratio of heating surface to grate area, and 
 the volume consumed in a given time. These conditions do not seem to 
 affect the consumption of oil, the evaporation being about the same per 
 pound of oil for all rates of combustion, it being impossible to consume the 
 oil without a proper supply of air, and, as no smoke is made, no unconsumed 
 fuel escapes from the smokestack, as is the case with soft coal. The fol- 
 lowing formula is given for obtaining the value of oil, as compared with coal, 
 as a locomotive fuel, the result being the price per gallon at which oil will 
 be the equivalent of coal. In this formula the cost of both oil and coal must 
 be the cost delivered on the engine, and not the purchasing price: 
 
 BXIO. 7X7 
 
 A = 
 
 2,000XC 
 
 A^ price per gallon at which oil will be equivalent of coal; B = cost of coal 
 per ton, plus the cost of handling ( say 50 cents per ton ) ; C = evaporative 
 power of coal. 
 
 From a lecture at the Naval War College, Newport, R, I., delivered by 
 P. A. Engineer John R. Edwards, U. S. N., in August, 1895, we quote the 
 following: 
 
 With reference to the use of liquid fuel on locomotives, it is interesting 
 to refer to the results obtained in England by Mr. James Holden, Locomotive 
 Superintendent of the Great Eastern Railway, by the process invented and 
 adopted by him. On the locomotive using liquid fuel there is an absence 
 of constant and laborious firing; the requisite pressure of steam is easily 
 obtained by an almost imperceptible movement of the injector valve ; there 
 is an absence of smoke, and a great uniformity of pressure. 
 
 In the inaugural address of the President of the Society of Engineers, 
 in February, 1894, he gave a description of these locomotives and their 
 working cost. He stated that an express engine using 35.4 pounds of coal 
 per mile, consumed under similar circumstances 11.8 pounds of coal and 10.5 
 pounds of liquid fuel, or a total of 22.3 pounds of fuel. 
 
 The advantages of the Holden system are summed up as follows: 
 
 1st. With an ordinary grate, steam can be easily raised without work- 
 ing the injector. 
 
 2d. Fuel can be interchanged according to the state of the market. 
 
 3d. With a thin coal fire, oil can be shut off at will without running 
 the risk of chilling the fire box. 
 
 4th. When standing, the coal fire will maintain steam. 
 
 For several years a number of locomotive engines on the Great Eastern 
 Railway have used liquid fuel, and one of these engines is recorded to have 
 
 — 37 — 
 
traveled 47,000 miles without a single failure or accident. But the great 
 diiticulty in extending the use of liquid fuel in England is the impossibility 
 of obtaining a sufficient supply at a low cost, otherwise it would be very 
 generally used, considering the great calorific effect and the practical 
 advantages of its application. 
 
 It has been very recently stated that since the introduction in the naval 
 ships of liquid fuel, the cost in Italy has increased one hundred and fifty per 
 cent (150 per cent). 
 
 One of the highest officials of the Pennsylvania Railroad asserted that 
 the great cost attending its use was a bar to its introduction in the loco- 
 motives of that road. 
 
 On the other hand, there are some places where it can be secured more 
 cheaply than coal. 
 
 The question of cost, therefore, depends upon location. 
 
 A great writer upon this subject has said: "We must look for the best 
 results from petroleum, both economically and technically, in those uses 
 where the improved product of the manufactured article more than counter- 
 balances .the difference in price of the two kinds of fuel." 
 
 CHIEF ENGINEER SOLIANI'S MONOGRAPH ON LIQUID FUEL. 
 
 Undoubtedly one of the best articles that has been published on this 
 subject is the paper of Chief Engineer Soliani of the Italian Navy, which 
 was read at the International Engineering Congress. He starts in with the 
 various kinds of petroleum used, gives the chemical composition, what its 
 actual calorific value as fuel is, and then goes on to tell about the experi- 
 ments in Russia, where it was first used on vessels in the Volga region and 
 on the Caspian Sea. He then gives us the pulverizing process adopted by 
 Mr. Urquhardt, and then brings us down to to-day's actual modern experi- 
 ence in the Italian Navy. 
 
 A careful study of this paper shows : 
 
 1st. That the only form of liquid fuel which is absolutely safe for use 
 on board of ship is what is known as petroleum refuse, which is a thick 
 viscous fluid of about the consistency of tar or very thick molasses. This 
 has to be sprayed or pulverized, either by jets of air or steam, for use in 
 the furnaces. 
 
 2d. The pulverizers form the principal element in the whole arrange- 
 ment for burning liquid fuel, and many kinds have been used or tried, or 
 simply patented. The Russian pulverizers are all worked by steam, and 
 they appear to be the best, because a pulverizer using steam may be 
 worked well with air, or any other suitable gaseous fluid with little or no 
 alteration. 
 
 3d. Where pulverizers are not used a compressor for forcing the air is 
 employed. Its great weight and space occupied forms a very serious ob- 
 jection to the compressor. 
 
 4th. That the use of liquid fuel by the Russians is almost confined to 
 the Volga region and the Caspian Sea. There the wood is scarce and costly 
 and also very bulky. Coal is extremely expensive. One very remarkable 
 fact in connection with the use of liquid fuel on Russian vessels is that the 
 difficulty with marine boilers of making up the waste of steam entailed by 
 
 — 38 — 
 
the pulverizers does not exist for the steamers runninjj; along the Volga 
 River. It is lessened, in case of the sea steamers, by the fact that the 
 great bulk of the Caspian trade is from Baku and other ports south to As- 
 trakhan, where fresh water is available in abundance, and can be stored by 
 the steamers both for outward and homeward passages. 
 
 5th. Italy, on account of its position and of its deficiency of coal, was 
 naturally interested in the matter. And that country, which even our 
 naval experts have, in years past, mistakenly reported as having adopted 
 this fuel for its war vessels, confines the practice to a few torpedo boats. 
 For their large vessels they do not contemplate the regular use of liquid 
 fuel. Pulverizers, however, are fitted in order that they may be held in 
 readiness for the same object as forced draft. 
 
 6th. The system of mixing petroleum spray with the coal seems to be 
 on the increase in the French and Italian navies, and furnishes a ready 
 means of rapidly increasing the steam pressure and speed, above that of 
 the natural draft. 
 
 7th. That the measure of success in the burning of liquid fuel will 
 depend upon the efficiency and durability of the pulverizer. Less than 
 three years ago the Italians believed that they had solved this question for 
 naval purposes by the invention of the Curriberti atomizer. They are now 
 rather doubtful about this sprinkler satisfying all their wants. The French, 
 who are following them more closely than any other nation, are about to 
 use their own pulverizers. 
 
 There is no one who has made a more protracted and scientific inves- 
 tigation of its capabilities than Mr. Isherwood, and this is the result of his 
 observations on liquid fuel as a combustible for naval purposes. In sum- 
 marizing the work of the Experimental Board, of which he was president, 
 he writes: 
 
 "The experiments in question embrace those made with Col. Foote's 
 apparatus at the Charleston Navy Yard, and those made with other appa- 
 ratus on different boilers in the New York Navy Yard, all of them, I believe, 
 of considerable value, but never reported in full with the exception of one 
 made about ten years ago, and which is now on the files of the Bureau of 
 Steam Engineering. In every case the patentees abandoned the trials before 
 they were completed, owing to the failure of their apparatus. 
 
 "The liquid oil has, in all cases, to be transformed into oil gas before 
 it can be burned. This transformation can be made by the direct applica- 
 tion externally of heat to the liquid, but the temperature of the oil on 
 the vaporizing surface is higher than the temperature required to de- 
 compose it, the result being deposition of solid carbon in the form of coke 
 which soon fills the vaporizing vessels and renders them useless. This 
 coke is frequently so hard that cold chisels can scarcely detach it, and if 
 thrown into a fire even in small fragments, it burns with excessive slow- 
 ness, like graphite. Whenever the vaporizing vessel is subjected to a high 
 temperature like that of a boiler furnace, the decomposition of the oil and 
 deposition of coke go rapidly on, so that in the course of a few hours any 
 vessel of practical size is filled by it. All apparatus exposed to anything 
 like furnace or flame temperature will inevitably fail from these causes in 
 the future as they have in the past. To make trials with such devices will 
 
 — 39 — 
 
merely serve to confirm this fact. Tlie smaller the vaporization vessel, and 
 the higher the temperature to which it is exposed, the more quickly will it 
 fail." 
 
 INSTALLATION OF THE SYSTEM AT THE CHICAGO EXPOSITION. 
 
 At the World's Fair at Chicago the boilers which furnished the steam 
 for driving the machinery were all fed with crude oil. The conditions there 
 were, of course, quite different from what would prevail aboard ship, but 
 they were all in favor of a more successful burning of the liquid fuel. Lake 
 Michigan with its supply of fresh water was near. There was no question 
 of either weights or space occupied to be taken into consideration. The 
 seven representative boiler firms which were pitted against each other sent 
 excellent men to look out for their respective plants. The piping was ar- 
 ranged in the most efficient manner, it not being necessary to make extra 
 bends or angles in order that it would clear a hatch or opening, as might 
 occur on board ship. And yet an official report says, "The quantity of pe- 
 troleum used for firing the main boiler plant at the World's Columbian Ex- 
 position amounted to upwards of 31,000 tons, and the work done is stated 
 to have totalled 32,316,000 horse power hours. This makes the consump- 
 tion of oil about 2.1 pounds per horse power hour." This report would 
 tend to dispose of some of the claims of the thermal efficiency of liquid 
 fuel. Is it possible that the commercial article is not so rich in hydrogen as 
 that furnished for experimental purposes? 
 
 From time to time we hear of the success attained by one of the Italian 
 cruisers on a short run with this fuel. A careful investigation invariably 
 shows, that when oil was used in connection with coal, the speed over that 
 of natural draft was increased. There is not one single instance on record 
 where the burning of liquid fuel, either alone or in combination with coal, 
 developed the speed of horse power that was secured with coal under forced 
 draft. 
 
 For the past year, the Austrians have been experimenting with it. It 
 is said that for every pound of residuum they were able to burn, seven - 
 tenths of a pound of water in the form of steam was required to spray it. 
 They have not yet been convinced of its merits for naval purposes, for not 
 a single boat in the Austrian service has yet been fitted permanently with 
 atomizers for burning this fuel. 
 
 A careful reading of the professional papers in regard to the success of 
 the French with this combustible furnishes one with such information as 
 the following: "The question is altogether in a state of tentative experi- 
 ment, and the fuel will have to be tried in different boilers and under se- 
 vere conditions before adoption in large vessels." Of another vessel it is 
 written: "The results are said to be good, but not definite." Concerning 
 three torpedo boats it is written: "The experiments have been more or less 
 successful." 
 
 Capt. A. M. Hunt, formerly of the U. S. N., read an exhaustive paper 
 before the Technical Society of the Pacific Coast, October 5th, 1894, on the 
 results obtained from oil at the Mid-Winter Fair, from which the following 
 extracts are taken : 
 
 A certain amount of eye training is necessary to judge whether or not 
 the oil is being burned so as to give the maximum heating effect.. With 
 
 — 41 — 
 
proper manipulation of the burner, it being of proper design, and a careful 
 regulation of the air, an almost flameless combustion can be obtained. The 
 furnace should never be filled with an opaque, luminous flame, although 
 many so-called practical oil men claim that such a combustion will give the 
 best results as regards evaporation. 
 
 The best results at the Fair were always obtained by so manipulating 
 the burner, with the air full on, as to get a blue, Bunsen- burner- like flame, 
 and then shutting off steam and air until a tinge of luminosity began to show, 
 chasing through the furnace in waves. Under such conditions the carbon 
 in the oil is being entirely consumed, and the air supply is being limited 
 just to the point necessary for its consumption. Luminosity indicates the 
 presence of unconsumed carbon, and consequent failure to obtain the full 
 heating effect. After the furnace once becomes thoroughly heated there 
 should be absolutely no evidence of smoke issuing from the chimney. 
 
 The flame must not be allowed to impinge directly against the iron of a 
 boiler. Overheating of the metal is apt to be the result. If a solid particle 
 or drop of the oil strikes the comparatively cold metal the volatile matter is 
 driven off and a carbon deposit left, which, becoming incandescent, and 
 being in direct contact with the iron, burns it. 
 
 At the Mid- Winter Fair there was a chance to determine the efficiency of 
 oil as fuel, and the results of several of the tests conducted by Mr. E. C. 
 Meier, assistant in charge of the boiler plant, and the author, are appended. 
 In these tests both the feed water and the oil were measured by Worthington 
 meters, and while meter tests are always regarded with great suspicion by 
 engineers, these tests were so conducted as to be quite reliable. 
 
 Before any tests were made the feed water meter was thoroughly cali- 
 brated by weighing the water passed through it. At first it was found im- 
 possible to get concordant results from different sets of weighings, especially 
 when the temperature of the feed water was high. A pressure gauge was 
 finally placed on the boiler side of the meter, and the discharge valve pass- 
 ing water into the weighing barrels, set so as to maintain on the meter the 
 ordinary boiler pressure, and the pump run at a speed which furnished feed 
 water at the rate required for the boilers under test. It was found, after so 
 doing, that the results of different sets of calibrations did not vary more than 
 two-tenths of a pound per cubic foot registered. This was as close as the 
 limit of accuracy of the scales. 
 
 The oil meter was calibrated in, the same manner. This meter was 
 provided with small vents to enable any gas which might collect at the top 
 of meter chambers to be removed. Great care was taken to avoid any 
 chance for errors. The blow lines were blanked, and feed valves so ar- 
 ranged that no feed water could pass into boilers not in use. 
 
 The thermometers and steam gauges used were corrected by standards. 
 The only tests for dryness of the steam were made with an ordinary barrel 
 calorimeter, such as Thurston describes, and the results showed the steam 
 to be practically dry. 
 
 The average result of all the tests made was 14.2 pounds of water 
 evaporated from and at 212 degrees Fahrenheit per pound of oil, and the 
 highest evaporation of any test is 15.13 pounds to one. 
 
 It is a very common thing to hear oil men say that they have obtained 
 
 — 42 — 
 
an evaporation of 17 and even 18 pounds of water per pound of oil, and 
 you will find recorded the results of tests showing such evaporations, at- 
 tested by all the details of columns of figures and calculations. There is 
 suspicion that the oil used in such tests must have been thinned down with 
 liquified hydrogen, or that the experimenter deceived himself, willfully or 
 otherwise. 
 
 The theoretical evaporation of oil is about 20.7 pounds to one. An 
 evaporation of 18 to one would indicate a boiler efficiency of about 87 per 
 cent, and assuming a furnace temperature of 2,400 degrees Fahrenheit, 
 the temperature of the issuing gases would be 312 degrees. If the temper- 
 ature of the issuing gases was 450 degrees, as would be more probable, the 
 furnace temperature would be 3,461 degrees, rather too high for comfort. 
 
 The results of certain tests made by the Edison Light and Power Com- 
 pany, of San Francisco, Cal., were as follows: 
 
 Evaporation with California oil 13.1 pounds to 1 
 
 " " Peru oil 12.1 " to 1 
 
 " White Ash coal 6.68 " to 1 
 
 The California oil used weighed 320 pounds to the barrel. The Peru 
 oil used weighed 294 pounds to the barrel. 
 
 1 pound of California oil = 1.96 pounds of coar. . 
 1 pound of Peru oil = 1.81 pounds of coal. 
 
 Accepting the results at the Mid -Winter Fair, an evaporation of 15 to 1 
 can be obtained with oil, using the Heine boilers. 
 
 In January, 1895, a series of tests were made with crude oil on Heine 
 boilers at the Harrison Street station of the Chicago Edison Company, with 
 the following average results: 
 
 Size of boiler 500 
 
 Lbs. of water per lb. oil from and at 212" 14.57 
 
 H. P. developed 593 
 
 Per cent, over rating 18.6 
 
 For fuel purposes two kinds of oil are used, crude petroleum, usually 
 from Lima, O., and residuum after distilling off the lighter oils. 
 
 The Lima crude petroleum oil comes to this (St, Louis) market in tank cars 
 holding 6000 gallons. The price is 1.8 cents per gallon, to which must be added 
 $5.00 per car for switching, etc. Even under favorable conditions, there- 
 fore, as to location of boiler plant, the cost of this oil delivered to the boiler 
 will be at least 2 cents per gallon. A gallon of this oil weighs 6.9 lbs. The 
 theoretical heat value of this oil is about 20,000 heats units, equivalent to a 
 theoretical evaporation of 20.7 lbs. of water. Assuming an efficiency of 80 
 per cent., the evaporation in practice would be 16.56 lbs. of water per pound 
 of oil. The cost of evaporating 1000 lbs. of water would therefore be 17.54 
 cents. With a bituminous coal giving an evaporation in practice of 5 lbs. of 
 water per pound of coal and costing ^1.25 per ton, the same work could be 
 done for 12.5 cents, a difference in favor of the coal of 40.32 per cent. It 
 will be observed also that the conaitions assumed in this calculation are 
 especially favorable to the oil. 
 
 The fuel oil or residuum weighs about 7.3 lbs. per gallon, and has a 
 calorific power of 16,880, or a theoretical evaporation of 17.47 lbs. water 
 
 — 43 — 
 
per pound of oil. At 3 cents a gallon and under the conditions assumed 
 above the cost of evaporating 1000 lbs. of water would be 29.28 cents or 134 
 per cent, more than when using the coal. W. B. P. 
 
 From these varying statements it is clear that local conditions must de- 
 cide when liquid fuel can be used to advantage. — F. i. at the World's Col- 
 umbian Exposition at Chicago, more than 25,000 H. P. of boilers are bemg 
 run by fuel oil piped there from Lima, O. Aside from the saving in dust, 
 noise, soot and ashes — made apparent by the white uniforms of the stokers 
 and the white boiler fronts — it would be an impossibility to bring in coal and 
 carry off ashes for this huge plant without seriously interfering with the 
 passenger traffic. It would require eighty cars for coal and twenty for ashes 
 daily. E. D. M. 
 
 300 H. P. Heine Boiler being moved. 
 
 FUEL GAS. 
 
 Gaseous Fuel has so many apparent practical advantages over any other 
 form of fuel, that it may be properly regarded as the ideal fuel. Near Pitts- 
 burgh, and in some favored districts of hidiana, Natural Gas has been found 
 in such quantities that — for some years at least — immense manufacturing in- 
 dustries have been based on it. Manufacturers who have once realized its 
 advantages are loth to surrender them and would gladly welcome some kind 
 of artificial gas to take its place — if this can be made cheap enough to com- 
 pete with the local coal, hiventors have been prolific of processes and de- 
 vices to fill this demand. 
 
 As there are certain fixed and well defined conditions on which the fuel, 
 value of such gases depends, we give below extracts from papers on the 
 subject by well known experts, which will enable the careful engineer to es- 
 timate in each particular case pretty closely whether gas may be economi- 
 cally substituted for coal. 
 
 — 44 — 
 
Mr. Emerso)i McMillin, in October, 1887, made an exhaustive investi- 
 gation of the subject of fuel gas from which we extract the following : 
 
 "The relative calorific value of the various gases now in use for heat- 
 ing and for illumination have been frec]uently published, yet, in the discus- 
 sion of this subject we cannot well avoid a reproduction of some of the 
 figures. 
 
 " Notwithstanding the fact that tables of this character have been so 
 often published, we are all more or less confused occasionally by seeing 
 statements made that make the comparison totally different from our pre- 
 conceived ideas as to their relative calorific values. 
 
 " This confusion occurs from the fact that at one time we see the com- 
 parison of the gases made by weight, and at another time the comparison is 
 made by volume. We present here the comparison made both by weight 
 and by volume, and shall use natural gas as the unit of value in both com- 
 parisons : 
 
 Table No. 21. 
 Relative Values. 
 
 By Weight. By Volume. 
 
 Natural gas 1,000 1,000 
 
 Coal gas 949 666 
 
 Water gas 292 292 
 
 Producer gas 76.5 130 
 
 *' The water gas rated in the above table — as you will understand — is 
 the gas obtained in the decomposition of steam by incandescent carbon, and 
 does not attempt to fix the calorific value of illuminating water gas, which 
 may be carbureted so as to exceed, when compared by volume, the value of 
 coal gas. 
 
 Table no. 22. 
 Composition of Gases. 
 
 Natural Gas. 
 
 Hydrogen 2.18 
 
 Marsh gas 92.60 
 
 Carbonic oxide 0.50 
 
 defiant gas 0.31 
 
 Carbonic acid 0.26 
 
 Nitrogen 3.61 
 
 Oxygen 0.34 
 
 Water vapor 0.00 
 
 Sulphydric acid 0.20 
 
 VOLUME. 
 
 
 Coal Gas. Water Gas. 
 
 Producer Gas 
 
 46.00 45.00 
 
 6.00 
 
 40.00 2.00 
 
 3.00 
 
 6.00 45.00 
 
 23.50 
 
 4.00 0.00 
 
 0.00 
 
 0.50 4.00 ' 
 
 1.50 
 
 1.50 2.00 
 
 65.00 
 
 0.50 0.50 
 
 0.00 
 
 1.50 1.50 
 
 1.00 
 
 
 
 
 
 100 00 100.00 100.00 100.00 
 
 — 45 — 
 
Table no. 23. 
 Composition of Gases. 
 
 Natural Gas. 
 
 Hydrogen 0.268 
 
 Marsh gas 90.383 
 
 Carbonic oxide 0.857 
 
 defiant gas 0.531 
 
 Carbonic acid 0.700 
 
 Nitrogen 6.178 
 
 Oxygen 0.666 
 
 Water vapor 000 
 
 Sulphydric acid 0.417 
 
 WEIGHT. 
 
 
 Coal Gas. 
 
 Water Ga.s. 
 
 Producer Gas. 
 
 8.21 
 
 5.431 
 
 0.458 
 
 57.20 
 
 1.931 
 
 1.831 
 
 15.02 
 
 76.041 
 
 25.095 
 
 10.01 
 
 0.000 
 
 0.000 
 
 1.97 
 
 10.622 
 
 2.517 
 
 3.75 
 
 3.380 
 
 69.413 
 
 1.43 
 
 0.965 
 
 0.000 
 
 2.41 
 
 1.630 
 
 0.686 
 
 100.000 100.000 100.000 100.000 
 
 " Some explanations of these analyses are necessary. The natural gas 
 is that of Findlay, O. The coal gas is probably an average sample of coal 
 gas, purified for use as an illuminant. The water gas is that of a sample of 
 gas made for heating, and consequently not purified, hence the larger per 
 cent, of CO2 that it contains. 
 
 "Since calculating the tables used in this paper, I am satisfied that the 
 sample of water gas is not an average one. The CO is too high, and H is 
 too low. Were proper corrections made in this respect, it would increase the 
 value in heat units of a pound, but not materially change the value when 
 volume is considered, and as that is the way in which gases are sold, the 
 tables will not be recalculated. 
 
 " The producer gas is that of an average sample of the Pennsylvania 
 Steel Works, made from anthracite, and is not of so high grade as would be 
 that made from soft coal. 
 
 "The natural gas excels, as shown in Table 21, because of the large per 
 cent, of marsh gas. In no other form, in the gases mentioned, do we get so 
 much hydrogen in a given volume of gas. 
 
 " It is the large per cent, of hydrogen in the coal gas that makes it so 
 nearly equivalent to the natural gas in a given weight, but much of the hy- 
 drogen in coal gas being free, makes it fall far short of natural gas in calorific 
 value per unit of volume. 
 
 "A further comparison of the value of the several gases named may be 
 made by showing the quantity of water that would be evaporated by 1000 
 feet of each kind of gas, allowing an excess of 20 per cent, of air, and 
 permitting the resultant gases to escape at a temperature of 500 degrees. 
 This sort of comparison probably has more practical value than either of the 
 others that have been previously given. We will assume that the air for 
 combustion is entering at a temperature of 60 degrees. 
 
 Table No. 24. 
 
 Water Evaporation. 
 
 Natural Gas. Coal Gas. Water Gas. Producer Gas 
 
 Cubic feet gas 1000 1000 1000 1000 
 
 Pounds water 893 591 262 115 
 
 — 47 — 
 
'■' The theoretical temperature that may be produced by these several 
 gases does not differ greatly as between the three first-named. The pro- 
 ducer gas falls about 25 per cent, below the others, giving a temperature of 
 only 3441° F. 
 
 " Water gas leads in this respect, with a temperature of 4850°. 
 
 "A comparison of the resultant products of combustion also shoWs water 
 gas to possess merit over either natural or coal gas, when the combustion of 
 equal quantities — say 1000 feet — is considered. An excess of 20 per cent, 
 of air is calculated in the following table : 
 
 Table No. 25. 
 
 Resultant Gases of Combustion. 
 
 Natural Coal Water Producer 
 
 Quantity— 1000 ft. Gas. Gas Gas. Gas. 
 
 Weight of gas before combustion, lbs 45.60 32.00 45.60 77.50 
 
 Steam 94.25 69.718 25.104 6.92 
 
 Carbonic acid 119.59 68.586 61.754 36.45 
 
 Sulphuric acid 0.36 -_- 
 
 Nitrogen 664.96 427.222 170.958 126.57 
 
 Total weight after combustion 879.16 565.526 257.816 169.94 
 
 Pounds oxygen for combination 167.46 107.961 43.149 19.67 
 
 " You will observe, by the following table, that, with the exception of 
 producer gas, each kind gives off nearly one pound of waste gases for each 
 pound of water evaporated. This quantity includes 20 per cent, excess of air; 
 
 Table No. 26. 
 
 Weights of Water Evaporated and Resultant Gases. 
 
 Natural Coal Water Producer 
 
 Gas. Gas. Gas. Gas. 
 
 Weight of water evaporated 893.25 591.000 262.000 115.100 
 
 Weight of gases after combustion --879. 16 665.526 257.816 169.945 
 
 " The vitiation of the atmosphere per unit of value in water evaporation 
 is practically the same in water gas as in natural gas. 
 
 " However, the excess of oxygen does no harm, and the steam and 
 nitrogen can not be regarded as very objectional products. The gas that 
 robs the air permanently of the most oxygen, and produces the greatest 
 quantity of carbonic acid per unit of work, must be classed as the most 
 objectionable from a sanitary standpoint. 
 
 Table No. 27. 
 
 Oxygen Absorbed and Carbonic Acid Produced. 
 
 In Combustion. Natural Coal Water Producer 
 
 Gas. Gas. Gas. Gas. 
 
 Pounds of oxygen absorbed per 100 lbs. water 
 
 evaporated 18.75 18.27 16.47 17.96 
 
 Pounds of CO2 produced per 100 lbs. water 
 
 evaporated 13.40 11.60 23.57 31.70 
 
 Oxygen absorbed plus CO2 produced 32.15 29.87 40.04 49.66 
 
 " Here, then, it is shown that if pollution by carbonic acid and the 
 impoverishment by the absorption of oxygen are equally deleterious to the 
 atmosphere, coal gas stands at the head as being the least objectionable." 
 
 Mr. McMillin then goes into an elaborate calculation of a mixture of 
 gases, which would combine the good qualities of the three artificial gases 
 compared, which he finds to be "in per cent., coal gas 20.35, water gas 
 32.17, producer gas 47.48." 
 
 — 48 — 
 
After calculating the cost of such gas, he proceeds : 
 
 "Here we may note some features, that to my mind are interesting; 
 that is, the cost of various gases per 1,000,000 units of heat which they are 
 theoretically capable of producing. 
 
 " In working out these figures I put wages, repairs and incidentals and 
 the cost of the ton of good gas coal at ^2.00, and a ton of hard coal or coke 
 at the same price, and the quantities of production as follows: Coal gas 
 from soft coal, 10,000 feet ; water gas from hard coal, 40,000 feet; and pro- 
 ducer gas, 150,000 feet. 
 
 TABLE No. 28. 
 
 Cost per 1,000,000 Units of Heat. 
 
 Coal gas 734,976 units, costing 20.00 cents = 27.21 cents per mill. 
 
 Water gas 322,346 units, costing 10.88 cents = 33.75 cents per mill. 
 
 Producer gas---117,000 units, costing 2.58 cents = 22.05 cents per mill. 
 Our mixture---323,115 units, costing 7.88 cents = 24.39 cents per mill. 
 
 "Thus it will be seen that after all coal gas costs but 11.6 per cent, 
 more per unit of heat than the mixture that we have worked out, while 
 water gas, per unit of heat, costs 38.38 per cent, more than the mixed 
 product." 
 
 After a discussion of methods of delivery and the various uses for the 
 fuel gas, he concludes : 
 
 "The demand for fuel gas, like the demand for electric light, has come 
 to stay. It will not down. Scientific investigators, as well as the public, 
 insist that there ought to be, and must be, a change in the mode of domestic 
 and industrial heating. Our present systems are not in keeping with the 
 progress of the nineteenth century." 
 
 Professor D. S. Jacobus — Oct., 1888 — says: "It is proposed to give an 
 estimate of the cost at which carbureted and uncarbureted water gas will 
 have to be sold in order to compete successfully for steam boiler use with 
 anthracite coal. 
 
 " The following are analyses of the gas direct from the generator, and 
 of the same after it has been carbureted for illuminating purposes : 
 
 TABLE NO. 29. 
 
 Analyses of Water Gas. 
 
 Percent by Volumes. 
 
 1. II. 
 
 Uncarbureted. Carbureted. 
 
 Nitrogen 4.69 2.5 
 
 Carbonic acid 3.47 .3 
 
 Etliyiene .0 12.5 
 
 Oxygen .0 .2 
 
 Benzole vapor .0 1.5 
 
 Carbonic oxide 36.80 29.0 
 
 Marshgas 2.16 24.0 
 
 Hydrogen 52.88 30.0 
 
 100.00 100.00 
 — 49 — 
 
"Experiments were made to verify the ratio between the heats of com- 
 bustion of the gas before and after being carbureted, by determining the 
 time and quantity of gas required to evaporate a given weight of water con- 
 tained in an open vessel, heating by means of a gas stove. The burner of 
 the stove used for burning the carbureted gas caused air to be mingled with 
 the gas before the latter was burned, thus producing a colorless flame. For 
 the uncarbureted gas, the burner was of the Argand pattern, and the air 
 was not mingled with the gas before it was burned. The results of the tests 
 are given in the following table : 
 
 TABLE NO. 30. 
 
 GAS 
 
 Uncarbureted 
 Uncarbureted 
 Carbureted-- 
 Carbureted-- 
 Carbureted ^- 
 
 Lbs. 
 
 B 
 
 O VI 
 
 £^ 
 
 O't- 
 
 £§■ 
 
 3 <U 
 
 Deg. F. peg. F. 
 
 56 
 59 
 56 
 59 
 68 
 
 61 
 62 
 61 
 62 
 66 
 
 
 a; C 
 
 CU 
 
 Inches. Min. 
 
 4 
 4 
 
 12 
 
 10 
 8i 
 
 > 
 
 3 O" 
 
 
 
 
 
 M 
 
 
 
 ,^ 
 
 
 
 o 
 
 
 
 
 
 
 0) 
 
 
 
 
 
 
 
 
 
 u 
 
 
 
 
 
 <L) 
 
 3 
 
 
 
 
 
 # 
 
 o 
 
 
 
 
 
 
 .Q 
 
 C 
 
 
 F 
 
 3 
 
 
 3 
 
 
 
 Z 
 
 
 O- <M .^ 
 
 *r <u -a 
 
 Cu. ft. I Lbs. 
 
 79.^ 
 
 79i 
 
 69 
 
 73i 
 
 63 
 
 36.1 
 34.8 
 19.4 
 
 18.2 
 19.8 
 
 4.64 
 4.64 
 4.64 
 4.64 
 4.60 
 
 Per 1000 cu. 
 ft. gas. 
 
 Lbs. 
 
 128.5 
 133.3 
 239.2 
 254.9 
 232.8 
 
 "From this table we obtain an average evaporation, per 1000 cubic 
 feet of uncarbureted gas, of 130.9 lbs. of water from the temperature of 
 212° and at atmospheric pressure, and for the carbureted gas an average of 
 242.1 lbs. That is, the experiments tend to show that the ratio of the 
 calorific power of the uncarbureted to that of the carbureted gas, by volume, 
 is -13^ = 54 
 
 ^^ 242.1 ^•^'^• 
 
 "The volume of one pound of air at 62° F. is 13.14 cubic feet, hence 
 the calorific power of the gases per cubic foot should be : 
 
 Uncarbureted ^^gg^^ = 283.3 H. U. 
 
 Carbureted .'J«2g^ = 640.5 H. U. 
 
 13.14 
 
 " One pound of good Lackawanna coal has a calorific power of 13000 
 heat units. The number of cubic feet of gas required to produce the same 
 heating effect as is produced in burning one ton of coal will therefore be : 
 
 Uncarbureted gas 
 
 13000X2000 
 283.3 
 
 91780. 
 
 Carbureted gas 13000x2000 _ 49590. 
 
 "The efficiency of a boiler will be about the same when burning gas 
 for fuel as when coal is used. (?) If, therefore, we disregard the difference 
 in the cost of attendance, in favor of using gaseous fuel, 40590 cubic feet of 
 carbureted, or 91780 cubic feet of uncarbureted gas, must be sold for the 
 same price as one (short) ton of coal, in order to successfully compete with 
 the latter for use under steam boilers. 
 
 50 
 
"We will estimate the probable excess of cost involved in firing with 
 
 coal above that of gas-firing. In burning natural gas, it has been found that 
 
 one man is able to attend to boilers aggregating 1500 horse-power, whereas, 
 
 if coal is used, 200 horse-power will be a fair figure. It therefore requires, 
 
 in the case of large plants, only about j2_ as much labor to f.re with gas as 
 
 is involved in firing with coal. If the wages of firemen are $2.50 per day of 
 
 twelve hours, the cost of firing one ton of coal in boilers that require four 
 
 pounds of coal per boiler horse-power per hour, will be 
 
 2.5X2000 , ,1 .o -, 
 
 . — dollars = 52.1 cents. 
 
 12X200X4 
 The cost of firing with gas would be -^^ of this amount so that the extra 
 cost of firing with coal would equal -if times 52.1 equal 45 cents. To make 
 a liberal allowance in favor of the gaseous fuel we will assume that the 
 extra labor of firing each ton of coal costs 50 cents. 
 
 *' The following table contains the prices at which the gas must be sold 
 per 1000 cubic feet in order to be as cheap as coal for boiler use ; first, dis- 
 regarding the difference in the cost of attendance, and secondly, assuming 
 that the extra cost of firing with coal is 50 cents per ton. 
 
 Table No. 31. 
 
 Cost of Burning Water Gas. 
 
 
 PRICE OF GAS PER 1000 CUBIC FEET. 
 
 Cost of Coal Delivered to 
 
 
 
 Boiler Room. 
 
 Not Including- Difference in 
 Cost of Attendance. 
 
 Including Difference in 
 Cost of Attendance. 
 
 Per Ton of 2000 Lbs. 
 
 
 
 
 
 
 Carbureted. 
 
 Uncarbureted. 
 
 Carbureted. 
 
 Uncarbureted. 
 
 $6.00 
 
 14.8 cts. 
 
 6.5 cts. 
 
 16.0 cts. 
 
 7.1 cts. 
 
 5.00 
 
 12.3 cts. 
 
 5.4 cts. 
 
 13.6 cts. 
 
 6.0 cts. 
 
 4.00 
 
 9.9 cts. 
 
 4.4 cts. 
 
 11.1 cts. 
 
 4.9 cts. 
 
 3.00 
 
 7.4 cts. 
 
 3.3 cts. 
 
 8.6 cts. 
 
 3.8 cts. 
 
 2.00 
 
 4.9 cts. 
 
 2.2 cts. 
 
 6.2 cts. 
 
 2.7 cts. 
 
 1.00 
 
 2.5 cts. 
 
 1.1 cts. 
 
 3.7 cts. 
 
 1.6 cts. 
 
 ''As the cost of manufacturing the uncarbureted gas, by the present 
 processes, not including interest on capital invested, is from 10 to 20 cents 
 per 1000 cubic feet, it does not appear possible to employ it economically 
 for a boiler fuel, until considerable reduction in cost of production shall have 
 been made." 
 
 Professor Wm. B. Potter, March, 1892, says: 
 
 " The convenience and economy attending the use of natural gas in a 
 number of localities in this country have led many people to believe that 
 fuel gas, made from coal at large central stations, and distributed to factories 
 and works, is the fuel of the future which will not only clear all chimneys 
 but reduce all fuel bills as well. While it is unquestionably true that fuel 
 gas is especially adapted for household use and will play an important part 
 in the future for such use, it is equally true that as a fuel for raising steam 
 it can never compete in the matter of economy with coal directly applied. 
 At several establishments where gas is employed for certain industrial heat 
 requirements attempts have been made to use the gas under boilers; at 
 first glowing reports were circulated indicating a saving over coal of 20 % 
 
 — .f^9, — 
 
and even 33A<^. A little experience has always shown, however, not only 
 that such results are not attained, but that the cost of the gaseous fuel is so 
 much in excess of coal used directly as to make it necessary to return to the 
 latter system. 
 
 " The following simple calculation will serve to show the uselessness of 
 all attempts to convert bituminous coal into gas and distribute it to boiler 
 plants. 
 
 "The average quality of fuel gas made from a trial run of several car 
 loads of Illinois coal in a well-designed fuel gas plant showed a calorific 
 value of 243,391 heat units per 1000 cubic feet of gas or 10,105,594 heat 
 units per ton of coal. This is equivalent to 5052.8 heat units per pound of 
 ■coal, whereas, by direct calorimeter test an average sample of the coal gave 
 11,172.6 heat units, or an efficiency of 45.2%. 
 
 " One pound of the coal by direct application showed a theoretical 
 evaporation of 11.56 lbs. of water. 
 
 " The gas from one pound of the coal showed a theoretical evaporation 
 •of 5.23 lbs. water. 
 
 "48.17 pounds of the coal were required to furnish 1000 feet of the gas. 
 
 " Taking the efficiency in the use of the coal direct at 50%, 
 
 " Taking the efficiency in the use of the gas direct at 90%, 
 
 " Taking the cost of the coal at 6 cents per bushel, 
 
 " Taking the cost of the gas at 8 cents per 1000 cubic feet, 
 we have as the cost of evaporating 1000 lbs. of water by coal directly 
 applied : 
 
 " tVo of 11.56 = 5.78 lbs. of water to be evaporated in practice by 
 1 lb. of coal. 
 
 " i^oji) = 173 lbs. of coal to evaporate 1000 lbs. of water ; 173 lbs. of 
 coal at 6 cents per bushel = 13 cents, and as the cost of the same coal con- 
 verted into gas and applied, 
 
 " "iVo of 5,23 = 4.71 lbs. of water to be evaporated in practice by gas 
 from 1 lb. of coal. 
 
 *' ijO„o_o ^ 212.3 lbs. of coal required = 4400 cubic feet of gas; 4400 
 ■cubic feet of gas at 8 cents per 1000 = 35.2 cents. 
 
 " It will be observed that the conditions assumed are especially favorable 
 to the gas, the cost being placed at the remarkably low figure of 8 cents per 
 1000 cubic feet, which is about the actual cost of manufacture and distribu- 
 tion upon a large scale, and a very high efficiency is taken. Notwithstanding 
 all this the coal used directly shows an advantage of over 170%." 
 
 Note : Prof. Potter's remarks are based on conditions found in St. Louis and 
 adjacent territory. 
 
 Natural Gas, is variously constituted, and hence the estimates of its 
 heating power vary. 
 
 Experiments in Pittsburgh show 1000 cubic feet of natural gas in actual 
 efficiency under boilers equal to from 80 to 133 pounds coal. The coal 
 varies from 12000 to 13000 B. T. U. per pound ; hence say 1,000,000 to 
 1,200,000 B. T. U. per 1000 feet of natural gas. 
 
 A Committee of the Western Society of Engineers of Pittsburgh, report 
 1 lb. good coal = 7^ cubic feet natural gas. 
 
 — 53 — 
 
When burnt with just enough air its temperature of combustion is 
 4200° F, The Westinghouse Brake Co. in Pittsburgh found that with the 
 best grade of Youghiogheny coal they could evaporate 10.38 lbs. water, and 
 with the same boiler 1.18 feet natural gas evaporated 1 lb. water. They con- 
 clude that 1 lb. Youghiogheny coal = 12r| lb. natural gas, or 1000 cubic 
 feet natural gas = 81.6 lb. coal. 
 
 The Indiana natural gas gives 1,100,000 B. T. U. for 1000 cubic feet 
 and weighs 0.045 lbs. per cubic foot. 
 
 The analyses compare as follows : 
 
 Table no. 32. 
 
 Analyses of Natural Gas. 
 
 Pittsburgh, Pa., Gas. 
 
 Hydrogen 22.0 
 
 Marsh gas 67.0 
 
 Carbonic oxide 0.6 
 
 defiant gas 1.0 
 
 Carbonic acid 0.6 
 
 Nitrogen 3.0 
 
 Oxygen 0.8 
 
 Ethylic hydride 5.0 
 
 Sulphuretted hydrogen 
 
 lOOO 
 
 indlay, Ohio, Gas 
 
 2.18 
 
 92.61 
 
 0.26 
 
 0.30 
 
 0.50 
 
 3.61 
 
 0.34 
 
 0.20 
 
 100.00 
 
 500 H. P. Heine Boiler ready for transportation. 
 — 54 — 
 
WATER. 
 
 Pure water at 62° F. weighs 62.355 pounds per cubic foot, or 8^- pounds 
 per U. S. gallon ; 7.48 gallons = 1 cubic foot. It takes 30 pounds or 3.6 
 gallons for each horse-power per hour. It would be difficult to get at the 
 total daily horse-power of steam used in the U. S., but it reaches into the 
 billions of gallons of feed water per day. 
 
 The importance of knowing what impurities exist in most feed waters, 
 how these act on a boiler, and how they may be removed is, therefore, 
 patent to every intelligent engineer. 
 
 We give, therefore, the thoughts of some prominent investigators on 
 the subject. 
 
 Prof. Thurston says : 
 
 'Mncrustation and sediment are deposited in boilers, the one by the 
 precipitation of mineral or other salts previously held in solution in the feed- 
 water, the other by the deposition of mineral insoluble matters, usually 
 earths, carried into it in suspension or mechanical admixture. Occasionally 
 also vegetable matter of a glutinous nature is held in solution in the feed- 
 water, and, precipitated by heat or concentration, covers the heating-surfaces 
 with a coating almost impermeable to heat and hence liable to cause an 
 over-heating that may be very dangerous to the structure. A powdery 
 mineral deposit sometimes met witli is equally dangerous, and for the same 
 reason. The animal and vegetable oils and greases carried over from the 
 condenser or feed water heater are also very likely to cause tro2ible. Only 
 mineral oils should be permitted to be thus introduced, and that in minimum 
 quantity. Both the efficiency and the safety of the boiler are endangered 
 by any of these deposits. 
 
 " The amount of the foreign matter brought into the steam-boiler is 
 often enormously great. A boiler of 100 horse-power uses, as an average, 
 probably a ton and a half of water per hour, or not far from 400 tons per 
 month, steaming ten hours per day, and even with water as pure as the 
 Croton at New York, receives 90 pounds of mineral matter, and from many 
 spring waters a ton which must be either blown out or deposited. These 
 impurities are usually either calcium carbonate or calcium sulphate, or a 
 mixture ; the first is most common on land, the second at sea. Organic 
 matters often harden these mineral scales, and make them more difficult of 
 removal. 
 
 "The only positive and certain remedy for incrustation and sediment 
 once deposited is periodical removal by mechanical means, at sufficiently 
 frequent intervals to insure against injury by too great accumulation. 
 Between times, some good may be done by special expedients suited to 
 the individual case. No one process and no one antidote will suffice for all 
 cases. 
 
 — 55 — 
 

 V.i*A' .^*\-'? 
 
 ' Hhp '•mm .'fei'iHi 
 
 ■■ ■! ^ ■ 
 
 ^ — - 
 
 ««,_, — 
 
 htTM 
 
 W^ 
 
 Ll-il 
 
 CL^' 
 
 CPH 
 
 ■pm 
 
 ^•/'Tri' 
 
 ^p-T— 
 
 r r— ■ 
 
 IBV- 
 
 rf-iM |pp» 
 
 '""-I ;""! — 1 IBT^ 
 
 "* '*-*^^ ■^ 
 
 ■t-^ 
 
 
 o 
 
 
 03 
 
 . 
 
 >, 
 
 ^ X 
 
 
 ^< 
 
 
 ^H 
 
 TO 
 
 :7= D 
 
 
 
 
 ^t 
 
 X 
 
 §u 
 
 £X 
 
 CJ ^ 
 
 X" 
 
 -p < 
 
 l-Tl 
 
 ^-J 
 
 
 t-^ 
 
 x: 
 
 ■^ -J 
 
 -M 
 
 U < 
 
 ^ 
 
 C/5 
 
 Ti 
 
 
 ci; 
 
 
 a. 
 
 
 Cu 
 
 
 3 
 
 
 cr 
 
 
 m 
 
" Where carbonate of lime exists, sal-ammoniac may be used as a pre- 
 ventive of incrustation, a double decomposition occuring, resulting in the 
 production of ammonium carbonate and calcium chloride — both of which are 
 soluble, and the first of which is volatile. The bicarbonate may be in part 
 precipitated before use by heating to the boiling-point, and thus breaking up 
 the salt and precipitating the insoluble carbonate. Solutions of caustic lime 
 and metallic zinc act in the same manner. Waters containing tannic acid 
 and the acid juices of oak, sumach, logwood, hemlock, and other woods, are 
 sometimes employed, but are apt to injure the iron of the boiler, as may 
 acetic or other acid contained in the various saccharine matters often intro- 
 duced into the boiler to prevent scale, and which also make the lime-sulphate 
 scale more troublesome than when clean. Organic matters should never be 
 used. 
 
 " The sulphate scale is sometimes attacked by the carbonate of soda, 
 the products being a soluble sodium sulphate and a pulverulent insoluble 
 calcium carbonate, which settles to the bottom like other sediments and is 
 easily washed off the heating-surfaces. Barium chloride acts similarly, 
 producing barium sulphate and calcium chloride. All the alkalies are used at 
 times to reduce incrustations of calcium sulphate, as is pure crude petroleum, 
 the tannate of soda, and other chemicals. 
 
 "The effect of incrustation, and of deposits of various kinds, is to 
 enormously reduce the conducting power of heating-surfaces ; so much so, 
 that the power, as well as ^he economic efficiency of a boiler, may become 
 very greatly reduced below that for which it is rated, and the supply of 
 steam furnished by it may become wholly inadequate to the requirements of 
 the case. 
 
 " It is estimated that a sixteenth of an inch (0.16 cm.) thickness of hard 
 * scale ' on the heating-surface of a boiler will caui>e a waste of nearly one- 
 eighth its efficiency, and the waste increases as the square of its thickness. 
 The boilers of steam vessels are peculiarly liable to injury from this cause 
 where using salt water, and the introduction of the surface-condenser has 
 been thus brought about as a remedy. Land boilers are subject to incrusta- 
 tion by the carbonate and other salts of lime, and by the deposit of sand or 
 mud mechanically suspended in the feed-water. 
 
 " It has been estimated that the annual cost of operation of locomotives 
 in limestone districts is increased $750 by deposits of scale." 
 
 We give below an extract from an interesting paper on the " Impurities 
 of Water," contributed by Messrs. Hunt and Clapp, to the transactions of 
 the American Institute of Mining Engineers, for 1888. 
 
 Commercial Analyses. 
 
 By far the most common commercial analysis of water is made to deter- 
 mine its fitness for making steam. Water containing more than five parts 
 per hundred thousand of free sulphuric or nitric acid is liable to cause serious 
 corrosion, not only of the metal of the boiler itself, but of the pipes, cylin- 
 ders, pistons, and valves with which the steam comes in contact. Sulphuric 
 acid is the only one of these acids liable to be present in the water from 
 
 — 57 — 
 
natural sources ; it being often produced in the water of the coal and iron 
 districts, by the oxidation of iron pyrites to sulphate of iron, which, being 
 soluble, is lixiviated from the earth strata, and carried into the strean?-. The 
 presence of organic matter taken up by the water in its after-course, reduc- 
 ing the iron and lining the bottom of the stream with red oxide of iron, and 
 leaving a considerable proportion of the sulphuric acid free in the water. 
 This is a troublesome feature with the water necessarily used in many of 
 the iron districts of this country. The sulphuric acid may come from other 
 natural chemical reactions than the one described above. Muriatic and nitric 
 acids, as well as often sulphuric acid, may be conveyed into water through 
 the refuse of various kinds of manufacturing establishments discharged into it. 
 
 The large total residue in water used for making steam causes the inte- 
 rior linings of the boilers to become coated, clogs their action, and often pro- 
 duces a dangerous hard scale, which prevents the cooling action of the water 
 from protecting the metal against burning. 
 
 Lime and magnesia bicarbonates in water lose their excess of carbonic 
 acid on boiling, and often, especially when the water contains sulphuric acid, 
 produce, with the other solid residues constantly being formed by the evap- 
 oration, a very hard and insoluble scale. 
 
 A larger amount than 100 parts per 100,000 of total solid residue will 
 ordinarily cause troublesome scale, and should condemn the water for use 
 in steam boilers, unless a better supply cannot be obtained. 
 
 The following is a tabulated form of the causes of trouble with water for 
 steam purposes, and the proposed remedies, given by Prof. L. M. Norton, in 
 his lecture on " Industrial Chemistry." 
 
 Brief Statement of Causes of Incrustation. 
 
 1. Deposition of suspended matter. 
 
 2. Deposition of dissolved salts from concentration. 
 
 3. Deposition of carbonates of lime and magnesia by boiling off car- 
 bonic acid, which holds them in solution. 
 
 4. Deposition of sulphates of lime, because sulphate of lime is but 
 slightly soluble in cold water, less soluble in hot water, insoluble above 140'' 
 Centigrade. (284 degrees Fahrenheit.) 
 
 5. Deposition of magnesia, because magnesium salts decompose at 
 high temperature. 
 
 6. Deposition of lime soap, iron soap, etc., formed by saponification 
 of grease. 
 
 Various Means of Preventing Incrustation. 
 
 1. Filtration. 
 
 2. Blowing off. 
 
 3. Use of internal collecting apparatus or devices for directing the cir- 
 culation. 
 
 4. Heating feed water. 
 
 5. Chemical or other treatment of water in boiler. 
 
 6. Introduction of zinc into boiler. 
 
 7. Chemical treatment of water outside of boiler. 
 
 — 58 — 
 
Tabular View. 
 
 Troublesome Substance. 
 
 Sediment, mud, clay, etc. 
 
 Readily soluble salts. 
 
 Bicarbonates of lime, magnesia, 
 iron. 
 
 Sulphate of lime. 
 
 Chloride and sulphate of magne- 
 sium. 
 
 Carbonate of soda in large amounts. 
 
 Acid (in mine waters). 
 
 Dissolved carbonic acid and ox- 
 ygen. 
 
 '/'rouble. 
 Incrustation. 
 Incrustation. 
 
 Incrustation. 
 
 Incrustation. 
 
 Corrosion. 
 
 Priming. 
 
 Corrosion. 
 
 Corrosion. 
 
 Grease (from condensed water). Corrosion. 
 
 Organic matter (sewage). Priming. 
 
 Organic matter. Corrosion. 
 
 Remedy or Pallintion. 
 
 Filtration. 
 Blowing off. 
 
 Blowing off. 
 
 Addition of can!* 
 lime, or magna- 
 
 f Heating feed, 
 j tic soda, 
 I sia, etc. 
 
 ( Addition of carbonate of soda, 
 1 barium chloride. 
 
 / Addition of carbonate of soda, 
 1 e:c. 
 
 / Addition of barium cliloride. 
 \ etc. 
 
 Alkali. 
 
 / Heating feed. Addition of caus- 
 1 tic soda, slacked lime, etc. 
 
 {Slacked lime and filtering. Car- 
 bonate of soda. Substituji 
 mineral oil. 
 
 / Precipitate with alum or ferric 
 1 chloride and filter. 
 
 Ditto. 
 
 The mineral matters causing the most troublesome boiler-scales are b' 
 carbonates and sulphates of lime and magnesia, oxides of iron and alumina, 
 and silica. We present here a table showing the amount and nature of im- 
 purities in feed water in different sections of the United States. (Table 33.) 
 
 Note. The mud drum of the Heine Boiler, surrounded as it is, by water at a 
 temperature of about 350° F., forms a sort of live steam purifier in which a large part 
 of the scale forming salts are precipitated. It is largely on this account that the 
 Heine Boiler is able to work satisfactorily with the most impure waters, where other 
 boilers, lacking the mud-drum-purifier, fail of success altogether. This has bee-i 
 practically demonstrated on many occasions. Probably no "tougher" water is 
 encountered by boiler users anywhere, than in Columbus, Ohio. Heine Boilers sup- 
 planted flue boilers there, that were struggling in vain against scale. The success of 
 the Heine Boiler with this water was a most unqualified one. The L. Hoster Brewing 
 Co. and the Columbus Electric Light and Power Co. both have large plants of 
 Heine Boilers, and we think will cheerfully testify to the superiority of the Heine 
 Boiler in this respect. It is not claimed that NO scale will form in the Heine Boiler 
 when operated with scale producing water. It is only those boilers which have no 
 particular reputation for good service, those boilers that are guaranteed (?) to do 
 anything and everything, that run scaleless on bad water. Eternal vigilance is the 
 price of many things besides liberty and constant watchfulness is necessary if scale 
 is to be avoided in any boiler. But common, every day experience has shown that 
 the conditions which aid in the prevention of scale in boilers are more perfectly pro- 
 vided for in the Heine than in any other type. 
 
 Oil or grease often causes as much trouble in boilers as scale or mud, 
 and is much more difficult to remove, as it cannot be " blown off." It re- 
 quires especial care where a part or the whole of the feed water comes from 
 condensers or from heating coils where exhaust steam is used. 
 
 We reprint a warning given by the oldest boiler insurance company in 
 the United States. 
 
 — 59 — 
 
Table No. 33. 
 Table of Water Analyses. 
 
 Grains per U. S. Gallon, 231 Cubic Inches. 
 
 WHERE FROM. 
 
 Buffalo, N. Y., Lake Erie 
 
 Pittsburgh, Allegheny River 
 
 Pittsburgh, Monongahela River- - 
 
 Milwaukee, Wisconsin River 
 
 Galveston, Texas, 1 
 
 Columbus, Ohio 
 
 Washington, D. C, citysupply-- 
 
 Baltimore, Md., city supply 
 
 Sioux City, la., city supply 
 
 Los Angeles, Cal., 1 
 
 Bay City, Michigan, Bay 
 
 Bay City, Michigan, River 
 
 Cincinnati, Ohio River 
 
 Watertown, Conn 
 
 Ft. Wayne, Ind 
 
 Wilmington, Del 
 
 Galveston, Texas, 2 
 
 Wichita, Kansas 
 
 Los Angeles, Cal., 2 
 
 St. Louis, Mo., well water 
 
 Pittsburgh, Pa., artesian well 
 
 Springfield, 111., 1 
 
 Springfield, 111., 2 
 
 Hillsboro, 111 
 
 Pueblo, Colo 
 
 Long Island City, L. I 
 
 Mississippi River, above Missouri 
 River 
 
 Mississippi River, below mouth of 
 Missouri River 
 
 Mississippi River at St. Louis 
 W. W 
 
 Missouri River above mouth 
 
 5.66 
 
 0.37 
 
 1.06 
 
 6.23 
 
 13.68 
 
 20.76 
 
 2.87 
 
 2.77 
 
 19.76 
 
 10.] 2 
 
 8.47 
 
 4.84 
 
 3.88 
 
 1.47 
 
 8.78 
 
 10.04 
 
 21.79 
 
 14.14 
 
 3.72 
 
 27.04 
 
 23.45 
 
 12.99 
 
 5.47 
 
 14.56 
 
 4.32 
 
 4.0 
 
 8.24 
 
 10.64 
 
 9.64 
 10.07 
 
 Hi 
 
 
 <u 
 
 
 c 
 
 
 w 
 
 
 n( 
 
 
 ? 
 
 
 
 
 
 
 
 
 
 
 
 
 
 a 
 
 <u 
 
 3 
 
 e 
 
 O) 
 
 J 
 
 
 3 
 
 32 
 
 3 
 
 78 
 
 5.12 
 
 4.67 
 
 13 
 
 52 
 
 11 
 
 74 
 
 3 
 
 27 
 
 0.65 
 
 1.24 
 
 5.84 
 
 10.36 
 
 33.66 
 
 0.78 
 
 4.51 
 
 6.22 
 
 0.02 
 
 29.149 
 
 25.91 
 
 12.59 
 
 23.73 
 
 5.71 
 
 7.40 
 
 4.31 
 
 2.97 
 
 16.15 
 
 28.0 
 
 1.02 
 
 7.41 
 
 6.94 
 
 8.92 
 
 0.58 
 0.58 
 0.64 
 1.76 
 
 326.04 
 7.02 
 
 Trace. 
 
 Trace. 
 
 1.17 
 
 3.51 
 
 20,48 
 
 126.78 
 1.79 
 1.76 
 3.51 
 4.29 
 
 398.99 
 24.34 
 
 15.57 
 18.41 
 1.97 
 1.56 
 2.39 
 1.20 
 16.0 
 
 0.50 
 
 1.36 
 
 1.54 
 
 1.87 
 
 O ^ 
 
 0.37 
 
 0.78 
 20.14 
 Trace. 
 0.58 
 0.36 
 0.10 
 1.03 
 2.63 
 1.15 
 3.00 
 
 Trace. 
 1.59 
 8.48 
 
 0.76 
 3.49 
 1.04 
 2.19 
 4.28 
 1.03 
 1.97 
 
 1.22 
 
 1.57 
 3.26 
 
 0.18 
 1.50 
 3.20 
 6.50 
 
 Trace. 
 6.50 
 2.10 
 3.80 
 4.40 
 4.10 
 8.74 
 
 10.92 
 
 Trace. 
 1.78 
 
 10.98 
 6.17 
 4.00 
 2.00 
 6.00 
 0.40 
 0.82 
 8.62 
 5.83 
 
 Trace. 
 5.12 
 1.0 
 
 5.25 
 
 15.86 
 
 9.85 
 11.37 
 
 9.74 
 
 6.60 
 
 10.80 
 
 39.30 
 
 353.84 
 
 46.60 
 
 8.60 
 
 7.30 
 
 27.60 
 
 26.20 
 
 49.20 
 
 179.20 
 
 6.73 
 
 9.52 
 
 31.08 
 
 35.00 
 
 4, .3. 93 
 
 66.39 
 
 23.07 
 
 70.29 
 
 49.43 
 
 33.17 
 
 21.45 
 
 21.55 
 
 28.76 
 
 39.0 
 
 15.01 
 
 36.49 
 
 29.54 
 35.49 
 
 — 60 — 
 
(Reprinted from "THE LOCOMOTIVE," March, 1885; published by the Hartford Steam 
 Boiler Inspection and Insurance Co.) 
 
 The Effect of Oil in Boilers. 
 
 We have often referred to the fact that the presence of grease or any of 
 the animal oils in steam boilers is alm.ost certain to cause trouble. Our 
 i-lustration this month gives a better idea of the effect produced than pages 
 of verbal description possibly could. It is from a photograph and is nowise 
 exaggerated. 
 
 The boiler from which the plate shown in the cut was taken, was a 
 nearly new one. It was made of a well-known brand of mild steel, and 
 that it was admirably adapted to the purpose for which it was used, is proved 
 by its stretching as it did without rupture. The dimensions of bulge shown 
 are four feet lengthwise of the boiler, three feet girthwise and nine inches 
 deep. The metal, originally 5-16 of an inch thick, drew down to ys inch in 
 thickness at the lowest point of the "bag" without the slightest indication 
 of fracture. 
 
 The circumstances under which the bulge occurred may best be described 
 in the words of the inspector who examined the boiler, and are as follows : 
 
 "Last Tuesday morning I was called in great haste to the works. 
 
 Upon arrival I found one of the boilers badly bulged, and with twenty pounds 
 of steam up. I could give no explanation until I had thoroughly examined 
 the internal parts of the boiler. 1 gave directions for cooling the boiler and 
 ordered top man-hole plate to be loosened, but not to be taken out until my 
 arrival in the afternoon, that I might see everything undisturbed. This was 
 done. On my arrival I took out the man-hole plates in top of shell and 
 front head * * * and made an examination." 
 
 *T found that the boiler had been cleaned the preceding Sunday, and at that 
 time a gallon or more of black oil had been thrown into it. Monday morning 
 the boiler was fired up and was run through the day at a pressure of 90 
 pounds per square inch. At six o'clock Monday night the engine was stop- 
 ped, the drafts were closed, and no more firing was done until nine o'clock. 
 Upon going to fire up at this time, the bulge was observed. From six to 
 nine o'clock a pressure of only 40 pounds was carried." 
 
 "Upon examination I found the entire boiler saturated with this oil." 
 
 This is almost certain to be the result of putting grease into a steam 
 boiler. It settles down on the fire-sheets, when the draft is closed, and the 
 circulation of water nearly stops, and prevents contact between the plates 
 
 — 61 — 
 
and the water. As a consequence, the plates over the fire become over- 
 heated; and under such circumstances a very slight steam -pressure is suffi- 
 cient to bag the sheets. Unless the boiler is made of very good material, 
 the plate is apt to be fractured, and explosion is likely to occur. 
 
 When oil is used to remove scale from steam-boilers, too much care 
 cannot be exercised to make sure that it is free from grease or animal oil. 
 Nothing but pure mineral oil should be used. Crude petroleum is one 
 thing; black oil, which may mean almost anything, is very likely to be 
 something quite different. 
 
 The action of grease in a boiler is peculiar, but not more so than we 
 might expect. It does not dissolve in the water, nor does it decompose, 
 neither does it remain on top of the water, but it seems to form itself into 
 what may be described as "slugs," which at first seem to be slightly lighter 
 than the water, of just such a gravity, in fact, that the circulation of the 
 water carries them about at will. After a short season of boiling, these 
 "slugs" or suspended drops seem to acquire a certain degree of "stickiness," 
 so that when they come in contact with shell and flues of the boiler, they 
 begin to adhere thereto. Then under the action of heat they begin the 
 process of "varnishing" the interior of the boiler. The thi7i7iest possible 
 coating of this vartiish is sufficient to bring about overheating of the plates ., 
 as we have found repeatedly in our experience. We emphasize the point 
 that it is not necessary to have a coating of grease of any appreciable 
 thickness to cause overheating and bagging of plates and leakage at seams. 
 
 The time when damage is most likely to occur is after the fires are 
 banked, for then, the formation of steam being checked, the circulation of 
 water stops, and the grease thus has an opportunity to settle on the bottom 
 of the boiler and prevent contact of the water with the fire -sheets. Under 
 these circumstances, a very low degree of heat in the furnace is sufficient to 
 overheat the plates to such an extent that bulging is sure to occur. When 
 the facts are understood, it will be found quite unnecessary to attribute the 
 damage to low water. 
 
 This accident also serves to illustrate the perfection to which the manu- 
 facture of steel for boiler plates has attained. It would be an extraordin- 
 arily good quality of iron that would stand such a test without fracture. 
 
 250 H. P. Heine Boiler "en route. 
 — 62 — 
 
Weight of Water. 
 
 The weight of water varies with the temperature as given by the fol- 
 lowing table. (C. A. SMITH.) 
 
 Table No. 34. 
 
 Weight of One Cubic Foot Water at Various Temperatures, 
 
 Temp., 
 Degrees F. 
 
 Weight per 
 Cubic Foot. 
 
 Temp., Weight per 
 Degrees F. Cubic Foot. 
 
 Temp., 
 Degrees F, 
 
 Weight per 
 Cubic Foot. 
 
 Temp., 
 Degrees F. 
 
 "Weight per 
 Cubic Foot. 
 
 32 
 
 62.418 
 
 85 
 
 62.182 
 
 145 
 
 61.291 
 
 35 
 
 62.422 
 
 90 
 
 62.133 
 
 150 
 
 61.201 
 
 39.1 
 
 62.425 
 
 95 
 
 62.074 
 
 155 
 
 61.096 
 
 40 
 
 62.425 
 
 100 
 
 62.022 
 
 160 
 
 60.991 
 
 45 
 
 62.422 
 
 105 
 
 61.960 
 
 165 
 
 60.843 
 
 50 
 
 62.409 
 
 110 
 
 61.868 
 
 170 
 
 60.783 
 
 55 
 
 62.394 
 
 115 
 
 61.807 
 
 175 
 
 60.665 
 
 60 
 
 62.372 
 
 120 
 
 61.715 
 
 180 
 
 60.548 
 
 65 
 
 62.344 
 
 125 
 
 61.654 
 
 185 
 
 60.430 
 
 70 
 
 62.313 
 
 130 
 
 61.563 
 
 190 
 
 60.314 
 
 75 
 
 62.275 
 
 135 
 
 61.472 
 
 195 
 
 60.198 
 
 80 
 
 62.232 
 
 140 
 
 61.381 
 
 200 
 
 60.081 
 
 205 
 210 
 
 212 
 
 By formula. 
 
 212 
 
 By measurem' 
 
 230 
 250 
 270 
 290 
 
 298 
 338 
 366 
 390 
 
 59.930 
 59.820 
 59.760 
 59.640 
 59.360 
 58.780 
 58.150 
 57.590 
 57.270 
 56.140 
 55.290 
 54.540 
 
 Very often in the trials of a boiler or engine the most convenient unit of 
 measurement of water is the cubic foot. This will be the case when a weir 
 measurement is made or when the water is measured by a water meter. The 
 U3e of a water meter involves many precautions, the most important being 
 the following : The meter should work under moderate head of supply and 
 small head of delivery ; it should be set in such a manner that it can be 
 tested in place under the exact conditions of use ; if a positive meter, it should 
 be especially constructed to work freely, if it is to be used in warm water. 
 This table is also used for estimating the weight of water in boilers, and for 
 correcting boiler trials for differences of water level. 
 
 150 H. P. Heme Boiler. 
 
 Size for Water Pipes. 
 
 We found at beginning of this article, 3.6 gallons feed water are required 
 for each H. P. per hour. This makes 6 gallons per minute for a 100 H. P. 
 boiler. In proportioning pipes, however, it is well to rem ember that boiler 
 
 — 64 — 
 
work is seldom perfectly steady, and that as the engine cuts off just as much 
 steam as the work demands at each stroke, all the discrepancies of demand 
 and sicfply have to be equalized in the boiler. Therefore we may often have 
 to evaporate during one-half hour 50 to 75 per cent more than the normal 
 requirements. For this reason it is sound policy to arrange the feed pipes so 
 that 10 gallons per minute may flow through them, without undue speed or 
 friction, for each 100 H. P. of boiler capacity. The following tables will 
 facilitate this work : 
 
 Table No. 35. 
 
 Table- Giving Rate of Flow of Water, in Ft, per Min., Through 
 
 Pipes of Various Sizes, for Varying Quantities of Flow. 
 
 Gallons 
 per min. 
 
 3/" 
 
 1" 
 
 l>i" 
 
 1>2" 
 
 2" 
 
 2K" 
 
 3" 
 
 4" 
 
 5 
 
 10 
 15 
 20 
 25 
 30 
 35 
 40 
 45 
 50 
 
 218 
 436 
 653 
 872 
 1090 
 
 122^ 
 245 
 367J 
 490 
 612J 
 735 
 857* 
 980 
 1102J 
 
 78^^ 
 157 
 235J 
 314 
 392J 
 451 
 549J 
 628 
 706^ 
 785 
 1177^ 
 
 54^ 
 109 
 163J 
 218 
 272.J 
 327 
 381J 
 436 
 490J 
 545 
 817J 
 1090 
 
 30J 
 61 
 
 911 
 122 
 152^ 
 183 
 213J 
 244 
 274.^ 
 305 
 457J 
 610 
 762J 
 915 
 1067^ 
 1220 
 
 19^ 
 
 38 
 
 58J 
 
 78 
 
 97^ 
 117 
 136i 
 156 
 175J 
 195 
 292i 
 380 
 487J 
 585 
 682^ 
 780 
 
 13i 
 
 27 
 
 54 
 
 67J 
 
 81 
 
 94J 
 108 
 12U 
 135 
 202* 
 270 
 337J 
 405 
 472^ 
 540 
 
 15^ 
 
 23 
 
 30§ 
 
 38^ 
 
 46 
 
 53| 
 
 61i 
 
 69 
 
 76| 
 
 75 
 100 
 
 
 
 115 
 153^ 
 1911 
 230 
 
 125 
 
 
 
 
 150 
 
 
 
 
 
 175 
 
 
 
 
 
 268i 
 306| 
 
 200 
 
 
 
 
 
 
 
 
 
 
 
 Table No. 36. 
 
 Table Giving Loss in Pressure Due to Friction, in Pounds per 
 Sq. In., for Pipe 100 Ft. Long. 
 
 By G. A. Ellis, C. E. 
 
 Gallons 
 discharg- 
 adpermin. 
 
 %•• 
 
 1" 
 
 IK" 
 
 \%" 
 
 2" 
 
 2i'o" 
 
 3" 
 
 4" 
 
 5 
 
 3.3 
 13.0 
 
 28.7 
 50.4 
 78.0 
 
 0.84 
 3.16 
 6.98 
 12.3 
 19.0 
 27.5 
 37.0 
 48.0 
 
 0.31 
 1.05 
 2.38 
 4.07 
 6.40 
 9.15 
 12.4 
 16.1 
 20.2 
 24.9 
 56.1 
 
 0.12 
 0.47 
 0.97 
 1.66 
 2.62 
 3.75 
 5.05 
 6.52 
 8.15 
 10.0 
 22.4 
 39.0 
 
 
 
 
 
 10 
 
 0.12 
 
 
 
 
 15 
 
 
 
 
 20 
 
 0.42 
 
 
 
 
 25 
 30 
 
 0.21 
 
 0.10 
 
 
 35 
 
 
 
 
 40 
 
 1.60 
 
 
 
 
 45 
 
 
 
 
 50 
 
 
 
 2.44 
 
 5.32 
 9.46 
 14.9 
 21.2 
 28.1 
 37.5 
 
 0.81 
 1.80 
 3.20 
 4.89 
 7.0 
 9.46 
 12.47 
 
 0.35 
 0.74 
 1.31 
 1.99 
 2,85 
 3.85 
 5.02 
 
 0.09 
 
 75 
 
 1 1 
 
 
 100 
 
 , 
 
 0.33 
 
 125 
 150 
 175 
 200 
 
 1 _..^ . 
 
 
 
 
 1 
 
 1 
 
 0.69 
 
 
 
 
 1 
 
 
 1.22 
 
 li 1 
 
 i 
 
 
 — 65 — 
 
Loss of Head Due to Bends. 
 
 Bends produce a loss of head in the flow of water in pipes. Weisbach 
 gives the following formula for this loss : 
 
 H = f — where H = loss of head in feet, f = coefficient of friction, v 
 
 2g ' 
 
 = velocity of flow in feet per second, g = 32.2. 
 
 As the loss of head or pressure is in most cases more conveniently stated 
 in pounds per square inch, we may change this formula by multiplying by 
 0.433, which is the equivalent in pounds per square inch for one foot head. 
 
 If P = loss in pressure in pounds per square inch, F = coefficient of 
 friction. 
 
 P = F ^^, v being the same as before. 
 
 From this formula has been calculated the following table of values for 
 F, corresponding to various exterior angles, A. 
 
 TABLE No. 37. 
 
 A = 
 F = 
 
 20° 
 0.020 
 
 40° 
 0.060 
 
 45° 
 0.079 
 
 60° 80° 
 0.158,0.320 
 
 90° 
 0.426 
 
 100° 
 0.546 
 
 110° 
 0.674 
 
 120° 
 0.806 
 
 130° 
 0.934 
 
 This applies to such short bends as are found in ordinary fittings, such 
 as 90° and 45° Ells, Tees, etc. 
 
 A globe valve will produce a loss about equal to two 90° bends, a 
 straightway valve about equal to one 45° bend. To use the above formula 
 Jind the speed p. second, bei7ig one-sixtieth of that found in Table No. ^5 / 
 square this speed, and divide the result by 64..^; multiply the quotient by the 
 tabular value of P corresponding- to the angle of the tiwn, A. 
 
 For instance a 400 H. P. battery of boilers is to be fed through a 2" 
 pipe. Allowing for fluctuations we figure 40 gallons per minute, making 244 
 feet per minute speed, equal to a velocity of 4.06 feet per second. Suppose 
 our pipe is in all 75 feet long ; we have from Table No. 36, for 40 gallons per 
 minute, 1.60 pounds loss; for 75 feet we have only 75 percent, of this 
 = 1.20 pounds. Suppose we have 6 right angled ells, each giving F = 
 0.426. We have then 4.06X4.06 = 16.48; divide this by 64.4 = 0.256. 
 Multiply this by F = 0.426 pounds, and as there are six ells, multiply again 
 by 6, and we have 6x0.426x0.256 = 0.654. The total friction in the pipe 
 is therefore 1.20+0.654 = 1.854 pounds per square inch. If the boiler 
 pressure is 100 pounds and the water level in the boiler is 8 feet higher than 
 the pump suction level, we have first 8x0.433 = 3.464 pounds. The total 
 pressure on the pump plunger then is 100+3.464+1.854 = 105.32 pounds 
 per square inch. If in place of six right angled ells we had used three 45° 
 ells, they would have cost us only 3x0.079 = 0.237 pounds ; 0.237x0.256 
 = 0.061. 
 
 The total friction head would have been 1.20+0.061=1.261 and the 
 total pressure on the plunger 100+3 = 464+1.261=104.73 pounds per square 
 inch, a saving over the other plan of nearly 0.6 pounds. . 
 
 To be accurate, we ought to add a certain head in either case " to pro- 
 duce the velocity." But this is very small, being for velocities of : 
 
 2; 3; 4; 5; 6; 8; 10; 12 and 18 feet per sec. 
 
 0.027; 0.061; 0.108; 0.168; 0.244; 0.433; 0.672; 0.970 and 2.18 lbs. per sq. in. 
 Our results should therefore have been increased by about 0.11 lbs. 
 
 66 — 
 
^^.:u>»if*y^J»| 
 
 ''"'^^x 
 
 "-'CJr 
 
 .Mm 
 
 
 ^*a.*'- > -A 
 
 Foresters' Temple. 
 
 Headquarters of Independent Order of Foresters, 
 
 TORONTO, ONT., CANADA. 
 
 Contains 240 H. P. of Heine Boilers. 
 
It is usual, however, to use larger pipes and thus to materially reduce 
 the frictional losses. 
 
 Rating Boilers by Feed Water. 
 
 The rating of boilers has, since the Centennial in 1876, been generally- 
 based on 30 pounds feed water per hour per H. P. This is a fair average 
 for good non-condensing engines working under about 70 to 100 pounds 
 pressure. But different pressures and different rates of expansion change 
 the requirements for feed-water. The following table, No. 38, gives Prof. 
 R. H. Thurston's estimate of the steam consumption for the best classes oj 
 engines in common use, when of moderate size and in good order: 
 
 TABLE No. 3S. 
 
 Weights of Feed Water and of Steam. 
 
 Non-condensing Engines. — R. H. T. 
 
 Steam Pressure. 
 
 
 Lbs. per H 
 
 . p. PER HOU 
 
 ?.— Ratio of 
 
 Expansion. 
 
 
 Atmos- 
 pheres. 
 
 Lbs. per 
 sq. in. 
 
 2 
 
 3 
 
 4 
 
 5 
 
 7 
 
 10 
 
 3 
 
 45 
 
 40 
 
 39 
 
 40 
 
 40 
 
 42 
 
 45 
 
 4 
 
 60 
 
 35 
 
 34 
 
 36 
 
 36 
 
 38 
 
 40 
 
 5 
 
 75 
 
 30 
 
 28 
 
 27 
 
 26 
 
 30 
 
 32 
 
 6 
 
 90 
 
 28 
 
 27 
 
 26 
 
 25 
 
 27 
 
 29 
 
 7 
 
 105 
 
 26 
 
 25 
 
 24 
 
 23 
 
 25 
 
 27 
 
 8 
 
 120 
 
 25 
 
 24 
 
 23 
 
 22 
 
 22 
 
 21 
 
 10 
 
 150 
 
 24 
 
 23 
 
 22 
 
 21 
 
 20 
 
 20 
 
 Condensing Engines. 
 
 2 
 
 30 
 
 30 
 
 28 
 
 28 
 
 30 
 
 35 
 
 40 
 
 3 
 
 45 
 
 28 
 
 27 
 
 27 
 
 26 
 
 28 
 
 32 
 
 4 
 
 60 
 
 27 
 
 26 
 
 25 
 
 24 
 
 25 
 
 27 
 
 5 
 
 75 
 
 26 
 
 25 
 
 25 
 
 23 
 
 22 
 
 24 
 
 6 
 
 90 
 
 26 
 
 24 
 
 24 
 
 22 
 
 21 
 
 20 
 
 8 
 
 120 
 
 25 
 
 23 
 
 23 
 
 22 
 
 21 
 
 20 
 
 10 
 
 150 
 
 25 
 
 23 
 
 22 
 
 21 
 
 20 
 
 19 
 
 Small engines having greater proportional losses in friction, in leaks, in 
 radiation, etc., and besides receiving generally less care in construction and 
 running than larger ones, require more feed-water (or steam) per hour. 
 
 Table No. 39 gives Mr. R. H, Duel's estimate for such engines. 
 
 — 68 — 
 
Table No. 39. 
 
 Feed-Water Required by Small Engines. 
 
 
 Pounds of Water per 
 
 
 Poun 
 
 ds 
 
 of Water per 
 
 Pressure ot Steam 
 
 Effective Horse-power 
 
 Pressure of Steam 
 
 £ffect 
 
 Ive 
 
 Horse-power 
 
 in Boiler, by Gauge. 
 
 per Hour. 
 
 in Boiler, by Gauge. 
 
 
 pe 
 
 r Hour. 
 
 10 
 
 118 
 
 60 
 
 
 
 75 
 
 15 
 
 111 
 
 70 
 
 
 
 71 
 
 20 
 
 105 
 
 80 
 
 
 
 G8 
 
 25 
 
 100 
 
 90 
 
 
 
 65 
 
 30 
 
 9r> 
 
 100 
 
 
 
 63 
 
 40 
 
 84 
 
 120 
 
 
 
 61 
 
 50 
 
 79 
 
 150 
 
 
 
 58 
 
 Boiler Room Alleghany Traction Co. Plant, 
 
 PITTSBURGH, PA. 
 
 500 H. P. Heine Boilers. 
 
 Heating Feed-Water. 
 
 Feed-water as it comes from wells or hydrants has ordinarily a tempera- 
 ture of from 35° in winter to from 60° to 70° in summer. 
 
 Much fuel can be saved by heating this water by the exhaust steam, 
 whose heat would otherwise be wasted. Until quite recently, only non- 
 condensing engines utilized feed-water heaters ; but lately they have been 
 introduced with success between the cylinder and the air pump in condensing 
 engines. The saving in fuel due to heating feed-water is given in Table 
 No. 40. 
 
 — 69 — 
 
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 UO 
 
 
 (M 
 (M 
 
 00 
 
 CO 
 
 o 
 
 1—1 
 
 iM 
 
 CO 
 
 
 
 CO 
 
 1 — 1 
 
 CO 
 
 00 
 CO 
 
 GO 
 
 1— 1 
 
 1—1 
 
 1—1 
 
 CO 
 
 1— 1 
 
 oo 
 1— 1 
 
 CO 
 1—1 
 
 (M 
 
 1—1 
 
 1—1 
 
 1—1 
 
 T— 1 
 
 1—1 
 
 o 
 
 1—1 
 
 o 
 
 1—1 
 
 CI 
 
 o 
 
 CO 
 
 CO 
 
 
 CO 
 
 05 
 
 CM 
 
 CO 
 
 '^ 
 
 -* 
 
 '^ 
 
 ■^ 
 
 CO 
 
 C-1 
 
 1—1 
 
 o 
 
 OO 
 
 CD 
 
 CO 
 
 CO 
 
 -=tl 
 
 o 
 
 CO 
 
 CM 
 
 00 
 
 ^ 
 
 o 
 
 CO 
 
 CM 
 
 00 
 
 CO 
 
 Oi 
 
 LO 
 
 Oi 
 
 Oi 
 
 Oi 
 
 CO 
 
 CO 
 
 t^ 
 
 t^ 
 
 t- 
 
 CD 
 
 CO 
 
 LO 
 
 LO 
 
 ^ 
 
 ^ 
 
 iO 
 
 CO 
 
 CO 
 
 CD 
 
 r- 
 
 CO 
 
 CD 
 
 LO 
 
 CO 
 
 CM 
 
 o 
 
 CO 
 
 LO 
 
 CM 
 
 Oi 
 
 >o 
 
 1— ( 
 
 l^ 
 
 CO 
 
 o 
 
 LO 
 
 ■^ 
 
 t- 
 
 CO 
 
 cs 
 
 ^ 
 
 q 
 
 CD 
 
 LO lO ■* ■* TJH CO 
 
 o 
 
 OS 
 
 CO 
 
 o 
 
 CO 
 
 CO 
 
 
 GO 
 
 o 
 
 CO 
 
 CD 
 CM 
 
 GO 
 
 CM 
 
 o 
 o 
 
 GO 
 
 LO 
 
 LO 
 
 1—1 
 
 1— ( 
 
 00 
 
 t- 
 
 t- 
 
 CD 
 
 CD 
 
 CD 
 
 LO 
 
 LO 
 
 ^ 
 
 '^ 
 
 ^ 
 
 CO 
 
 CO 
 
 CM 
 
 CM 
 
 CO 
 
 
 CO 
 
 c 
 
 CO 
 CD 
 
 1— ( 
 CM 
 
 o 
 
 00 
 
 00 
 
 CO 
 
 CO 
 
 
 T-l 
 
 1—1 
 
 00 
 
 CO 
 
 LO 
 CM 
 
 1—1 
 00 
 
 t- 
 
 CD 
 
 CD 
 
 CD 
 
 LO 
 
 LO 
 
 ^ 
 
 T^ 
 
 CO 
 
 CO 
 
 CO 
 
 CM 
 
 CM 
 
 1—1 
 
 00 
 CO 
 
 
 LO 
 
 CO 
 
 lO 
 
 CO 
 
 CM 
 
 o 
 
 lO 
 
 o 
 
 LO 
 
 CD 
 
 CM 
 CM 
 
 CO 
 
 1^ 
 
 CO 
 
 o 
 
 Ci 
 
 CO 
 
 LO 
 
 LO 
 
 LO 
 
 Tti 
 
 '^l 
 
 CO 
 
 CO 
 
 CO 
 
 CM 
 
 CM 
 
 1— 1 
 
 1—1 
 
 o 
 
 CO 
 
 LO 
 
 C<) 
 
 1—1 
 
 1—1 
 
 O 
 CO 
 
 CO 
 
 
 LO 
 
 o 
 
 CM 
 
 CD 
 
 1—1 
 
 CO 
 
 o 
 
 CO 
 
 00 
 
 LO 
 
 o 
 o 
 
 LO 
 
 LO 
 
 Ttl 
 
 -*l 
 
 CO 
 
 CO 
 
 CO 
 
 CM 
 
 cq 
 
 1—1 
 
 1—1 
 
 o 
 
 o 
 
 o 
 
 o 
 
 LO 
 
 o 
 
 LO 
 
 o 
 
 LO 
 
 o 
 
 LO 
 
 o 
 
 LO 
 
 o 
 
 LO 
 
 LO 
 
 CO 
 
 CO 
 
 t^ 
 
 t-- 
 
 00 
 
 GO 
 
 Oi 
 
 Ol 
 
 o 
 
 — 70 
 
STEAM. 
 
 When water is heated in an open vessel its temperature rises until it 
 reaches 212° (at sea level); if more heat is added a portion of the water 
 changes from a liquid form to a vapor called steam. If the process is carried 
 on in a closed vessel the pressure within the same rises on account of the 
 expansive force of the steam. The water then will rise to a higher temper- 
 ature with each increment of pressure before it begins to boil and form steam. 
 
 For the distinction between "sensible" and "latent" heat see p. 7. 
 
 The following table No. 41, giving the properties of saturated steam, is 
 adapted from Prof. Peabody's well known tables. The first column gives 
 the actual pressure in pounds per square inch above the atmosphere. 
 
 Column two gives the temperature in degrees Fahrenheit for the cor- 
 responding pressure. 
 
 Columns three and four give the heat, in heat units, of steam and water, 
 respectively, from 32° F. 
 
 Column five gives the heat of vaporization for the corresponding pres- 
 sure, and is the difference between columns three and four. 
 
 Columns six and seven give the weight of one cubic foot in pounds and 
 the volume of one pound in cubic feet, of saturated steam. 
 
 Column eight gives the approximate weight of one cubic foot of water 
 for the corresponding weight and temperature and is calculated from Prof. 
 Rankin's approximate formula : 
 
 D 
 
 2 Dn 
 
 To + 461 
 500 
 
 + 
 
 500 
 
 To + 461 
 
 where 
 
 D = required density. Do = max. density = 62.425 lbs. 
 To = given temperature in degrees F. 
 
 — 71 
 
Column nine gives tlie factor of equivalent evaporation from and at 212° 
 F., assuming feed to be 212° in each case. For the factor of evaporation for 
 any temperature of feed, add 0.00104 to the given factor for each degree dif- 
 ference in temperature between feed and 212°. 
 
 For complete table of factors of evaporation, see page 152. 
 
 The horse-power of a boiler is obtained by dividing the equivalent 
 evaporation from and at 212° by 30.978. This is on the basis of feed from 
 212° to steam at 70 pounds pressure. On the basis of feed from 100° to steam 
 at 70 lbs., divide the equivalent evaporation by 34.485. 
 
 TABLE No. 41. 
 
 Table of the Properties of Saturated Steam. 
 
 From Peabody's Tables. 
 
 c • 
 — c 
 
 tv. 
 
 3— ' 
 « u 
 
 3 J! 
 
 a 
 
 Q 
 c 
 
 *j o 
 
 I-; Heat Units in Liquid 
 § from 32° F. 
 
 bo 
 
 c 
 o 
 
 1 • 
 
 o ^ 
 
 >*= 
 
 := ■ 
 
 M C 
 
 o 
 c 
 ■ai£ 
 
 3 
 
 u 
 
 c 
 
 o a! 
 
 3.y 
 > 
 
 3 
 
 u 
 
 °« 
 
 >*" . 
 
 3 U, 
 
 
 
 212.00 
 
 1146.6 
 
 965.8 
 
 0.03760 
 
 26.60 
 
 59.76 (Fo"»»i») 
 59.64(o»>»'"-»e^) 
 
 1.0000 
 
 10 
 
 239.36 
 
 1154.9 
 
 208.4 
 
 946.5 
 
 0.06128 
 
 16.32 
 
 59.04 
 
 1.0086 
 
 20 
 
 258.68 
 
 1160.8 
 
 227.9 
 
 932.9 
 
 0.08439 
 
 11.85 
 
 58.50 
 
 1.0147 
 
 30 
 
 273.87 
 
 1165.5 
 
 243.2 
 
 922.3 
 
 0.1070 
 
 9.347 
 
 58.07 
 
 1.0196 
 
 40 
 
 286.54 
 
 1169.3 
 
 255.9 
 
 913.4 
 
 0.1292 
 
 7.736 
 
 57.69 
 
 1.0235 
 
 50 
 
 297.46 
 
 1172.6 
 
 266.9 
 
 905.7 
 
 0.1512 
 
 6.612 
 
 57.32 
 
 1.0269 
 
 55 
 
 302.42 
 
 1174.2 
 
 271.9 
 
 902.3 
 
 0.1621 
 
 6.169 
 
 57.22 
 
 1.0286 
 
 60 
 
 307.10 
 
 1175.6 
 
 276.6 
 
 899.0 
 
 0.1729 
 
 5.784 
 
 57.08 
 
 1.0300 
 
 65 
 
 311.54 
 
 1176.9 
 
 281.1 
 
 895.8 
 
 0.1837 
 
 5.443 
 
 56.95 
 
 1.0314 
 
 70 
 
 315.77 
 
 1178.2 
 
 285.6 
 
 892.7 
 
 0.1945 
 
 5.142 
 
 56.82 
 
 1.0327 
 
 75 
 
 319.80 
 
 1179.5 
 
 289.8 
 
 889.8 
 
 0.2052 
 
 4.873 
 
 56.69 
 
 1.0341 
 
 80 
 
 323.66 
 
 1180.6 
 
 293.8 
 
 886.9 
 
 0.2159 
 
 4.633 
 
 56.59 
 
 1.0352 
 
 85 
 
 327.36 
 
 1181.8 
 
 297.7 
 
 884.2 
 
 0.2265 
 
 4.415 
 
 56.47 
 
 1.0365 
 
 90 
 
 330.92 
 
 1182.8 
 
 301.5 
 
 881.5 
 
 0.2371 
 
 4.218 
 
 56.36 
 
 1.0375 
 
 95 
 
 334.35 
 
 1183.9 
 
 305.0 
 
 879.0 
 
 0.2477 
 
 4.037 
 
 56.25 
 
 1.0386 
 
 100 
 
 337.66 
 
 1184.9 
 
 308.5 
 
 876.5 
 
 0.2583 
 
 3.872 
 
 56.18 
 
 1.0397 
 
 105 
 
 340.86 
 
 1185.9 
 
 311.8 
 
 874.1 
 
 0.2689 
 
 3.720 
 
 56.07 
 
 1.0407 
 
 110 
 
 343.95 
 
 1186.8 
 
 315.0 
 
 871.8 
 
 0.2794 
 
 3.580 
 
 55.97 
 
 1.0417 
 
 115 
 
 346.94 
 
 1187.7 
 
 318.2 
 
 869.6 
 
 0.2898 
 
 3.452 
 
 55.87 
 
 1.0426 
 
 120 
 
 349.85 
 
 1188.6 
 
 321.2 
 
 867.4 
 
 0.3003 
 
 3.330 
 
 55.77 
 
 1.0435 
 
 125 
 
 352.68 
 
 1189.5 
 
 324.2 
 
 865.3 
 
 0.3107 
 
 3.219 
 
 55.69 
 
 1.0444 
 
 130 
 
 355.43 
 
 1190.3 
 
 327.0 
 
 863.3 
 
 0.3212 
 
 3.113 
 
 55.58 
 
 1.0452 
 
 135 
 
 358.10 
 
 1191.1 
 
 329.8 
 
 861.3 
 
 0.3315 
 
 3.017 
 
 55.52 
 
 1.0461 
 
 140 
 
 360.70 
 
 1191.9 
 
 332.5 
 
 859.4 
 
 0.3420 
 
 2.924 
 
 55.44 
 
 1.0469 
 
 145 
 
 363.25 
 
 1192.8 
 
 335.2 
 
 857.5 
 
 0.3524 
 
 2.838 
 
 55.36 
 
 1.0478 
 
 160 
 
 365.73 
 
 1193.5 
 
 337.8 
 
 855.7 
 
 0.3629 
 
 2.756 
 
 55.29 
 
 1.0486 
 
 155 
 
 368.62 
 
 1194.3 
 
 340 3 
 
 853.9 
 
 0.3731 
 
 2.681 
 
 55.22 
 
 1.0494 
 
 160 
 
 370.51 
 
 1195.0 
 
 342.8 
 
 852.1 
 
 0.3835 
 
 2.608 
 
 55.15 
 
 1.0500 
 
 165 
 
 372.83 
 
 1195.7 
 
 345.2 
 
 850.4 
 
 0.3939 
 
 2.539 
 
 55.07 
 
 1.0508 
 
 170 
 
 375.09 
 
 1196.3 
 
 347.6 
 
 848.7 
 
 0.4043 
 
 2.474 
 
 54.99 
 
 1.0514 
 
 175 
 
 377.31 
 
 1197.0 
 
 349.9 
 
 847.1 
 
 0.4147 
 
 2.412 
 
 54.93 
 
 1.0522 
 
 180 
 
 379.48 
 
 1197.7 
 
 352.2 
 
 845.4 
 
 0.4251 
 
 2.353 
 
 54.86 
 
 1.0529 
 
 185 
 
 381.60 
 
 1198.3 
 
 354.4 
 
 843.9 
 
 0.4353 
 
 2.297 
 
 , 54.79 
 
 1.0535 
 
 190 
 
 383.70 
 
 1199.0 
 
 356.6 
 
 842.3 
 
 0.4455 
 
 2.244 
 
 54.73 
 
 1.0542 
 
 195 
 
 385.75 
 
 1199.6 
 
 358.8 
 
 840.8 
 
 0.4559 
 
 2.193 
 
 54.66 
 
 1.0549 
 
 200 
 
 387.76 
 
 1200.2 
 
 360.9 
 
 839.2 
 
 0.4663 
 
 2.145 
 
 54.60 
 
 1.0555 
 
 325 
 
 397.36 
 
 1203.1 
 
 370.9 
 
 832.2 
 
 0.5179 
 
 1.930 
 
 54.27 
 
 1.0585 
 
 250 
 
 406.07 
 
 1205.8 
 
 380.1 
 
 825.7 
 
 0.5699 
 
 1.755 
 
 54.03 
 
 1.0613 
 
 275 
 
 414.22 
 
 1208.3 
 
 3S8.5 
 
 819.8 
 
 0.621 
 
 1.609 
 
 53.77 
 
 1.0639 
 
 300 
 
 421.83 
 
 1210.6 
 
 396.5 
 
 814.1 
 
 0.674 
 
 " 1.483 
 
 53.54 
 
 1.0666 
 
 — 72 — 
 
The Betz Building, 
 
 PHILADELPHIA, PA., 
 
 Contains 500 H, P. Heine Boilers, 
 
Of the Motion of Steam. 
 
 The flow of steam of a greater pressure into an atmosphere of a less 
 pressure, increases as the difference of pressure is increased, until the 
 external pressure becomes only 58 per cent of the absolute pressure in the 
 boiler. The flow of steam is neither increased nor diminished by the fall of 
 the external pressure below 58 per cent, or about fths of the inside pressure, 
 even to the extent of a perfect vacuum. In flowing through a nozzle of the 
 best form, the steam expands to the external pressure, and to the volume 
 due to this pressure, so long as it is not less than 58 per cent of the internal 
 pressure. For an external pressure of 58 per cent, and for lower percentages, 
 the ratio of expansion is 1 to 1,624. The following table. No. 42, is selected 
 from Mr. Brownlee's data exemplifying the rates of discharge, under a 
 constant internal pressure, into various external pressures: 
 
 Table No. 42. 
 
 Outflow of Steam ; From a Given Initial Pressure into 
 Various Lower Pressures. 
 
 Absolute Initial Pressure in Boiler, 75 Lbs. per Square Inch. 
 
 D. K. C. 
 
 Absolute Pressure 
 
 in Boiler in Lbs. 
 
 per Square Inch. 
 
 External Pressure 
 
 in Lbs. 
 per Square Inch. 
 
 Ratio of 
 
 Expansion in 
 
 Nozzle. 
 
 Velocity of 
 Outflow at Con- 
 stant Density. 
 
 Actual Velocity 
 of Outflow, 
 Expanded. 
 
 Discharge per 
 
 Square Inch 
 
 of Orifice per 
 
 Minute. 
 
 Lbs. 
 
 Lbs. 
 
 Ratio. 
 
 R. per Sec. 
 
 Ft. per Sec. 
 
 Lbs. 
 
 75 
 
 74 
 
 1.012 
 
 227.5 
 
 230. 
 
 16.68 
 
 75 
 
 72 
 
 1.037 
 
 386.7 
 
 401. 
 
 28.35 
 
 75 
 
 70 
 
 1.063 
 
 490. 
 
 521. 
 
 35.93 
 
 75 
 
 65 
 
 1.136 
 
 660. 
 
 749. 
 
 48.38 
 
 75 
 
 61.62 
 
 1.198 
 
 736. 
 
 876. 
 
 53.97 
 
 75 
 
 60 
 
 1.219 
 
 765. 
 
 933. 
 
 56.12 
 
 75 
 
 50 
 
 1.434 
 
 873. 
 
 1252. 
 
 64. 
 
 75 
 
 45 
 
 1.575 
 
 890. 
 
 1401. 
 
 65.24 
 
 75 
 
 43.46 (58%) 
 
 1.624 
 
 890.6 
 
 1446.5 
 
 65.3 
 
 75 
 
 15 
 
 1.624 
 
 890.6 
 
 1446.5 
 
 65.3 
 
 75 
 
 
 
 1.624 
 
 890.6 
 
 1446.5 
 
 65.3 
 
 When, on the contrary, steam of varying initial pressure is discharged 
 into the atmosphere — pressures of which the atmospheric pressure is not 
 more than 58 per cent — the velocity of outflow at constant density, that is, 
 supposing the initial density to be maintained, is given by the formula — 
 
 V = 3.5953 VT (1) 
 where V = the velocity of outflow in feet per minute, as for steam of the 
 initial density, h = the height in feet of a column of steam of the given abso- 
 lute initial pressure of uniform density, the weight of which is equal to the 
 pressure on the unit of base. 
 
 The following table is calculated from this formula : 
 
 — 74 — 
 
Table no. 4:!. 
 Outflow of Steam into the Atmosphere. 
 
 D. K. c. 
 
 Absoljte initial 
 
 External pres- 
 
 
 Velocity of out- 
 
 Actual velocity 
 
 Discharge per 
 
 pressure in 
 lbs. per sq. in. 
 
 sure in lbs. 
 per sq. in. 
 
 sion in nozzle. 
 Ratio. 
 
 flow at con- 
 stant density. 
 
 of outflow, e.\- 
 panded. 
 
 sq. in of ori- 
 fice per inin. 
 
 Lbs. 
 
 Lbs. 
 
 Ft. per sec. 
 
 Ft. per sec. 
 
 Lbs. 
 
 25.37 
 
 14.7 
 
 1.624 
 
 863 
 
 1401 
 
 22.81 
 
 30 
 
 14.7 
 
 1.624 
 
 867 
 
 1408 
 
 26.84 
 
 40 
 
 14.7 
 
 1.624 
 
 874 
 
 1419 
 
 35.18 
 
 45 
 
 14.7 
 
 1.624 
 
 877 
 
 1424 
 
 39.78 
 
 50 
 
 14.7 
 
 1.624 
 
 880 
 
 1429 
 
 44.06 
 
 60 
 
 14.7 
 
 1.624 
 
 885 
 
 1437 
 
 52.59 
 
 70 
 
 14.7 
 
 1.624 
 
 889 
 
 1444 
 
 61.07 
 
 75 
 
 14.7 
 
 1.624 
 
 891 
 
 1447 
 
 65.30 
 
 90 
 
 14.7 
 
 1.624 
 
 895 
 
 1454 
 
 77.94 
 
 100 
 
 14.7 
 
 1.624 
 
 898 
 
 1459 
 
 86.34 
 
 115 
 
 14.7 
 
 1.624 
 
 902 
 
 1466 
 
 98.76 
 
 135 
 
 14.7 
 
 1.624 
 
 906 
 
 1472 
 
 115.61 
 
 155 
 
 14.7 
 
 1.624 
 
 910 
 
 1478 
 
 132.21 
 
 165 
 
 14.7 
 
 1.624 
 
 912 
 
 1481 
 
 140.46 
 
 215 
 
 14.7 
 
 1.624 
 
 919 
 
 1493 
 
 181.58 
 
 The Economic Value of Dry Steam. 
 
 Saturated steam is defined as steam of the maximum pressure and 
 density due to its temperature. It is steam in its normal condition, being 
 both at the condensing and the generating point. It is formed thus in a well- 
 designed boiler, and any heat added would evaporate more water, while heat 
 taken away would condense some of the steam. In badly-proportioned 
 boilers, however, we find water entrained in the steam in the form of a fine 
 mist. This is caused by imperfect arrangements for separating the steam 
 from the water ; by a liberating surface either too small or too near the hot 
 metal ; by a cramped or low steam-space; or by more heating surface than 
 the water-space or circulation warrants. It is only during the last decade 
 that the attention of steam users generally has been bent on getting dry 
 steam, i.e., saturated steam containing but a small percentage of entrained 
 water. 
 
 Formerly, with long stroke and slow speed engines, and when cylinder 
 condensation was understood but by a few experts, this entrainment was 
 rarely measured. 
 
 In Mr. D. K. Clark's celebrated Manual for Mechanical Engineers (1877), 
 which contains the record and careful analysis of many notable boiler tests, 
 entrainment is not even mentioned. Most of the high results of ancient 
 tests which are paraded in advertisements are therefore open to the suspicion 
 that they may have been obtained by delivering " soda water " in place of 
 steam. Since calorimeter tests have become common, entrainments up to 6 
 and 10 per cent, have been found in boilers apparently giving high economy. 
 As early as 1860, Chief Engineer Isherwood, of the U. S. Navy, began 
 investigating the economic losses due to moisture in the cylinder. 
 
Superheated steam was suggested as a remedy for cylinder condensation 
 by Prof. Dixwell, of Boston, early in 1875, and Mr. Hirn, of Mulhouse, made 
 extensive and successful experiments in this line in 1873 and 1875 (first 
 published in 1877). Where good saturated steam induces such wasteful 
 condensation in the cylinder, wet steam greatly increases the losses. For 
 the water cools the internal surfaces of the cylinder more rapidly than steam 
 of the same temperature, and this increases the cylinder condensation. 
 Hence, economic reasons condemned wet steam, and finally close-coupled 
 and nigh-speed engines protested against entrainment in the emphatic language 
 of broken valves and blown out cylinder heads. 
 
 Marine boilers are called upon for a maximum of work in a minimum of 
 space, and are therefore more liable to entrain water ; this was especially 
 the case with the low-pressures in use before 1880. We therefore find super- 
 heated steam resorted to in the navy at an early day. 
 
 Exhaustive experiments made by Mr. Isherwood early in the sixties 
 show large gains in economy by superheating, and thus illustrate the losses 
 due to water in the steam. 
 
 We choose only two examples in which the boiler pressure and the rate 
 of expansion are alike ; the economy found is therefore clearly du<? to super- 
 heating the steam, or conversely the loss is due to cylinder condensation. 
 
 Table No. 44. 
 
 Name of Steamer. 
 
 Pounds 
 
 Gauge 
 
 Pressure. 
 
 Rate 
 
 of 
 
 Expansion. 
 
 Pounds 
 
 Coal 
 
 PerH.P.perh. 
 
 Character of steam used. 
 
 Saving in Coal. 
 
 Dallas 
 
 32 
 33 
 
 3.22 
 3.22 
 
 3.80 
 
 2.58 
 
 Saturated. 
 Superheated. 
 
 
 Georgeanna 
 
 47.3 % 
 
 Eutaw 
 
 27 
 28 
 
 1.85 
 1.85 
 
 3.84 
 2.99 
 
 Saturated. 
 Superheated. 
 
 
 Eutaw 
 
 28.4 ofo 
 
 At the instance of Prof. Dixwell, the Government in 1877 sent Chief 
 Engineers Loring, Baker and Farmer to Boston to test the effect of super- 
 heated steam on the small Corliss engine of the Institute of Technology. 
 The boiler pressure throughout the six tests was kept uniform. Three dif- 
 ferent rates of expansion were taken, and with each, one test was run with 
 saturated and one with superheated steam, the degree of superheat being 
 adjusted to the rate of expansion. The total steam used was condensed and 
 weighed, and the loss by cylinder condensation thus accurately determined. 
 
 Table No. 45. 
 
 Tests of Corliss Engine 8" x 24," Mass. Inst, of Technology. 
 
 
 Rate 
 
 of 
 
 Expansion. 
 
 Superheat. 
 
 Pounds steam per H. P. per hour. 
 
 
 Boiler 
 Pressure. 
 
 1st Test, 
 Superheated. 
 
 2d Test, 
 Saturated. 
 
 when using 
 Saturated Steam. 
 
 50.4 
 50.1 
 50.2 
 
 4.05 
 2.16 
 1.44 
 
 279° F. 
 194° F. 
 129° F. 
 
 19.39 
 21.75 
 26.48 
 
 27.66 
 29.14 
 33.54 
 
 42.6 % 
 33.9 % 
 26.6 % 
 
 76 
 
Both series of experiments show great losses by cylinder condensation ; 
 tney show also that these losses increase with the rate of expansion ; and 
 they show greater losses with marine than with land boilers. This effect of 
 cylinder condensation and wet steam can also be partially counteracted by 
 steam or hot air jackets around the cylinders. 
 
 In his admirable work on the Steam Engine, Mr. D. K. Clark gives a 
 number of carefully prepared tables on the Practice of Expansive Working 
 in Steam Engines. By comparing in these the amount of steam shown by 
 the indicator cards on the basis of dry saturated steam with the actual feed 
 water used, we find the percentage of loss due to cylinder condensation and 
 entrainment. This is figured in percentages of the calculated amounts, and 
 therefore shows how much should be added to estimates based on indicator cards 
 to find the actual evaporation necessary for a required amount of work in a 
 given engine. The H. P. of the engine, the total initial pressure above 
 vacuum in the cylinder, the total rate of expansion, and the superheat are 
 given, as the figures can only be used under similar conditions. 
 
 Table No. 46. 
 Table Illustrating Cylinder Condensation and Entrainment. 
 
 E. D. M. 
 
 Kind of Engine. 
 
 Porter-Allen, not jacketed 
 
 Cornish, steam jacketed 
 
 i( (( i( 
 
 K (f (( 
 
 l( It u 
 
 Reynolds Corliss, not jacketed,cond'g 
 " " non-condensing-- 
 
 Harris-Corliss, no jacket, condensing 
 " " " non-condensing 
 
 Wheelock, " condensing 
 
 " " non-condensing 
 
 Corliss, steam jacket, condensing — 
 
 Hirn, no jacket, condensing 
 
 i< i< (< 
 
 (( (I It 
 
 Cornish, steam jacket, condensing-- 
 
 Woolf Comp'd Cond'g, steam jacket 
 
 nojacket--- 
 
 " '• Pump'g En, st'm jckt 
 
 Woolf Comp'd Marine, stean^ in jckt. 
 
 " " no jacket 
 
 Same Eng, 2dcyl. only, steam jacket 
 
 " " " no jacket 
 
 Receiver Comp'd Marine, steam jckt. 
 Marine Cond'g, i cylinder, no jacket 
 
 (< K (< <( 
 
 Single Cylinder, f no jacket 
 
 American, | steam in jacket- - 
 
 Marine, I no jacket 
 
 Condensing, | steam in jacket- - 
 
 Condensing, no jacket 
 
 Condensing, I, steam in jacket-- 
 
 
 1/1 
 
 
 
 (1) 
 
 c 
 
 c 
 lU 
 
 o 
 
 u 
 
 c 
 
 
 o 
 
 2 o 
 
 ■X. 
 
 O 3 
 
 <1> 
 
 o. 
 
 3 
 
 (/3 
 
 i5 ^ 
 H 
 
 66. 
 
 76 
 
 35.5° F. 
 
 6.34 
 
 124.6 
 
 34 
 
 None. 
 
 3.62 
 
 149.5 
 
 27 
 
 " 
 
 2.81 
 
 190.7 
 
 36 
 
 i( 
 
 3.66 
 
 217.0 
 
 40 
 
 " 
 
 3.65 
 
 165.0 
 
 101 
 
 (( 
 
 6.83 
 
 138.7 
 
 105 
 
 " 
 
 5.57 
 
 167.4 
 
 105 
 
 (( 
 
 7.39 
 
 135.8 
 
 104 
 
 (( 
 
 6.55 
 
 160.4 
 
 1(3 
 
 i( 
 
 6.64 
 
 141.8 
 
 103 
 
 " 
 
 5.23 
 
 418.3 
 
 35 
 
 (( 
 
 4.69 
 
 142.4 
 
 60 
 
 150°F. 
 
 3.75 
 
 134.6 
 
 54 
 
 None. 
 
 3.75 
 
 111.6 
 
 56 
 
 85°F. 
 
 5.84 
 
 106.3 
 
 65 
 
 None. 
 
 5.84 
 
 101.8 
 
 33 
 
 li 
 
 6.85 
 
 46.2 
 
 51 
 
 i( 
 
 11.59 
 
 27.8 
 
 48 
 
 " 
 
 14.73 
 
 118.4 
 
 36 
 
 u 
 
 11.35 
 
 96.3 
 
 90.6 
 
 " 
 
 7.68 
 
 72.9 
 
 89.7 
 
 It 
 
 7.15 
 
 78.0 
 
 78.2 
 
 tl 
 
 9.49 
 
 69.4 
 
 89.0 
 
 " 
 
 8.25 
 
 217.6 
 
 66.2 
 
 " 
 
 5.12 
 
 201.1 
 
 67.6 
 
 " 
 
 3.17 
 
 204.7 
 
 45.1 
 
 " 
 
 3.47 
 
 88.7 
 
 24.5 
 
 " 
 
 1.76 
 
 96.5 
 
 25.2 
 
 It 
 
 1.75 
 
 185.8 
 
 53.2 
 
 It 
 
 3.83 
 
 171.8 
 
 53.5 
 
 It 
 
 4.01 
 
 249.5 
 
 79.2 
 
 It 
 
 5.41 
 
 283.1 
 
 82.3 
 
 It 
 
 5.19 
 
 Pounds Water p. 
 H. P. p. hour. 
 
 i^ c 
 
 3 c 3 w 
 
 IB C •Og 
 
 24.69 
 16.76 
 18.69 
 14.23 
 16.70 
 16.67 
 21.49 
 15.83 
 21.02 
 15.26 
 20.80 
 14.51 
 16.42 
 18.14 
 14.20 
 14.42 
 22.06 
 17.62 
 21.44 
 17.19 
 16.15 
 15.48 
 18.08 
 18.71 
 18.44 
 18.02 
 20.79 
 27.66 
 29.27 
 19^24 
 18.27 
 16.95 
 16.88 
 
 <^ 
 
 25.81 
 
 20.72 
 
 21.38 
 
 18.82 
 
 20.08 
 
 20.37 
 
 23.07 
 
 19.15 
 
 23.68 
 
 19.22 
 
 24.61 
 
 17.4 
 
 17.2 
 
 22.41 
 
 16.16 
 
 19.93 
 
 22.94 
 
 22.32 
 
 32.72 
 
 22.62 
 
 21.72 
 
 23.34 
 
 27.09 
 
 30 32 
 
 20.24 
 
 26.53 
 
 28.09 
 
 42.27 
 
 37.34 
 
 25.93 
 
 21.86 
 
 23.80 
 
 21.12 
 
 Differ'ce. 
 Per Cent. 
 
 
 4.5% 
 19.2% 
 13.0% 
 24.4% 
 16.9% 
 18.2% 
 
 6.8% 
 17.3% 
 11.2% 
 20.6% 
 15.4% 
 20.0% 
 
 4.4% 
 19.1% 
 12.1% 
 27.6% 
 
 4.0% 
 26.6% 
 52.6% 
 31.6% 
 34.5% 
 50.7% 
 49.8% 
 62.0% 
 
 9.8% 
 47.2% 
 35.1% 
 52.8% 
 20.8% 
 34.7% 
 19.6^ 
 40.5% 
 25.1% 
 
 — 77 — 
 

 C 
 C/5 
 
 T3 
 OJ 
 
 'o 
 CQ 
 
 .s 
 
 -^m X 
 
 o 
 
We see then that a calculation of water consumption from indicator 
 cards may be anywhere from 4 per cent, to 62 per cent, out of the way. 
 
 We note further that superheating may counteract on the average all 
 but 7 per cent, of the loss by moisture ; careful lagging and good boilers 
 may reduce it to 11.2 per cent, in the best of non-condensing engines ; steam 
 jackets in condensing engines may limit it to an average of 22.5 per cent., 
 while in unjacketed condensing engines we may expect an average of 36.8 
 per cent. 
 
 Here again the land boilers show their advantage over the marine types. 
 The average loss in steam jacketed land engines is 19.46 per cent, against 
 26.6 per cent, for the same type of marine engines ; without jackets the land 
 practice shows 21 per cent, loss against 46.1 per cent, for marine. It is 
 evident that this discrepancy is in the boilers, and not in the engines, since 
 marine engines are even more carefully built than land engines. 
 
 In specifying horizontal tubular or return tubular boilers for their work, 
 careful engineers insist that the steam shall contain not more than 2 per cent, 
 (sometimes 3 per cent.) of entrained water. This is considered good work 
 for that type of boiler, and ample heating surface, and large liberating 
 area and steam space are necessary to attain it. 
 
 Well designed water tube boilers give much better results. Several 
 well authenticated tests of Heine Safety Boilers record entrainments as low 
 as 1-8 of 1 per cent., and 1-2 of 1 per cent, when forcing 50 per cent, above 
 rating, and from 1-12 of 1 per cent, entrainment to 1-7 of 1 per cent, super- 
 heat at rating. Here then is a cnance for economy in the engine gained by 
 the boiler in addition to its own economy in fuel. E. D. M. 
 
 The Rating of Boilers. 
 
 R. H. T. 
 
 It is considered usually advisable to assume a set of practically attaina- 
 ble conditions in average good practice, and to take the power so obtainable 
 as the measure of the power of the boiler in commercial and engineering 
 transactions. The unit generally assumed has been usually the weight of 
 steam demanded per horse power per hour by a fairly good steam engine. 
 This magnitude has been gradually decreasing from the earliest period of the 
 history of the steam engine. In the time of Watt, one cubic foot of water 
 per hour was thought fair ; at the middle of the present century, ten pounds 
 of coal was a usual figure, and five pounds, commonly equivalent to about 
 forty pounds of feed water evaporated, was allowed the best engines. After 
 the introduction of the modern forms of engine, this last figure was reduced 
 25 per cent. , and the most recent improvements have still further lessened 
 the consumption of fuel and of steam. By general consent the unit has now 
 become thirty pounds of dry steam per horse power per hour, which repre- 
 sents the performance of good non-condensing mill engines. Large engines, 
 with condensers and compounded cylinders, will do still better. A committee 
 of the American Society of Mechanical Engineers recommended thirty 
 pounds as the unit of boiler power, and this is now generally accepted. They 
 advised that the commercial horse power be taken as an evaporation of jo 
 poiinds of water per hour from a feed water temperature of ioo° Fahreriheit 
 
 — 79 — 
 
into steain at jo pounds gauge pressure, which may be considered to be equal 
 to 34^ units of evaporation, that is, to 34^ pounds of water evaporated from 
 a feed water temperature of 212° Fahrenheit into steam at the same tempera- 
 ture. This standard is equal to 33,305 British thermal units per hour. 
 
 It was the opinion of this committee that a boiler rated at any stated 
 power should be capable of developing that power with easy firing, moder- 
 ate draught, and ordinary fuel, while exhibiting good economy, and at least 
 one-third more than its rated power to meet emergencies. 
 
 Kansas City Water Works, 
 
 KANSAS CITY, MO. 
 
 Contains 8oo H. P. Heine Boilers. 
 
 The Energy Stored in Steam Boilers. 
 
 R. H. T. 
 
 A steam boiler is not only an apparatus by means of which the potential 
 energy of chemical affinity is rendered actual and available, but it is also a 
 storage reservoir, or a magazine, in which a quantity of such energy is tem- 
 porarily held; and this quantity, always enormous, is directly proportional to 
 the weight of water and of steam which the boiler at the time contains. The 
 energy of gunpowder is somewhat variable, but a cubic foot of heated water 
 under a pressure of 60 or 70 lbs. per square inch has about the same energy 
 as one pound of gunpowder. At a low red heat water has about 40 times 
 this amount of energy. Following are presented the weight's of steam and of 
 water contained in each of the more common forms of steam boilers, the 
 total and relative amounts of energy confined in each under the usual condi- 
 tions of working in every day practice, and their relative destructive power 
 in case of explosion : 
 
 — 80 — 
 
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 — 82 — 
 
Tlie stored available energy in zvatci-tiibe boilers is usually less than 
 that of any of the other stationary boilers, and not very far from the amount 
 stored, pound for pound, by the plain tubular boiler, the best of the older 
 forms. It is evident that their admitted safety from destructive explosion does 
 not come from this relation, however, but from the division of the contents 
 into small portions, and especially from those details of construction which 
 make it tolerably certain that any rupture shall be local. A violent explosion 
 can only come of the general disruption of a boiler and the liberation at once 
 of large masses of steam and water. 
 
 The Mallinckrodt Building, St. Louis, Mo., 
 Contains 300 H. P. Heine Boilers. 
 
 Heating Buildings by Steam. 
 
 In heating buildings by steam we have two things to consider. First, 
 the amount of fresh air entering the building per hour which has to be heated 
 from the external to the desired internal temperature, and second, the amount 
 of heat to be supplied to take the place of what is lost by conduction through 
 walls, windows, roofs, ceilings and doors and thence by radiation and convec- 
 tion to the outer air. 
 
 It is generally customary to assume the air to be warmed as entering 
 the house at 0° F., and in the United States the rule is to require an interior 
 temperature of 70° F. The weight of 1 cu. ft. of air at 0° F. is 0.086 lbs ; its 
 specific heat at constant pressure is 0.2377 (see Table No. 7). Therefore, 
 to raise 1 cu. ft. of air at 0° F. one degree in temperature, we require 
 0.086 X 0.2377 = 0.02 H. U. To bring it from 0° to 70° will take 1.4 H. U. 
 This of course is true only when the air is measured at the inlet opening ; 
 for as it grows warmer it expands and a cu. ft. weighs less. 
 
 The amount of heat required to replace that dissipated through the ex- 
 posed surfaces of the building can be figured from the following diagram^ 
 Table No. 48, which has been prepared by Mr. Alfred R. Wolff, M. E. It is 
 "the graphical interpretation, in American units, of the practice and 
 coefficients prescribed by law by the German Government in the design 
 of the heating plants of its public buildings, and generally used in 
 Germany for all buildings." Mr. Wolff has checked the coefficients by 
 examples of good American practice, and found satisfactory agreement in the 
 results. 
 
 — 83 
 
10''20"30'*40"30"60'*70>"90W 120" MO" W 180" 
 
 Fahrenheit. Ot— 1:^ 
 
 Heal^lkn8iniired,inBifflshThennal 
 liiir8,per8quareFoorof Surfeccper Hour. 
 
 84 — 
 
The tormuhi for the loss is Q =SxKx(^ — /o). 
 
 K is the loss by transmission in B. T. U. per hour per square foot of 
 outer surface, per degree F. difference in temperature on the two sides. 
 
 ^the number of square feet of transmitting surface,/ the interior, ana 
 4 the exterior temperature in degrees Fahrenheit, of the air. 
 
 The values of K are given in the following table* 
 
 Table No. 4o 
 A. R. W. 
 
 For each square foot of brick wall of thickness : 
 
 Thickness of brick wall= 
 
 4" 
 
 8" 
 
 12" 
 
 16" 
 
 20" 
 
 24" 
 
 28" 
 
 32" 
 
 36" 
 
 40" 
 
 K= 
 
 0.68 
 
 0.46 
 
 0.32 
 
 0.26 
 
 0.23 
 
 0.20 
 
 0.174 
 
 O.lo 
 
 0.129 
 
 0.115 
 
 1 square foot, wooden beam construction, "1 as flooring, A'= 0.083 
 
 planked over, or ceiled : J as ceiling, A'= 0.104 
 
 1 square foot, fireproof construction, \ as flooring, K= 0.124 
 
 floored over : J as ceiling, A'= 0.145 
 
 1 square foot, single window K= 0.776 
 
 1 square foot, single skylight K= 1.118 
 
 1 square foot, double window A''= 0.518 
 
 1 square foot, double skylight K= 0.621 
 
 1 square foot, door K= 0.414 
 
 These coefficients are to be increased respectively, as follows: 
 
 Ten per cent, where the exposure is a northerly one and winds are to 
 be counted on as important factors. 
 
 Ten per cent, when the building is heated during the daytime only, and 
 the location of the building is not an exposed one. 
 
 Thirty per cent, when the building is heated during the daytime only, 
 and the location of the building is exposed. 
 
 Fifty per cent, when the building is heated during the winter months 
 intermittently, with long intervals (say days or weeks) of non-heating. 
 
 In using this table it is necessary to know the conditions as to tempera- 
 ture of adjoining buildings having the same party-wall and of the different 
 stories, cellar, attic, etc., of the building to be heated. Then with the plans 
 of the building at hand the total square feet of each kind of surface can be 
 measured and the estimate rapidly made from the diagram, Table No. 48, as 
 follows : 
 
 Find the difference in temperatures t — h on the lower horizontal line ; 
 run up the vertical line thus found until it intersects the diagonal line repre- 
 senting the kind of surface ; follow the horizontal line to the left and read on 
 the vertical scale the value of K (/ — /o). 
 
 F. i., 70° required in the room, temperature of adjoining hallway being 
 10°. Find difference 60°. The division wall being 24" ; run up on the 60'' 
 line to the diagonal for 24" wall, then follow the horizontal line to the left 
 and you fmd 12 H. U. as the value of K (/ — /o). Suppose there is a door in 
 the wall ; the 60° line strikes it midway between 24 and 26 on the vertical 
 scale, hence we have 25 H. U. for every square foot of door. 
 
 — 85 — 
 
For the amount of air which siiould be admitted to each room, Morin 
 gives 
 
 Table No. .-.o. 
 
 Cubic feet of air required for ventilation per head per liour. 
 
 Hospitals, ordinary maladies 2470 
 
 Hospitals, wounded, etc 3530 
 
 Hospitals, in times of epidemic 5300 
 
 Theatres 1585 
 
 Assembly rooms, prolonged sittings 2120 
 
 Prisons 1760 
 
 Workshops, ordinary 2120 
 
 Workshops, insalubrious conditions 3530 
 
 Barracks, day 1060, at night 1760 
 
 Infant schools 706 
 
 Adult schools 1410 
 
 Stables 7060 
 
 Having determined the total number of H. U. required for each room, 
 the kind and quantity of the radiating surface is next to be determined. 
 
 The character of the surfaces determines their efficiency. 
 
 Mr. P. Kaeuffer, M. E., of Mayence, Germany, has made a number of 
 careful experiments on radiating surfaces, the results of which, recalculated 
 for American units, we give in 
 
 Table no. 5i. 
 
 Transmission of heat by radiating surfaces, per square foot per hour in B.T.U. 
 
 Smooth vertical plane 406 
 
 Vertical plane with about 80% surface in ribs or corrugations 170 
 
 Smooth vertical pipe surface 480 
 
 Vertical tube with 67% of surface in corrugations 221 
 
 Horizontal smooth tube or pipe 369 
 
 Horizontal tube with 67% of surface in corrugations 185 
 
 Note, — This table is correct for steam of 15 to 22 pounds pressure ; for exhaust 
 steam reduce in proportion to temperature, except for corrugated and ribbed surfaces, 
 which lose very rapidly for low steam temperatures. For hot water, 50 per cent, of the 
 tabular numbers are approximately correct. 
 
 Approximately (for St. Louis conditions) 9 feet of 1" pipe with exhaust 
 steam, or 6 feet of 1" pipe with 50 pounds steam, Mill heat 1000 cubic feet 
 of air 70° per hour. 
 
 French practice is about 1 square foot of radiating surface for 230 cubic 
 feet of space for exhaust steam. This is about 13 feet run of 1" pipe for 
 1000 cubic feet of space. 
 
 Mr. Wolff gives 250 H. U. per hour per square foot surface for ordinary 
 bronzed cast iron radiators, and 400 H. U. for non-painted radiating surfaces, 
 counting steam pressure from 3 to 5 pounds per square inch. (About 60% 
 of these amounts for hot water heating.) When the total number of he a f 
 units required are known the work of the boiler can be directly estimated 
 from them ; bearing in mind that if the water condensed in the radiators is 
 returned to the boiler at 212°, we have in each pound of exhaust steam 965.8 
 heat units available, in steam of 2 pounds, 5 pounds, or 10 pounds gauge 
 pressure, we have 967.5 H. U., 969.7 H. U., or 974.1 H. U. respectively 
 per pound of steam delivered to the system. 
 
 — 87 — 
 
As we have seen by Table No. 51, the effectiveness of radiating sur- 
 faces varies too much to make it the basis of the amount of boiler power 
 required. Still, for rough approximations it is so used ; some experts esti- 
 mate a square foot of boiler-heating surface for every 7 or 10 square feet of 
 radiating surface ; some go as far as 1 to 15. Mr. Kaeuffer's estimates are 
 for about 1 square foot of boiler H. S. for 6 square feet of the best and 18 
 square feet of the poorest radiating surface. (See Table 51.) In roughly 
 estimating from the cubical contents of buildings, we must observe that 
 small buildings, having proportionately more exposed wall and window sur- 
 face per 1000 cubic feet of contents, require proportionately more boiler 
 power. And as the amount of ventilation necessary depends on the nature 
 of the use of the building, this also affects the amount of boiler power 
 required. 
 
 TABLE No. 52. 
 
 Approximate Number of Cubic Feet which 1 H. P. 
 in Boiler will Heat. 
 
 Hospitals, exposition buildings, etc., with much window 
 
 surface 6000 to 8000 
 
 Dwellings, stores, small shops, etc 8000 to 12000 
 
 Foundries, large workshops, etc 8000 to 16000 
 
 Theaters, schools, prisons, churches, etc 10000 to 18000 
 
 Armories, gymnasiums, etc 15000 to 25000 
 
 The remarks about increase in the value of K under Table No. 49 apply 
 directly to increase in boiler power for similar conditions. 
 
 Heating Liquids by Steam. 
 
 Liquids may be heated by blowing the steam into them through a num- 
 ber of small openings, or by passing the steam through a coil of pipe sub- 
 merged in the liquid, or by passing the steam through an external casing. In 
 the former case dilution results, and any impurities in the steam of course 
 enter into and foul the liquid. The latter two methods are therefore more 
 frequently adopted in practice. In heating water, it is found that the work 
 done per unit of surface and temperature is greatly increased when boiling 
 begins and evaporation takes place, even though the difference in temperature 
 be less. In this connection the experiments of Thos. Craddock are interest- 
 ing. A velocity of 3 feet per second of the water doubled the rate of trans- 
 mission in still water; he found that this circulation became more valuable 
 as the difference in temperatures became less. 
 
 The following table by Mr. Thos. Box illustrates this point. When 
 evaporation had set in and caused circulation^ the effectiveness of the surfaces 
 was trebled^ although the difference of temperature was only one-third of 
 that in the still water, an apparent nine-fold increase. 
 
Table no. 53. 
 
 Table of Experiments on the Power of Steam Cased Vessels 
 and Steam Pipes in Heating Water. 
 
 Box. 
 
 Temperature of the 
 water heated. 
 
 Teinp. 
 of the 
 Steam. 
 
 Difference of 
 Temperature of 
 Steam and Water. 
 
 Units per sq. ft. per hr. for 
 1'^ difference of temp. 
 
 
 
 By Experiment. 
 
 By Table. 
 
 Kind of Heater 
 
 
 Maxi- 
 mum. 
 
 Mean. 
 
 
 Mini- 
 mum. 
 
 Units. 
 
 Mean. 
 
 Units. 
 
 Mean. 
 
 
 Deg. 
 65 
 GO 
 69 
 
 39 
 46 
 
 » 
 
 Deg. 
 110 
 102^ 
 109>^ 
 
 212 
 
 212 
 
 Deg. 
 
 212 
 212 
 
 Deg. 
 212 
 212 
 212 
 
 274 
 274 
 
 274 
 250 
 
 Deg. Deg. 
 147 to 202 
 152 to 109 1. 
 143 to 1021^ 
 
 235 to 62 
 228 to 62 
 
 62 
 38 
 
 230 1 
 207 } 
 210 J 
 
 335 \ 
 315/ 
 
 974 \ 
 1020/ 
 
 216 
 
 325 
 
 997 
 
 r 216^ 
 
 \ 210 
 I 221 J 
 
 f 3251 
 I 333/ 
 
 f 1000 \ 
 1 1000 J 
 
 216 
 
 329 
 1000 
 
 r Vertical tube. 
 i Vertical tube. 
 I Vertical tube, 
 f Steam cased 
 < vessel, 
 i Worm. 
 /Worm. 
 I Worm. 
 
 * 
 
 
 
 
 *NoTK — These two results were evaporation of water already at 212° F., the preceding one 
 showing that only about one-third as much heat was transmitted in heating still water. 
 
 A remarkable fact was noted in some experiments in this line by Mr. 
 B. G. Nichol, in 1875, namely, that a horizontal position of the pipe was 
 more effective than a vertical one. This is the reverse of what is found in 
 heating air. (Compare Table No. 51, Kaeuffer.) 
 
 Safety Valves. 
 
 It was formerly the custom to proportion the Safety Valves according to 
 the heating surface. But as the performance per square foot of H. S. varies 
 widely in different boilers (from 2 to 15 lbs. hourly evaporation), the wiser 
 plan of giving the safety valves a fixed ratio to the grate area has been 
 adopted. 
 
 The United States Treasury Department, through its Board of Super- 
 vising Inspectors of Steam Vessels has established the following rules: 
 
 "Lever safety valves to be attached to marine boilers shall have an area 
 of not less than one square inch to two sqtiare feet of grate surface in the 
 boiler, and the seats of all such safety valves shall have an angle of inclina- 
 tion of 45° to the center line of their axes. 
 
 "The valves shall be so arranged that each boiler shall have one sepa- 
 rate safety valve, unless the arrangement is such as to preclude the possibility 
 of shutting off the communication of any boiler with the safety valve, or 
 valves employed. This arrangement shall also apply to lock-up safety 
 valves when they are employed. 
 
 "Any spring-loaded safety valves constructed so as to give an increased 
 lift by the operation of steam, after being raised from their seats, or any 
 spring-loaded safety valve constructed in any other manner, or so as to give 
 an effective area equal to that of the afore-mentioned spring-loaded safety 
 valve, may be used in lieu of the common lever-weighted valves on all 
 boilers on steam vessels, and all such spring-loaded safety valves shall be 
 required to have an area of not less than one square inch to three square 
 feet of grate surface of the boiler, and each spring-loaded safety valve shall 
 
 89 
 
O 
 i-, 
 
 OQ 
 
 o 
 CQ 
 
 3: 
 o 
 
 Du 
 X 
 
 8 
 
be supplied with a lever tliat will raise tlie valve from its seat a distance of 
 not less than that equal to one-eighth the diameter of the valve opening, and 
 the seats of all such safety valves shall have an angle of inclination to the 
 center line of their axis of 45\ But in no case shall any spring-loaded safety 
 valve be used in lieu of the lever-weighted safety valve without h-^ving first 
 been approved by the Board of Supervising Inspectors." 
 
 This rule, so far as it applies to lever-weighted safety valves, is identical 
 with the Board of Trade Rule of Great Britain. 
 
 It has, however, the one defect that it takes no account of the pressure 
 carried. And a safety valve of correct size for 50 lbs. pressure would be 
 more than three times too large for 200 lbs. pressure, and may become a 
 source of danger. 
 
 The Philadelphia Boiler Law takes this into account and orders that 
 the "least aggregate area of safety valve (being the least sectional area for 
 the discharge of steam) to be placed upon all stationarj^ boilers with natural 
 or chimney draft, may be expressed by the formula 
 
 ^ _ 22.5 G 
 
 P + 8.62 
 
 in which A is the area of combined safety valves in inches. G is area of 
 grate in square feet. P is pressure of steam in pounds per square inch to be 
 carried in the boiler above the atmosphere. The following table gives the 
 results of the formula for one square foot of grate as applied to boilers used 
 at different pressures. 
 
 TABLE No. 54. 
 Pressure per Square Inch. 
 
 10 
 1.21 
 
 20 
 0.79 
 
 30 
 0.58 
 
 40 50 
 0.46 0.38 
 
 60 
 0.33 
 
 70 
 0.29 
 
 80 
 0.25 
 
 90 
 0.23 
 
 100 1 110 
 0.21 19 
 
 120 
 0.17 
 
 150 
 0.142 
 
 175 
 0.123 
 
 Valve area in square inches, corresponding to one square foot of grate. 
 
 Horse-Power and Steam Consumption of Pumping Engines. 
 
 Multiply the number of million gallons pumped per 24 hours by the total 
 head (including suction head), expressed either in feet or in pounds. This 
 product multiplied by 0.176 if the head is stated in feet, or by 0.405 if the 
 head is given in pounds, will be the horse-power of work done by the water 
 end, or the horse-power of the water column. Thus f. i., a 15 million gallon 
 engine v/ith 260 ft. total head does 15x260x0.176 = 686.4 horse-power; 
 and a 15 million gallon engine raising water against a total pressure of 110 
 lbs. does 15x110x0.405 = 668.3 horse-power. It is the universal practice 
 among engineers to express the economic efficiency of a pumping engine by 
 what is called its "■ dicfy," i. e. the number of millions of foot pounds of 
 work it will do for every hundred pounds of coal burned under the boilers. 
 
 Generally specifications base the duty to be guaranteed on an assumed 
 evaporation of 10:1 or state that for every 1000 lbs. of steam (measured by 
 the boiler feed-water) such duty is to be given. 
 
 Either method fails to define where the duty of the boiler ends and that 
 of the engine begins, since neither states from what temperature of feed to 
 what pressure of steam the boilers are to evaporate. 
 
 By the established practice among mechanical engineers, boiler per- 
 formances are compared as to economy on the basis of evaporation from and 
 
 91 
 
at 212° F. In the absence of any specific statement the assumed evaporation 
 of 10 to 1 would, therefore, be thus construed, and as this is about the best 
 performance that can be safely counted on per pound of best coal, It virtually 
 becomes the basis of calculation, 
 
 A pumping engine of 100 million duty will require 19.8 lbs. feed-water 
 per hour per horse-power of work in water column, based on an evaporation 
 of 10 lbs. water per pound of coal from and at 212° F. 
 
 Bui as pumping engines are constructed for steam pressures varying 
 from 75 lbs. for high pressure single cylinder engines to 175 pounds for 
 triple expansion ; and as the feed-water may be, say 100° F. the temperature 
 of the hot well, or 212° F. from a good exhaust heater, the amount of feed- 
 water required by the engine per horse-power per hour will vary according 
 to these conditions. 
 
 The higher the steam pressure the greater the amount of energy avail- 
 able in each pound of steam. The lower the feed temperature the larger the 
 proportion of the boiler's work which had to be expended in merely heating 
 the water up to the boiling-point. On this basis the following table has 
 been figured : 
 
 Table No. 55. 
 
 Showing Lbs. Feed-Water per Horse-power required by 
 Pumping Engines per Hour. 
 
 E. D. M. 
 
 Duty. 
 
 From Feed at 212" F. to Steam of : 
 
 5 lbs. 100 lbs. 125 lbs. 150 lbs. 175 lbs 
 
 From Feed at 100° F. to Steam of: 
 
 75 lbs. 
 
 100 lbs. 125 lbs. 
 
 150 lbs. 175 lbs. 
 
 Equivalent 
 to Boiler 
 Work in 
 U. ofE..or 
 
 Pounds 
 
 from andat 
 
 212° F. 
 
 110 Mill, 
 
 100 Mill. 
 
 90 Mill. 
 
 80 Mill, 
 
 70 Mill, 
 
 60 Mill, 
 
 50 Mill, 
 
 17.37 
 19.11 
 21.23 
 23.90 
 27.30 
 31.85 
 38.22 
 
 17.30 
 19.03 
 21.14 
 23.80 
 27.19 
 31.71 
 38.06 
 
 17.23 
 18.95 
 21.06 
 23.70 
 
 27.07 
 31.58 
 37.90 
 
 17.16 
 18.87 
 20.97 
 23.60 
 26.96 
 31.45 
 37.74 
 
 17, 
 
 18, 
 20. 
 23, 
 26, 
 31, 
 37. 
 
 15.64 
 17.20 
 19.11 
 21.50 
 24.57 
 28.67 
 34.40 
 
 57 
 12 
 02 
 40 
 ,46 
 ,53 
 24 
 
 15.50 
 17.05 
 18.94 
 21.31 
 24.36 
 28.42 
 34.10 
 
 15.44 
 16.98 
 18.87 
 21.22 
 24.26 
 28.30 
 33.96 
 
 .38 
 ,92 
 ,80 
 ,15 
 ,17 
 ,20 
 ,84 
 
 18.00 
 19.80 
 22.00 
 24.75 
 28.29 
 33.00 
 39.60 
 
 Note. The horse-power is the H. P. of the water column. The evaporation is 
 assumed at 10 lbs. water from and at 212° F. per lb. of coal. 
 
 Economy in boilers is always stated in '' pounds of water evaporated from 
 and at IVT F. per pound of fuel,'" designated as ''■Units of Evaporation.^^ 
 (See Vol. VI, Transactions Am. Soc. M. E.— 1881). 
 
 Unless a contract specifically provides otherwise the '■'assumed evapora- 
 tion''' is to be so understood. 
 
 The last vertical column of the table gives the equivalent work for the 
 boiler in each case per horse-power of the water column ; in fact, all the 
 figures in each horizontal line are exact equivalents of each other. Again, 
 comparing the vertical columns with each other it is clear that an engine pro- 
 
 — 92— 
 
vided with a first-class feed-water heater will save 11.1% over the same 
 engine relying simply on its hot well. 
 
 Given an assumed evaporation per pound of such coal as the guarantee 
 is based on ; or the evaporation found by actual test of the boilers. Divide 
 the figure in the last vertical column by such evaporation, and you have 
 the number of pounds of the coal per horse-power in each case. 
 
 E. D. M. 
 
 Condensers. 
 
 H. R. W. 
 
 When steam expands in the cylinder of a steam engine, its pressure 
 gradually reduces, and ultimately becomes so small that it cannot profitably 
 be used for driving the piston. At this stage a time has arrived when the 
 attenuated vapor should be disposed of by some method, so as not to exert 
 any back pressure or resistance to the return of the piston. If there were 
 no atmospheric pressure, exhausting into the open air would effect the desired 
 object. But, as there is in reality a pressure of about 14.7 pounds per 
 square inch, due to the weight of the super-incumbent atmosphere, it follows 
 that steam in a non-condensing engine cannot economically be expanded be- 
 low this pressure, and must eventually be exhausted against the atmos- 
 phere, which exerts a back pressure to that extent. 
 
 It is evident that if this back pressure be removed, the engine will not 
 only be aided, by the exhausting side of the piston being relieved of a resis- 
 tance of 14.7 pounds per square inch, but moreover, as the exhaust or release 
 of the steam from the engine cylinder will be against no pressure, the steam 
 can be expanded in the cylinder quite, or nearly, to absolute of pressure, 
 and thus its full expansive power can be obtained. 
 
 Contact, in a closed vessel, with a spray of cold water or with one side 
 of a series of tubes, on the other side of which cold water is circulating, de- 
 prives the steam of nearly all its latent heat, and condenses it. In either 
 case the act of condensation is almost instantaneous. A change of state oc- 
 curs, and the vapor steam is reduced to liquid water. As this water of con- 
 densation only occupies about one sixteen-hundredths of the space filled by 
 the steam from which it was formed, it follows that the remainder of the 
 space is void or vacant, and no pressure exists. Now, the expanded steam 
 from the engine is conducted into this empty or vacuous space, and, as it 
 meets with no resistance, the very limit of its usefulness is reached. 
 
 The vessel in which this condensation of steam takes place is the con- 
 densing chamber. The cold water that produces the condensation is the in- 
 jection water; and the heated water, on leaving the condenser is the dis- 
 charge water. 
 
 To make the action of the condensing apparatus continuous, the flow of 
 the injection water, and the removal of the discharge water including the 
 water from the liquifaction of the steam, must likewise be continuous. 
 
 The vacuum in the condenser is not quite perfect, because the cold in- 
 jection water is heated by the steam, and emits a vapor of a tension due to 
 the temperature. When the temperature is no degrees Fahrenheit, the 
 tension or pressure of the vapor will be represented by about 4" of mercury ; 
 that is, when the mercury in the ordinary barometer stands at 30", a barom- 
 eter with the space above the mercury communicating with the condenser, 
 
 — 93 — 
 
Cape Town Tramways Co., Limited, 
 
 CAPE TOWN, AFRICA. 
 
 900 H. P. of Heine Boilers. 
 
will stand at about 26". The imperfection of vacuum is not wholly tracea« 
 ble to the vapor in the condenser, but also to the presence of air, a small 
 quantity of which enters with the injection water and with the steam ; the 
 larger part, however, comes through air leaks and faulty connections and 
 badly packed stuffing boxes. The air would gradually accumulate until it 
 destroyed the vacuum, if provision were not made to constantly withdraw itj, 
 together with the heated water, by means of a pump. 
 
 The amount of water required to thoroughly condense the steam from 
 an engine is dependent upon two conditions : the total heat and volume of 
 the steam, and the temperature of the injection water. The former repre- 
 sents the work to be done, and the latter the value of the water by whose 
 cooling agency the work of condensation of the steam is to be accomplished. 
 Generally stated, with 26" vacuum, the injection water at ordinary tempera- 
 ture, not exceeding 70 degrees Fahrenheit, from 20 to 30 times the quantity 
 of water evaporated in the boilers will be required for the complete liquifac- 
 tion of the exhaust steam. The efficiency of injection water decreases very 
 rapidly as its temperature increases, and at 80 degrees and 90 degrees 
 Fahrenheit, very much larger quantities are to be employed. Under the 
 conditions of common temperature of water and a vacuum of 26" of mercury, 
 the injection water necessary per H. P. developed by the engine, will be 
 from li gallons per minute when the steam admission is for one-fourth of the 
 stroke, up to 2 gallons per minute when the steam is carried three-fourths ol 
 the stroke of the eng-ine. 
 
 The power exerted by a steam engine during a single stroke of a piston, 
 is due directly to the difference between the pressures on the opposite sides 
 of the piston. Newton said, " all force is vis atergo;" — a push from be- 
 hind. A vacuum does not in itself give power. It only effects a removal of 
 resistance from the retreating side of the piston, and consequently adds just 
 so much activeness to the other, or pushing side. The value of a vacuum of 
 26" of mercury to an engine, may be generally approximated by considering 
 it to be equivalent to a net gain of 12 lbs. average pressure per square inch 
 of piston area. It is obvious that this amount of power gained bears nearly 
 the same ratio to the power developed by the engine when non-condensing, 
 as 12 lbs. does to the mean effective, or average pressure of the steam in the 
 cylinder. So, if the mean effective pressure is known, a close idea of the 
 percentage of gain that will be derived by the use of a vacuum with a non- 
 condensing engine, may be arrived at. 
 
 By the use of Watt's formula, in which, 
 
 A = Area of piston in square inches. 
 
 V = Velocity of piston in feet per minute. 
 
 M. E. P. = Mean effective pressure of the steam in pounds per square 
 inch on the piston. 
 
 AXVXM.E.P. „ p 
 
 ■ 38000 = Horsepower. 
 
 And by substituting 12 for M. E. P., the value of vacuum of 12 lbs. ex- 
 pressed in horse power is found. 
 
 Ax Vxl2 
 
 — ^ — ■= Horse power made available by vacuum. 
 
 — 95 — 
 
Table of Mean Effective Pressures. 
 
 The following graphical table will afford a ready and comprehensive 
 means of ascertaining the mean effective pressure of steam in an engine 
 cylinder when the initial steam pressure and point of cut-off, or the number 
 of expansions of the steam, are known. 
 
 It should be borne in mind that " absolute pressure" is calculated from 
 the absolute vacuum of the barometer, while " gauge pressure " as indicated 
 by the ordinary pressure gauge, begins with atmospheric pressure as its zero ; 
 consequently "absolute pressure" is nearly 15 pounds greater than " gauge 
 pressure." 
 
 TABLE NO. 56. 
 
 Mean Effective Pressures. 
 
 NOi OF EXPANSIONS "[t^l '^|"|'-|^| "1 ^ °i ^ "^l "> ■i*| •* 
 
 1 "1 
 
 J 
 
 POINTS OF CUT OFF ^0 ?5 20 is IB iV 12 10 1 s" 7 "g t i 9 8 '2" If 4F1JIl! 
 
 200 
 
 190 
 
 180 
 
 170 
 
 160 
 
 150 
 
 ^140 
 
 |l30 
 O 
 
 5120 
 
 qEioo 
 
 K 90 
 
 z 
 
 S ^' 
 
 m 
 *60 
 
 50 
 
 40 
 
 30 
 
 20 
 
 10 
 
 / / III/ / MEAN'eFF'ECTIVEPRESS^liRE IN POUNDS / / / // / / \ 
 10 SO 30/ 40/ 50/ 60 Ao/ 80 /if, /lOO /110 120 130 140 150 160 1^ 180 /igO/ZOn | 
 
 
 
 
 
 
 
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 120 60 40 30 25 20 17 15 13 12 11 10 
 
 PER CENT OF POWER GAINEC BY VACUUM 
 
 
 (From Special Catalogue of The Worthington Condenser.) 
 
 The left hand vertical column of figures gives the initial (absolute) 
 steam pressure, and the upper horizontal row, the number of expansions 
 that correspond to the several points of cut-off ; directly under this is a 
 similar one of the mean effective pressures. 
 
 96 
 
To determine the M. E. P. produced in an engine cylinder witii an 
 initial pressure of 90 pounds steam (gauge pressure), cut-off at one-quarter 
 stroke, expanded and finally exhausted into a vacuum ; add 15 to 90, and find 
 105 in the initial pressure column ; follow the horizontal line to the right 
 until it intersects the oblique line which corresponds to ^ cut-off. Then read 
 the M. E. P. from the row of figures directly above, which in this case is 63 
 pounds. 
 
 If, as in a non-condensing engine, the steam is exhausted against atmos- 
 pheric pressure, this 63 pounds M. E. P. should be reduced by 15 pounds, 
 giving 48 pounds as the net result.* 
 
 By glancing down and reading on the lower scale the figures directly 
 under the 48 pounds M. E. P. on the upper row, will be seen the percentage of 
 power that a vacuum will add to an engine using 90 pounds "gauge pressure " 
 steam, cut-off at one-quarter stroke. Thus, in this instance, the value of 
 the vacuum is found to be between 25 and 30 per cent of the power of the 
 engine when running non-condensing. 
 
 H. R. W. 
 
 *NOTE. — In condensing engines it will be safer to deduct from 3 to 5 pounds for 
 imperfect vacuum, etc., and in non-condensing engines 16 to 18 pounds in place of 15 
 for back pressure, etc. 
 
 E. D. M. 
 
 Minneapolis Industrial Exposition Building, Minneapolis, Minn., 
 With Heine Boiler Plant of 1000 H. P. 
 
 NOTE ON BOILER TESTS :— Table No. 57 gives the results of thirty-three tests made 
 with various coals. To justly estimate the efticiency of the boiler from same, compare the 
 heat values of the coals as given in Table 12. 
 
 — 97 
 
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 —98— 
 
CODE OF RULES FOR BOILER TESTS. 
 
 Recommended by the American Society of Mechanical Engineers, November, 1884. 
 
 A Committee of the Society is now engaged on a new and more complete Code of Rules, 
 which is to suggest Standard Coals for different localities. 
 
 Starting and Stopping a Test. 
 
 A test should last at least ten hours of continuous running, and twenty- 
 four hours whenever practicable. The conditions of the boiler and furnace 
 in all respects should be, as nearly as possible, the same at the end as at the 
 beginning of the test. The steam pressure should be the same, the water- 
 level the same, the fire upon the grates should be the same in quantity and 
 condition, and the walls, flues, etc., should be of the same temperature. To 
 secure as near an approximation to exact uniformity as possible in conditions 
 of the fire and in the temperatures of the walls and flues, the following 
 method of starting and stopping a test should be adopted : 
 
 Standard Method. — Steam being raised to the working pressure, remove 
 rapidly all the fire from the grate, close the damper, clean the ash-pit, and 
 as quickly as possible, start a new fire with weighed wood and coal, noting 
 the time of starting the test and the height of the water-level while the 
 water is in a quiescent state, just before lighting the fire. 
 
 At the end of the test, remove the whole fire, clean the grates and ash- 
 pit, and note the water-level when the water is in a quiescent state ; record 
 the time of hauling the fire as the end of the test. The water-level should 
 be as nearly as possible the same as at the beginning of the test. If it is not 
 the same, a correction should be made by computation, and not by operating 
 pump after test is completed. It will generally be'necessary to regulate the 
 discharge of steam from the boiler tested by means of the stop-valve for a 
 time while fires are being hauled at the beginning and at the end of the test, 
 in order to keep the steam pressure in the boiler at those times up to the 
 average during the test. 
 
 Alternate Method. — Instead of the Standard Method above described, 
 the following may be employed where local conditions render it necessary : 
 
 At the regular time for slicing and cleaning fires have them burned 
 rather low, as is usual before cleaning, and then thoroughly cleaned ; note 
 the amount of coal left on the grate as nearly as it can be estimated ; note 
 the pressure of steam and the height of the water-level — which should be at 
 the medium height to be carried throughout the test — at the same time ; and 
 note this time as the time of starting the test. Fresh coal, which has been 
 weighed, should now be fired. The ash-pits should be thoroughly cleaned 
 at once after starting. Before the end Of the test the fires should be burned 
 low, just as before the start, and the fires cleaned in such a manner as to 
 leave the same amount of fire, and in the same condition, on the grates as at 
 the start. The water-level and steam pressure should be brought to the 
 same point as at the start, and the time of the ending of the test should be 
 noted just before fresh coal is fired. 
 
 — 99 — 
 
o 
 03 
 
 u — .b 
 ■z: (J "^ 
 
 ^ Ce: £X 
 f O • 
 
 o 
 o 
 o 
 
 o 
 
Durinir the Test, 
 
 Keep the Co7iditio7is Uniform. — The boiler should be run continuously, 
 without stopping for meal-times or for rise or fall of pressure of steam due to 
 change of demand for steam. The draught being adjusted to the rate of 
 evaporation or combustion desired before the test is begun, it should be 
 retained constant during the test by means of the damper. 
 
 If the boiler is not connected to the same steam-pipe with other boilers, 
 an extra outlet for steam with valve in same should be provided, so that in 
 case the pressure should rise to that at which the safety valve is set, it may 
 be reduced to the desired point by opening the extra outlet, without checking 
 the fires. 
 
 If the boiler is connected to a main steam-pipe with other boilers, the 
 safety valve on the boiler being tested should be set a few pounds higher 
 than those of the other boilers, so that in case of a rise in pressure the other 
 boilers may blow off, and the pressure be reduced by closing their dampers, 
 allowing the damper of the boiler being tested to remain open, and firing as 
 usual. 
 
 All the conditions should be kept as nearly uniform as possible, such as 
 force of draught, pressure of steam, and height of water. The time of clean- 
 ing the fires will depend upon the character of the fuel, the rapidity of com- 
 bustion, and the kind of grates. When very good coal is used, and the 
 combustion not too rapid, a ten-hour test may be run without any cleaning 
 of the grates, other than just before the beginning and just before the end 
 of the test. But in case the grates have to be cleaned during the test, the 
 intervals between one cleaning and another should be uniform. 
 
 Keeping the Records. — The coal should be weighed and delivered to the 
 firemen in equal portions, each sufficient for about one hour's run, and a 
 fresh portion should not be delivered until the previous one has all been fired. 
 The time required to consume each portion should be noted, the time being 
 recorded at the instant of firing the first of each new portion. It is desirable 
 that at the same time the amount of water fed into the boiler should be 
 accurately noted and recorded, including the height of the water in the boiler, 
 and the average pressure of steam and temperature of feed during the time. 
 By thus recording the amount of water evaporated by successive portions of 
 coal, the record of the test may be divided into several divisions, if desired, 
 at the end of the test, to discover the degree of uniformity of combustion, 
 evaporation, and economy at different stages of the test. 
 
 Priming Tests. — In all tests in which accuracy of results is important, 
 calorimeter tests should be made of the percentage of moisture in the steam, 
 or of the degree of super-heating. At least ten such tests should be made 
 during the trial of the boiler, or so many as to reduce the probable average 
 error to less than one per cent, and the final records of the boiler test cor- 
 rected according to the average results of the calorimeter tests. 
 
 On account of the difficulty of securing accuracy in these tests the greatest 
 care should be taken in the measurements of weights and temperatures. 
 The thermometers should be accurate to within a tenth of one degree, and 
 the scales on which the water is weighed to within one-hundreth of a pound. 
 
 —101— 
 
Analyses of Gases. Measurement of Air Supply, Etc. 
 
 In tests for purposes of scientific research, in which the determination of 
 all the variables entering into the test is desired, certain observations should 
 be made which are in general not necessary in tests for commercial purposes. 
 These are the measurement of the air supply, the determination of its 
 contained moisture, the measurement and analysis of the flue gases, the 
 determination of the amount of heat lost by radiation, of the amount of infil- 
 tration of air through the setting, the direct determination by calorimeter 
 experiments of the absolute heating value of the fuel, and (by condensation 
 of all the steam made by the boiler) of the total heat imparted to the water. 
 
 The analysis of the flue gases is an especially valuable method of deter- 
 mining the relative value of different methods of firing, or of different kinds 
 of furnaces. In making these analyses great care should be taken to procure 
 average samples, since the composition is apt to vary at different points of 
 the flue, and the analyses should be intrusted only to a thoroughly competent 
 chemist, who is provided with complete and accurate apparatus. 
 
 As the determination of the other variables mentioned above are not 
 likely to be undertaken except by engineers of high scientific attainments, and 
 as apparatus for making them is likely to be improved in the course of scien- 
 tific research, it is not deemed advisable to include in this code any specific 
 directions for making them. 
 
 Record of the Test. 
 
 A " log " of the test should be kept on properly prepared blanks con- 
 taining headings as follows : 
 
 Table No. 58. 
 
 
 Pressures. 
 
 Temperatures. 
 
 Fuel. 
 
 Feed Water. 
 
 Time. 
 
 E 
 o 
 « 
 
 <u 
 
 « 
 
 E 
 
 B 
 V 
 
 Cn 
 
 be 
 
 3 
 u 
 
 Q 
 
 '3 
 
 c 
 ■2 
 
 E 
 o 
 o 
 
 o 
 OQ 
 
 D 
 
 U. 
 
 
 e 
 
 ijr> 
 
 E 
 
 •a 
 
 c 
 p 
 
 E 
 
 3 
 O 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Reporting the Trial. 
 
 The final results should be recorded upon a properly prepared blank, 
 and should include as many of the following items as are adapted for the 
 specific object for which the trial is made. The items marked with a * may 
 be omitted for ordinary trials, but are desirable for comparison with similar 
 data from other sources. 
 
 -102- 
 
Table No. so. 
 
 Results of the trials of a- 
 
 Boiler at 
 
 To determine 
 
 1. Date of trial --- 
 
 2. Duration of trial 
 
 *9. 
 10. 
 
 "11. 
 "12. 
 "13. 
 
 14. 
 
 15. 
 
 16. 
 17. 
 18. 
 19. 
 20. 
 
 *21. 
 *22. 
 
 23. 
 24. 
 25. 
 
 26. 
 
 27. 
 
 28. 
 
 ♦29. 
 t30. 
 
 31. 
 32. 
 33. 
 
 34. 
 
 Dimensions and proportions. 
 (Leave space for complete description). 
 
 Grate-surface wide long area -- 
 
 Water-heating surface 
 
 Superheating-surface 
 
 Ratio of water-heating surface to grate-surface- 
 
 AVERAGE PRESSURES. 
 
 Steam-pressure in boiler, by gauge 
 
 Absolute steam-pressure 
 
 Atmospheric pressure, per barometer 
 
 Force of draught in inches of water 
 
 AVERAGE TEMPERATURES. 
 
 Of external air 
 
 Of fire-room 
 
 Of steam 
 
 Of escaping gases- 
 Of feed-water 
 
 FUEL. 
 
 Total amount of coal consumed 
 
 Moisture in coal 
 
 Dry coal consumed 
 
 Total refuse, dry pounds= 
 
 Total combustible (dry weight of coal, item 18, less 
 
 refuse, item 19') 
 
 Dry coal consumed per hour 
 
 Combustible consumed per hour 
 
 RESULTS OF CALORIMETRIC TESTS. 
 
 Quality of steam, dry steam being taken as unity-. 
 
 Percentage of moisture in steam 
 
 Num.ber of degrees superheated 
 
 WATER. 
 
 Total weight of water pumped into boiler and ap 
 
 parently evaporated 
 
 Water actually evaporated, corrected for quality of 
 
 steam 
 
 Equivalent water evaporated into dry steam from 
 
 and at 212^ F 
 
 Equivalent total heat derived from fuel in B. T. U-- 
 Equivalent water evaporated into dry steam from 
 
 and at 212'^^ F. per hour 
 
 Economic Evaporation. 
 
 Water actually evaporated per pound of dry coal, 
 from actual pressure and temperature 
 
 Equivalent water evaporated per pound of dry coal, 
 from and at 212^ F 
 
 Equivalent water evaporated per pound of combusti- 
 ble from and at 212° F __ 
 
 Commercial Evaporation. 
 
 Equivalent water evaporated per pound of dry coal 
 with one-sixth refuse, at 70 lbs. gauge pressure, 
 from temperature of 100' F. = item 3^X0.7249 
 pounds 
 
 hours. 
 
 sq. ft. 
 sq. ft. 
 sq. ft. 
 
 lbs. 
 lbs. 
 in. 
 in. 
 
 deg. 
 deg. 
 deg. 
 deg. 
 deg. 
 
 lbs. 
 per cent. 
 
 lbs. 
 per cent. 
 
 lbs. 
 lbs. 
 lbs. 
 
 per cent, 
 deg. 
 
 lbs. 
 
 lbs. 
 
 lbs. 
 B. T. U. 
 
 lbs. 
 
 lbs. 
 lbs. 
 lbs. 
 
 lbs. 
 
 t Corrected for inequality of water level and of steam pressure at beginning and end 
 of test. 
 
 —103— 
 
Table No. 59.— Continued. 
 
 35. 
 
 ^38. 
 
 39. 
 
 *40. 
 *41. 
 *42. 
 
 43. 
 
 44. 
 45. 
 
 RATE OF COMBUSTION. 
 
 Dry coal actually burned per square foot of grate- 
 surface per hour 
 
 1 Per sq. ft. of grate 
 
 Consumption of dry coal Per^sn^^V'of water 
 per hour. Coal assumed [ heltinhurfrce 
 with one-sixth refuse. I Pe'j^^J.^ft.'ofleast' 
 
 area for draught.. 
 RATE OF EVAPORATION. 
 
 Water evaporated from and at 212° F. per square foot 
 of heating surface per hour 
 
 Water evaporated per hour 
 from temperature of 100° 
 F. into steam of 70 lbs. 
 gauge pressure. 
 
 Per sq. ft. of grate- 
 surface 
 
 Per sq. ft. of heat- 
 ing surface 
 
 Per sq. ft. of least 
 area for draught.. 
 
 COMMERCIAL HORSE-POWER. 
 
 On basis of 30 lbs. of water per hour evaporated 
 from temperature of 100° F. into steam of 70 lbs. 
 gauge pressure (34^2 lbs. from and at 212°) 
 
 Horse-power, builders' rating, at square feet 
 
 per horse-power , 
 
 Per cent, developed above, or below, rating 
 
 lbs. 
 lbs. 
 lbs. 
 lbs. 
 
 lbs. 
 lbs. 
 lbs. 
 lbs. 
 
 H. P. 
 
 H. P. 
 
 per cent. 
 
 Note.— Items 20, 22, 33, 34, 36, 37, 38 are of little practical value. For if the result 
 proves to be less satisfactory than expected on the actual coal, it is easy for an expert 
 fireman to decrease No. 20 by simply raking out some partly-consumed coal in cleaning 
 fires, and thus making a fine showing on that simply ideal or theoretical unit, the "pound 
 combustible." The question at issue is always what can be done with an actual coal, not 
 the '"''as-sHmed coal" of items 34, 36, 37 and 38. 
 
 E. D. M. 
 
 Hauling a 250 H. P. Heine Boiler up a Mountain. 
 
CONDENSATION OF STEAM IN PIPES. 
 
 When steam pipes are exposed to the open air, the steam condenses 
 more or less rapidly, according to the condition of the surfaces and the 
 temperature and rate of motion of the air. This loss is quite serious in 
 itself and further increases the losses by cylinder condensation, as indicated 
 on page 77. 
 
 Experiments made by different parties in still air gave the following 
 results : 
 
 TABLE No. 60. 
 
 Condensation in Uncovered Pipes. 
 
 OBSERVER. 
 
 Difference of 
 
 Temperature of Steam 
 
 and Air. 
 
 Steam Condensed 
 
 per Square Foot per 
 
 Hour, per 1° F. 
 
 H. U. Lost per 
 
 Square Foot per Hour, 
 
 per l" F. 
 
 Tregold 
 
 161° F. 
 196.6° F. 
 151° F. 
 168° F. 
 
 0.0022 lb. 
 0.0030 lb. 
 0.00217 lb. 
 0.0020 lb. 
 
 2.100 
 
 Burnat 
 
 2.864 
 
 Clement 
 
 2.071 
 
 Grouvelle 
 
 1.909 
 
 
 
 Average for steam of 20 
 lbs. absolute pressure 
 
 169° F. 
 
 0.00235 lb. 
 
 2.236 
 
 We further give an abstract of the results of a careful series of tests 
 made by Mr. George M. Brill, M. E., in 1895, with the best modern cover- 
 ings, and with the most accurate instruments. The steam pressure carried 
 ran between 110 and 119 lbs. per square inch, and the temperature of the 
 air varied from 50° to 81° F. in the various tests. 
 
 For the purposes of these tests about 60 feet of standard 8 -inch wrought 
 pipe, coupled together, in order to make it smooth and regular, was sus- 
 pended where it could not be subjected to currents of air. In order to get 
 the steam as dry as possible it was sent through a separator on its way to 
 the test pipe, and in the short connection between the separator and the 
 pipe was placed a throttling calorimeter. The test pipe had an inclination 
 of one foot in its entire length, which insured drainage of all the water of 
 condensation to the lower end, at which point the receiver was connected, 
 and into which the water gravitated as rapidly as formed. The water was 
 measured in this receiver, which consisted of four feet of 12 -inch pipe, with 
 graduated water glasses attached near the top and bottom. The same vol- 
 ume of water was allowed to collect each time, was measured under the 
 steam pressure, and blown from the receiver at the end of the run. A care- 
 ful determination was made of the amount of water collected by weighing 
 the same volume while cold, and correcting for difference in weight due to 
 the difference in temperature for the respective runs. 
 
 -106— 
 
The tests were made upon a scale large enough — in fact, upon a pipe 
 of the size and length which is very common in the average power plant — 
 with sufficient care, and in a manner to insure accuracy in the results ob- 
 tained, and are consequently of much interest and value to all users of 
 steam. 
 
 The results reduced to the proper units are given in Table No, 61 
 below, and may be taken as fairly representative of the best modern prac- 
 tice. Of course, whenever steam pipes are placed where they are exposed 
 to currents of air, the amount of condensation will be much greater than the 
 tabular numbers. 
 
 This table also gives the saving in pounds of steam, and in dollars and 
 cents due to the use of coverings. This saving is based on the assumption 
 that coal costs ;^2.44 per ton, and adding 12 per cent for cost of firing, and 
 taking 7 lbs. water per lb. of coal as an evaporative figure, which are rough 
 approximations to average American conditions. 
 
 TABLE NO. 6i. 
 
 Showing Radiation Due to Bare and Covered Pipes, and Sav- 
 ing Due to Coverings. 
 
 KINDS OF COVERING. 
 
 B. T. U. Transmitted 
 per Hour per Square 
 Foot Pipe per Degree 
 Difference in Temper- 
 ature. 
 
 Lbs. Steam Condensed 
 per Hour per Square 
 Foot Pipe per Degree 
 Difference in Temper- 
 ature. 
 
 J- 01 
 
 S..S- 
 
 > V 
 
 ,« o ■- 
 
 ^2 S. 
 
 c a C 
 — D « 
 
 Bare Pipe 
 
 2.7059 
 .3838 
 .2556 
 .2846 
 .5023 
 .3496 
 
 .2119 
 .3448 
 .3166 
 .4220 
 .9531 
 .8787 
 
 .003107 
 .000432 
 .000285 
 .000311 
 .000591 
 .000409 
 
 .000243 
 .000410 
 .000364 
 .000472 
 .001089 
 .001010 
 
 
 
 Magnesia 
 
 635,801 
 670,666 
 662,957 
 603,389 
 645,174 
 
 682,930 
 646,488 
 654,197 
 625,376 
 479,960 
 500,284 
 
 $110.82 
 
 Rock Wool 
 
 116.90 
 
 Mineral Wool 
 
 115.55 
 
 Fire Felt 
 
 Manville Sectional 
 
 Manville Sectional and 
 
 Hair Felt 
 
 Manville Wool Cement.. 
 Champion Mineral Wool, 
 
 Hair Felt 
 
 Riley Cement 
 
 Fossil Meal 
 
 105.17 
 112.45 
 
 119.03 
 112.68 
 114.03 
 109.00 
 83.66 
 87.20 
 
 
 
 The presence of sulphur in the best coverings and its recognized injur- 
 ious effects, makes it imperative that moisture must be kept from the cov- 
 erings, for if present, will surely combine with the sulphur, thus making it 
 active. This could be stated in other words, keep the pipes and coverhi^ in 
 good repair. Much of the inefficiency of coverings is due to the lack of 
 attention given them ; they are often seen hanging loosely from the pipe 
 which they are supposed to protect. 
 
 —107— 
 
All coverings should be looked after at least once a year and given nec- 
 essary repairs, refitted to the pipe, the spaces due to shrinkage taken up, 
 for little can be expected from the best non-conductors if they are allowed 
 to become saturated with water, or if air currents are permitted to circulate 
 between them and the pipe. 
 
 As a very rough approximation we may say that each 10 square feet of 
 uncovered pipe will condense, in winter, 105 lbs. of steam during a day of 
 ten hours. Under the same conditions, the same pipe protected with the 
 best covering will condense approximately 8i lbs. steam. 
 
 In summer these figures will be reduced respectively to 80 lbs. and 
 6 J lbs, of steam. 
 
 Moisture in steam at the end of a long pipe line is often erroneously 
 attributed to priming of the boiler; whereas, it is really due to condensation. 
 The amount of steam condensed is really but a very small proportion of the 
 total steam passing through the pipe, but gradually collecting at some point 
 in the line, it is carried along in a body at intervals, producing the effects 
 of entrained water. 
 
 Denver Consolidated Electric Light Co., 
 
 DENVER, COLO. 
 
 Contains 3500 H. P. of Heine Boilers. 
 
 -108— 
 
CHIMNEYS AND DRAFT. 
 
 According to Data and Rules given in our article on Combustion (p. 13, 
 etc.)? we find that from 12 to 14 lbs. of air are required per pound of coal. 
 Anthracites require the least, bituminous coals more in proportion to their 
 excess in volatile constituents. Most authorities consider a surplus of air 
 requisite for complete combustion, so that a total amount varying from 18 to 
 24 lbs. of air per pound of coal is advised by various authors. 
 
 Taking 13 lbs. as the average amount of air chemically required, and 
 the air at 62° F. and chimney gases at 500° F., this means that in order to 
 attain perfect combustion we must sacrifice from 6 to 12 per cent of the calo- 
 rific value of every pound of coal we burn in drawing " surplus " air through 
 the furnace. Besides this, there is a loss in the cooling of the gases, and 
 thus lessening the quantity of heat transmitted to the boiler. A thorough 
 mixture of the air and the coal gas would do away with the necessity of most 
 of this surplus air and thus prevent these losses. We have seen (pp. 14, 
 15) that an increase in the rate and temperature of combustion reduces the 
 proportion of surplus air required. This means reduced grate area and in- 
 creased draft, and points to high chimneys. 
 
 What we call draft is simply the fall of the heavier (because colder) 
 outside air to supply the place of the lighter (because heated) gases which 
 rise from the furnace to escape through the chimney. We cause it artificially 
 in a furnace just as wind is caused by the heat of the sun in nature. 
 
 The difference in weight of the column of hot gas in the chimney and 
 that of a column of the outside air of the same height is the force which 
 causes the draft. 
 
 It is customary to measure the draft in inches of water. We will assume 
 the external air to be at 62° F. and that in the chimney at 500° F. A cubic 
 foot of air at 62° F. weighs 0.0761 lbs.; and at 500° it weighs 0.041 3 lbs.; the 
 difference is 0.0348 lbs. For a chimney 100 ft. high we would have on every 
 square foot of its cross section at the bottom an upward pressure of 100 times 
 0.0348 lbs. = 3.48 lbs. A cubic foot of water at 62° F. weighs 62.32 lb., 
 i. e., a column of water 12" high exerts a pressure of 62.32 lbs. per square 
 foot on its base; i" of water therefore means a pressure of 5.193 lbs. on a 
 square foot or one of 0.577 ounces on a square inch. Our loo-ft. stack 
 therefore shows a draft of 3.48-f-5.i93, equals 0.67 inches of water or about 
 0.39 ounces of pressure per square inch. 
 
 In the above we have considered the gases in the stack as of the same 
 specific gravity as air. But this is not true. The chimney gases are a 
 mixture of carbonic acid gas nitrogen and gaseous steam, complete combus- 
 tion being assumed. 
 
 Carbonic acid gas has a specific gravity of 1.529; nitrogen of 0.971; 
 steam of 0.624 ; air being taken as the basis = i. 
 
 Hence in place of air at 500° F. weighing 0.413 lbs. per cubic foot, we 
 have a mixture of gases whose weight varies with the varying amounts of 
 
 -109— 
 
-?^'"^'AV-^ 4cvA^<.. -n..- 
 
 Brick Chimney at the Omaha & Grant Smelting and Refining Works, 
 
 DENVER, COLO. 
 Designed by Wm. M. Scanlan. 
 
each constituent. These differ with different coals, and therefore different 
 kinds of coal will cause differences in tlie draft of a given chimney, even 
 when the temperatures involved are the same. The following table gives 
 for five well known coals the number of pounds of air required per 100 lbs. 
 of coal burnt, weights of the resultant gases, the number of cubic feet oi 
 chimney gases at 500'* F. and the weight per cubic foot of the mixture, at 
 this temperature in the chimney. 
 
 Table No. 63. 
 
 KIND OF COAL. 
 
 Per Cent. 
 
 Per 100 Lbs. Coal. 
 
 -§ ■ 
 
 o o- 
 
 O So 
 
 o 
 
 " o 
 
 Anthracite (Pa.). 
 New River (Bit.) 
 Youghiogheny " 
 Mt. Olive 
 CoUinsville " 
 
 A 
 
 1.81 
 
 86.75 
 
 6.18 
 
 5.26 1279 
 
 1374 
 
 31440 
 
 NR 
 
 .... 
 
 77.00 
 
 18.00 
 
 5.00 1385 
 
 1480 
 
 34454 
 
 Y 
 
 2.00 
 
 59.00 
 
 33.00 
 
 6.00 1448 
 
 1542 
 
 36367 
 
 MO 
 
 6.80 
 
 46.00 
 
 37.00 
 
 10.20 1353 
 
 1443 
 
 34711 
 
 C 
 
 9.00 
 
 32.00 
 
 46.00 
 
 13.00 1345 
 
 1432 
 
 35052 
 
 0.0437 
 0.0429 
 0.0424 
 0.0416 
 0.0408 
 
 These different weights of the gases of combustion then cause differ- 
 ences in draft power of the same chimney, even when the temperatures 
 of the gases and of the outer air are the same in all cases. Table No, 
 64 is figured for certain average conditions of practice. The last line is 
 added to show the results as usually figured on the assumption that the 
 chimney gases have the same weight as air. 
 
 TABLE No. 64. 
 
 Draft Pressures Due to Different Coals, with Different Tem- 
 peratures of Air, but same Chimney Temperature. Chimney 
 100 Feet high above Grates. 
 
 Gases of Com- 
 bustion 
 from 
 
 Weight 
 
 1 Cubic Foot 
 
 at 500° fc\ 
 
 Weight 
 1 Cubic Foot 
 Air at 0" F. 
 
 Draft in 
 
 inches 
 
 of Water. 
 
 Weight 
 1 Cubic Foot 
 Air at 62°F. 
 
 Draft in 
 
 inches 
 
 of Water. 
 
 Weight 
 1 CubicFoot 
 Air at 102°F 
 
 Draft in 
 
 inches 
 
 of Water. 
 
 A 
 
 N.R 
 
 Y 
 
 M. O 
 
 C 
 
 Air 
 
 0.0437 
 0.0429 
 0.0424 
 0.0416 
 0.0408 
 0.0413 
 
 0.0864 
 
 0.0864 
 0.0864 
 0.0864 
 0.0864 
 0.0864 
 
 0.822 
 0.837 
 0.847 
 0.863 
 0.878 
 0.869 
 
 0.0761 
 
 0.0761 
 
 0.0761 
 
 0.0761 
 
 0.0761 
 i 
 0.0761 
 
 0.624 
 0.639 
 0.649 
 0.664 
 0.680 
 0.670 
 
 0.0707 
 
 0.0707 
 0.0707 
 0.0707 
 0.0707 
 0.0707 
 
 0.520 
 0.535 
 0.545 
 0.560 
 0.576 
 0.565 
 
 —111- 
 
The table further shows that difference in temperature of the outer air 
 may affect the draft of the chimney to the amount of 50 per cent and over. 
 In practice we find sometimes too little air, which shows inexcusably bad 
 design or management, sometimes (though rarely) just enough, and some- 
 times (see p. 15) amounts of surplus air varying from 10 per cent, to 100 
 per cent, hi the former case we have imperfect combustion which may mean 
 a waste of the entire volatile portion of the fuel, which by Table 63 may run 
 up to 20 per cent and more of actual loss. 
 
 In the other cases we have to draw into the furnace, heat and expel 
 through the chimney varying quantities of inert air, which again represent 
 various percentages of loss. The following table illustrates this : 
 
 Table No. 65. 
 Showing Weight and Volume of Chimney Gases from 100 lbs. 
 each of Various Coals at 500° F. on the Assumption of Various 
 Percentages of Surplus Air. 
 
 Ref 
 
 10% Surplus Air. 
 
 25% Surplus Air. 
 
 50% Surplus Aik. 
 
 100% Surplus Air. 
 
 Letter 
 
 ^^ Wt. per 
 "'*• Cnb. Ft. 
 
 Vol. 
 Cnb. 
 Ft. 
 
 Wt. 
 
 wt. per 
 Cob. Ft. 
 
 Vol. 
 
 Cnb. Wt. 
 Ft. 
 
 wt. per 
 Cub. Ft. 
 
 Vol. 
 
 Cub. 
 
 Ft. 
 
 Wt. 
 
 wt. per 
 Cub. Ft. 
 
 Vol. 
 Cub. 
 
 Ft. 
 
 A... 
 
 N.R. 
 
 Y... 
 
 M.O. 
 
 C... 
 
 1502 
 1619 
 1687 
 1578 
 1567 
 
 0.0435 
 0.0428 
 0.0420 
 0.0416 
 0.0409 
 
 34540 
 37814 
 40187 
 37981 
 38322 
 
 1694 
 1826 
 1904 
 1781 
 1768 
 
 0.0434 
 0.0427 
 0.0419 
 0.0415 
 0.0409 
 
 39190 
 
 42808 
 45447 
 42891 
 43182 
 
 2014 
 2172 
 2266 
 2119 
 2104 
 
 0.0429 
 
 0.0418 
 0.0418 
 0.0415 
 0-0410 
 
 46940 
 51154 
 54207 
 51071 
 51310 
 
 2653 
 
 2865 
 2990 
 2796 
 2777 
 
 0.0425 
 
 0.0416 
 0.0417 
 0.0414 
 0.0411 
 
 62440 
 67854 
 71747 
 67431 
 67570 
 
 If we take for example Youghiogheny coal, we see that with 100 per cent 
 surplus air the weight of the chimney gases has been reduced to 0.0417 lbs. 
 per cu. ft. We have, then with the air at 62° F., a draft pressure of 0.66 
 inches in place of the 0.649 inches of Table 64. That is a gain of 1^ per 
 cent in draft by admitting 100 per cent surplus air; but we have 96 per cent 
 more in volume of gases to push through the chimney. If we still assume 
 the temperature of chimney gases at 500° F,, this surplus air (at 0.2379 
 specific heat) requires 150592 H. U. to bring it from 62° to 500°. As this 
 Youghiogheny coal averages 12800 H. U. per lb., it would take all the heat 
 from 11.76 lbs. of coal to heat this surplus air, a loss of nearly 12 per cent in 
 the efficiency or economy. 
 
 If on the other hand we assume that the chimney temperature will be 
 reduced, and no fuel is wasted in heating this surplus air, this total possi- 
 ble reduction based on the same at 62° F., with the specific heat of air at 
 0.2379, that of the gases of combustion at 0.2495, and that of the mixture at 
 0.244, amounts to 207° F., entailing practically the same loss in heat, viz., 
 151100 H. U. But with the chimney temperature at only 293° F. we would 
 have only 0.023 difference in weight of inside and outside columns, or 0.44 
 inch draft, in place of 0.65 inch, a loss of over 32 per cent in chimney 
 efficiency or capacity. In other words this surplus air has reduced the 
 velocity of the gases in the chimney nearly one-third, while giving us 96 per 
 cent more gases to move. This shows forcibly that a low chimney temper- 
 
 —112— 
 
C —s^-<ic— 
 
 '!'-■ 
 
 Example of Iron Chimney. 
 Designed by J. P. Withrovv. 
 
ature may snow waste ot fuel; it shows economy only when attained with a 
 minimum of surplus air. 
 
 The velocity per second of the gases in the stack is given by the formula 
 V=lAgh in which "h" is the height of a column of the hot chimney gas 
 whose weight is equal to the difference in weight of the air outside and the 
 gas inside of the chimney. As we can express this head in inches of water 
 "p," we get the formula V=Cl/P in which the constant " C " varies ac- 
 cording to the composition of this gas. For the gaser. at 600° F. from the 
 various coals above considered, the formula becomes : 
 
 V = 87.2 VV for Anthracite Coal. 
 
 V = 87.92 VV for New River Coal. 
 
 V = 88.56 VV for Youghiogheny Coal. 
 
 V = 89.36 VV for Mt. Olive Coal. 
 
 V = 90.24 l/P for CoUinsville Coal. 
 
 For +he entrance velocity of the air under the grate, we have for 62° 
 F. the formula V=66.1 VV 
 
 These formulas give us velocities of 75 ft. p. second and over for the 
 quite ; usual draft pressure of 0.75 inch of water. But no such velocities 
 exist in boiler chimneys. The reason is that only a small part of that differ- 
 ence in pressure, which our draft gauge measures at the base of the stack is 
 or can be utilized for producing velocity. The greater part of it is required 
 to overcome the frictions of the grate with its bed of fuel, and that of the 
 boiler flues or tubes. The ignoring of this fact has led to the oft repeated 
 error that there is practically no gain in chimney capacity by an increase 
 in the temperature of the gases, because their increase in volume counter- 
 balances the increment in velocity. And thus the maximum capacity is 
 stated as reached when the gases have about double the volume of the 
 external air. On the other hand, an English authority, Mr. Thos. Box, 
 shows that with a flue 100 ft. long from furnace to base of chimney, the 
 maximum power or capacity is reached only when the gases in the stack 
 have about 3^ times the volume of the external air, i. e., when their temper- 
 ature has risen to nearly 1400° F. Neither of these views recognize that 
 the character of the fuel, the thickness of the bed upon the grate, the 
 methods of firing, and the proportions of the grate are really the determining 
 factors in this question. And while it is true that temperatures as high as 
 1100° F. have been observed in practice, they show very bad practice. 
 But even in much more moderate limits an increase of stack temperature 
 may materially increase the power or capacity of a given stack. 
 
 Careful experiments are sadly needed for determining what fractional 
 parts of the draft are expended in overcoming the various frictions men- 
 tioned. But from a large number of boiler tests we may safely figure out 
 that modern practice requires entering velocities of from 9 to 25 ft. per sec- 
 ond for the air, and escaping velocities of from 7 to 30 ft. for the chimney 
 gases; and with due allowance for chimney frictions, we have then a total 
 of from 0.03 to 0.22 inch of draft required for these. The frictions in fur- 
 nace and boiler are similarly found to run from 0.4 to 0.6 inch, making the 
 totals range from 0.43 to 0.82 inch. With these data in hand we can figure 
 
 —114— 
 
out the probable effect of high chimney temperature in increasing the actual 
 working power of a stack. 
 
 We will assume a plant with a chimney 100 ft. high, burning Youghio- 
 gheny coal at a pretty brisk rate, taking 50 per cent surplus air, and chim- 
 ney gases at 500° F. and air at G2° F. The stack at this rate is doing its 
 duty well, and the plant is fairly economical. A demand for one-third more 
 steam is made by those little additions to the machinery or increased direct 
 use of live steam, which in the popular belief "cost nothing when you once 
 have a good boiler." The boiler and the jircman have to get this steam so?ne 
 hoxv. The only recourse will be such changes in the method of firing as will 
 burn more coal per minute, and the only way to do it is by letting the gases 
 escape hotter and thus get the increased draft. By firing oftener and more 
 judiciously, the bed of fuel will not be much thickened and the friction here 
 will be increased probably only one-fourth, and in the flues hardly that 
 much. 
 
 Suppose the chimney gases to go to 900'' F. then the account will stand 
 about as follows : 
 
 Ordinary Work 
 
 Work. Ificreased. 
 
 In percent 100% 133^% 
 
 Stack temperature 500° 900° 
 
 Air 62° 62° 
 
 Available draft 0.649 inch. 0.889 inch. 
 
 Air entering at velocity of 10 ft. p. sec 13.3 ft. p. sec. 
 
 Gases escaping at velocity of 12 ft. p. sec. 23.0 ft. p. sec. 
 
 Draft required for entering velocity 0.0230 inch. 0.0400 inch. 
 
 Draft required for escaping velocity 0.0182 " 0.0676 " 
 
 Draft required to overcome furnace frictions-- 0.6000 " 0.7500 " 
 
 Total expended 0.6412 " 0.8576 " 
 
 Leaving balance available 0.0078 " 0.0314 " 
 
 Total pounds gas from 100 lbs. and 133 Ibs.coal with 50% 
 
 surplus air 2266 lbs. 3021 lbs. 
 
 Total volume at 500° and 900° 54207 cu. ft. 101376 cu. ft. 
 
 As these volumes bear to each other the same ratio as the velocities 
 12:23, the stack is now doing its work just as well as before. In fact the 
 balance of draft remaining could be used in increasing the velocity of exit 
 to nearly 28 ft., i. e., carrying off nearly 22 per cent more gas in volume, 
 equivalent to a further increase in capacity for coal burning of nearly 16 per 
 cent. Or practically we can increase the capacity or power of the stack by 
 nearly fifty per cent by increasing the temperature of the gases from 500° to 
 900° F. The cost of doing this is of course very great. 
 
 At 500° the chimney required for its total work of drawing in the air and 
 expelling the gases about 13 per cent of the fuel burnt ; at 900° it requires 
 25 per cent, a clear loss or waste of 12 per cent. 
 
 The same result can be attained without a pound of additional fuel by 
 raising the chimney 40 ft. 
 
 Table No. 66 illustrates this general question, but in applying it to any 
 existing problem, careful measurements should first be made of existing resist- 
 ances on the way from boiler front to base of chimney. 
 
 —115- 
 
TABLE NO. 66. 
 
 Showing Changes in Capacity of Chimney by Changes in 
 Temperature of Gases, With Height Constant ; or Changes in 
 Height with Temperature Constant. Air at 62° F. Weight of 
 Gases, the Average of the Five Coals Considered. 
 
 Temperature of escaping gases 
 with 100 ft. chimney 
 
 Per cent of total coal necessary to \ 
 establish draft - / 
 
 Draft obtained in inches of water- • • 
 
 Height of chimney for same draft, \ 
 at 500° F., in feet i 
 
 400° 
 
 500° 
 
 600° 
 
 700° 
 
 800° 
 
 10 
 
 13 
 
 16 
 
 19 
 
 22 
 
 0.56 
 
 0.65 
 
 0.73 
 
 0.79 
 
 0.85 
 
 86 
 
 100 
 
 112 
 
 121 
 
 131 
 
 900° 
 
 25 
 
 0.89 
 
 137 
 
 We append a further table showing the effect on velocities and areas of 
 chimneys from differences in quantities and mixtures of gases, and from the 
 varying values as boiler fuels of the five coals considered. While this is 
 figured on the basis of no surplus air, the ratios found will be but little 
 affected by such surplus. 
 
 Table No. 67. 
 
 Velocities in % of A 
 
 Quantities of gas in cub. ft 
 
 Areas should be, in % of A for equal 1 
 
 quantities of coal J 
 
 Comparative evaporative efficiency ) 
 
 in lbs water from and at 212° j 
 
 Pounds coal burnt to be equal in effect 1 
 
 to 100 pounds A / 
 
 Equivalent chimney areas % 
 
 Anthra- 
 cite. 
 
 New 
 Biver. 
 
 Yonghio- 
 gheny. 
 
 Mt. 
 Olive. 
 
 100 
 31440 
 
 101 
 34454 
 
 102 
 36367 
 
 103 
 34711 
 
 100 
 
 108.5 
 
 113.4 
 
 107.2 
 
 9 
 
 10.5 
 
 10 
 
 7.5 
 
 100 
 
 85.7 
 
 90 
 
 120 
 
 100 
 
 93 
 
 102 
 
 128 
 
 Collins - 
 ville. 
 
 104 
 35052 
 
 107.2 
 
 128.5 
 138 
 
 The above considerations show the practical difficulties in the way of 
 any general formulas for chimney height and area, and explain why the 
 " doctors disagree " in regard to them. If we had exhaustive and complete 
 tests on the amount of grate and fuel bed frictions under the severe condi- 
 tions of modern boiler practice, and with different kinds, qualities and condi- 
 tions of coal, probably all accepted formulas would, by substitution of new 
 constants, be brought into substantial accord. But constants based on grates 
 with 25 to 33 per cent air space, and on a consumption of 8 to 15 lbs. coal 
 per hour per square foot of grate will lead to erroneous results in modern 
 practice with 50 per cent air space and a consumption of 20 to 40 lbs. coal. 
 Therefore our results must be modified by careful judgment based on well 
 known local conditions. The best known formulas are Smith's, Kent's and 
 Gale's. They are as follows : 
 
 A = 
 
 Smith. 
 0.0825 F 
 
 l/h 
 r0.0825F\2 
 
 A = 
 
 Kent. 
 0.06 F 
 
 l/h 
 0.06 F\2 
 
 Gale, 
 A = 0.07 F^ 
 
 , /0.0825F\2 , /0.06F\2 , 180/ 
 
 F >2 
 
 A / " \ A ^ " t \gV 
 
 In which " A " ==■ area, " h " = height of stack in feet, " F " = pounds 
 
 116— 
 
Brick Chimney at the Power House of the Union Depot Ry. Co., 
 
 ST. LOUIS, MO. 
 
 Designed by E. D. Meier, M. E. 
 
coal burnt per hour, "t" = the stack temperarure,and "G " = grate area. 
 But in Kent's formula, "A" represents the effective area only, and he adds 
 a ring 2" wide all around to allow for chimney frictions. Thus if the formula 
 gives you a chimney of 41" diameter or of 36" square, you must make its 
 actual size 45" diam. or 40" square. For 100 ft. height, Kent's formula gives 
 a total area 11 per cent larger than Smith's for 250 lbs. coal per hour (50 H. 
 P.) ; exactly the same for 500 lbs. coal (100 H. P.) ; 18 per cent smaller for 
 1000 lbs. (200 H. P.) ; 24 per cent smaller for 5000 lbs. (1000 H. P.) etc. 
 The 5 lbs. coal per H. P. is merely a convenient assumption, and is based on 
 an evaporation of 7 lbs. water per lb. of coal. The areas will vary accord- 
 ing to the quality of coal, and such data on evaporation as local practice sup- 
 plies, as indicated by our Table No. 67. 
 
 Kent's formula has the advantage of recognizing the practical fact that 
 for larger powers the area of chimney required per horse power becomes 
 le^'s. 
 
 The general form of Gale's formulas is more promising. But as his con- 
 stants are based on observed data much smaller than those of best modera 
 practice, they lead to rather too large results. But his making the height 
 depend onh' on the stack temperature and the rate of combustion is 
 much more in accord with the facts than making height and area inter- 
 dependent as the other two formulas do. With Gale's constants modified so- 
 that h = — jr(7=^) "the heights can be fixed and then Kent's formula for 
 areas applied. The interdependence of height and area exists only in limits 
 defined by practical observation. Outside of these the assumption leads to 
 an absurdity. F. i. Kent's formula for area would give a 64" chimney 9 ft. 
 high as equivalent to a 35" chimney 100 ft. high. 
 
 Practical and local considerations generally fix the height required. The 
 chimney must be higher than surrounding buildings or hills, else whenever 
 the wind comes from the direction of the higher object, the draft will be 
 seriously impaired. Then the nature of the coal must be considered. 
 
 Mr. J. J. de Kinder, M. E., who has been engaged on a large number of 
 boiler and coal tests for the Pa. R. R. and other large consumers, using tele- 
 scopic stacks to meet this very question, gives 75 ft. as height for the most 
 free-burning bituminous coals, 115 ft. for slow-burning bituminous, and from. 
 125 to 150 ft. for anthracite coals. These latter being of three kinds, free- 
 burning such as Lykens Valley ; semi-free-burning such as Delaware and 
 Lackawanna ; and hard-burning such as Lehigh Valley ; they cannot be dis- 
 tinguished from each other by appearance. 
 
 DeKinder gives as necessary draft for anthracite 0.75 inch to 0.88 inch^ 
 and is in substantial agreement with Dr. Emery and Mr. Hague in this. He 
 gives 20 to 25 lbs. per hour as mimimum rates of combustion, 40 per cent air 
 space in grates for anthracite and 50 per cent for bituminous coals. 
 
 We give in Table No. 68 appropriate heights and areas of chimneys for 
 powers from 75 to 3100 horse-power ; based on an assumed evaporation of 7 
 lbs. water per lb. coal, equivalent to 5 lbs. coal per H. P. per hour. 
 
 For better or poorer coals any figures from this table can be readily 
 modified by referring to the tables in the earlier pages of this article. 
 
 If bituminous slack is to be used, the chimney should not be less than 
 
 —118— 
 
100 feet high, and not less than 125 feet high for anthraciie pea, or 150 feet 
 for anthracite buckwhecit. 
 
 Table No. gs. 
 
 
 a) to 
 
 55 
 
 HEIGHTS IN FEET. 
 
 
 Area 
 
 Square 
 
 Feet 
 
 75 
 
 80 
 
 85 
 
 90 
 
 95 
 
 100 
 
 110 
 
 120 
 
 130 
 
 140 
 
 150 
 
 175 
 
 200 
 
 
 COxMMEUCIAL HORSE POWEU. 
 
 3.14 
 
 24 
 26 
 28 
 30 
 32 
 3t 
 36 
 40 
 44 
 48 
 54 
 60 
 66 
 72 
 84 
 96 
 108 
 120 
 
 75 
 90 
 
 78 
 
 92 
 
 106 
 
 122 
 
 81 
 95 
 110 
 127 
 144 
 162 
 
 
 
 
 
 
 
 
 
 
 
 3.69 
 
 98 
 114 
 130 
 149 
 168 
 188 
 
 
 
 
 
 
 
 
 
 
 4.28 
 
 117 
 133 
 152 
 171 
 192 
 237 
 287 
 
 120 
 137 
 156 
 176 
 198 
 244 
 296 
 352 
 445 
 
 
 
 
 
 
 
 
 4.91 
 
 
 
 
 
 
 
 
 6.59 
 
 164 
 185 
 
 208 
 257 
 310 
 370 
 468 
 577 
 697 
 
 
 
 
 
 
 
 6.31 
 
 
 
 
 
 
 
 
 
 7.07 
 
 
 
 215 
 267 
 322 
 384 
 484 
 600 
 725 
 862 
 1173 
 
 
 
 
 
 
 8.73 
 
 279 
 
 337 
 
 400 
 
 507 
 
 627 
 
 758 
 
 902 
 
 1229 
 
 1584 
 
 2058 
 
 
 
 
 
 10.56 
 
 
 
 
 
 
 
 
 
 12.57 
 
 
 
 
 
 413 
 
 526 
 
 650 
 
 784 
 
 932 
 
 1270 
 
 1660 
 
 2102 
 
 2596 
 
 
 
 
 15.90 
 
 
 
 
 
 
 
 19.63 
 
 
 
 
 
 
 672 
 815 
 969 
 1319 
 1725 
 2181 
 2693 
 
 
 
 23.76 
 
 
 
 
 
 
 
 
 
 28.27 
 
 
 
 
 
 
 
 1044 
 1422 
 1859 
 2352 
 
 9904 
 
 
 38.48 
 
 
 
 
 
 
 
 
 
 50.27 
 
 
 
 
 
 
 
 
 1983 
 
 63.62 
 
 
 
 
 
 
 
 
 
 2511 
 
 78.54 
 
 
 
 
 
 
 
 
 
 3100 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Whenever it becomes necessary to have long flues leading to a chimney, 
 the power of the latter becomes more or less impaired. We adapt the fol- 
 lowing table from Mr. Thos. Box ; the ioial length of flue from grate to 
 base of chimney must be considered. 
 
 Table No. 69, 
 Reduction of Chimney Draft by Long Flues. 
 
 Total length of flues in feet. 
 Chimney draft in percent • • • 
 
 50 
 100 
 
 100 
 93 
 
 200 
 79 
 
 400 
 66 
 
 600 
 58 
 
 800 
 52 
 
 1000 
 48 
 
 2000 
 35 
 
 A further loss in draft results from any downward course of the gases in 
 the flue. It may be roughly accounted for by using double the length of 
 such down turn in making up the total flue lengths for the above table. 
 
 Where several boilers lead into one chimney, a further factor comes in 
 to reduce the required area. The heaviest work for the chimney is just 
 after firing, since the friction through the fresh coal is greater and the tem- 
 perature less than some minutes later. But it would be very bad practice to 
 fire all boilers or all doors simultaneously. Hence the second and succeeding 
 boilers do not require as much area as the first. It will be safe to figure 75 
 per cent for the second and 50 per cent each for the third, fourth, etc. But 
 it is advisable to increase the height slightly for each boiler added. 
 
 E. D. M. 
 
 -119— 
 
CONCENTRATION AND DISTRIBUTION OF POWER. 
 
 From the time that man first began to call the forces of nature 
 to aid him in his handicraft, there has been a gradual increase in 
 the size of power plants. At each stage of progress it became 
 plainer that />ower, repairs and labor could be saved by larger wind 
 or water wheels, turbines, and finally steam engines. The best 
 engineer or millwright costs less than two of somewhat less ability, 
 duplicate parts for one machine serve for prompt repairs as well 
 for one out of twenty as for one out of three, a 500-horse power 
 engine costs less than two of 250-horse power, etc., etc. 
 
 But there were other causes which imposed limits which it was 
 disastrous to pass. The laborers grew in number in some ratio with 
 the increase in power; they must live near the works. Often the 
 best place for the power plant was the worst place for them. The 
 conversion from heat energy to mechanical force frequently de- 
 mands a site at low water level difficult of access or unhealthy for 
 the laborers. Shafting and even wire cables have short distance 
 limits for the economical transmission of power. 
 
 But with the development of electrical pozuer, which com- 
 menced in the last decade, and is advancing now in almost geo- 
 metrical ratio, very large steam plants have multiplied, It becomes 
 possible to develop an immejise amount of power in one place, 
 since with but one more conversion — from mechanical into elec- 
 trical energy — we can send it, divided into just such quantities as 
 
 —121— 
 
fit each time and place, to points many miles apart, with losses 
 exactly controllable. Locations can therefore be chosen where 
 fuel and water are cheapest, where the refuse is easiest disposed 
 of, etc., and where every item ot economy, multiplied by the enor- 
 mous quantities involved, becomes a question of grave concern 
 and careful calculation. In these large and essentially modern 
 power plants will be found, as peer of the best type of the com- 
 pound condensing or triple expansion engine, the Modern Water 
 Tube Boiler. When in a plant like these, the old fire tube type 
 of boiler is found, it is but an exception which proves the rule. As 
 an apt illustration of this development we may compare the Cen- 
 tennial Exposition at Philadelphia in 1876 where a single 1000- 
 horse power engine sufficed to drive all the machinery, and where 
 fire tube boilers were the rule and water tube the exception, with 
 the great Columbian Worlds Fair of 1893 at Chicago, where an 
 installation of i^,ooo-horse power boilers becomes necessary, from 
 which condensing engines of the compound and triple expansion 
 type will develop about 25,000-horse power, two-thirds of which 
 will be converted into electrical energy.* All these boilers are of 
 the Modern Water Tube type, space, safety, economy and cesthetic 
 considerations having barred the others. 
 
 The detailed and painstaking investigation into all the points 
 involved in steam making, which in such large plants precedes 
 and influences the design, and the choice and size of the parts, is 
 of course not possible in small plants, whose owners must neces- 
 sarily follow on the lines marked out by these large and successful 
 installations. But they will the more readily profit by such expe- 
 rience when prepared to analyze the different elements which 
 together compose a modern boiler plant. As a guide to such 
 analysis we offer in the following pages a few elementary thoughts 
 on the salient points involved. 
 
 *By general consent a horse power in a boiler is considered as the evaporation into 
 steam, at seventy pounds gage pressure, of thirty pounds of water per hour, as being about 
 the quantity a good slide valve engine requires. A good single cylinder Corliss engine uses 
 only twenty-five pounds, a compound condensing eighteen to twenty pounds, and a triple 
 expansion thirteen to sixteen pounds. This explains the apparent discrepancy betweeu 
 boiler and engine power. 
 
 ]^22 
 
A MODERN BOILER PLANT. 
 
 A good boiler plant is something essentially modern. Since Watt yoked 
 the Power, and Stephenson harnessed the Speed of Steam to the triumphal car 
 of modern progress, invention has been busy, throughout the civilized 
 world, with improvements in all the elements of a complete steam plant. 
 
 But owing partly to the fact that the engine seemed to offer more 
 chances for experiment, and better opportunity for observation, and partly 
 to the knowledge that the losses in the engine were vastly greater than in 
 even a carelessly designed boiler plant, the engine has received by far 
 greater attention. Even now it is not an unusual thing to find a steam 
 plant in which every rejineme?it of modern engineering has been carefully 
 brought to bear in the design and construction of engine and shafting, while 
 the boiler plant has been settled by prescribing the number of square feet 
 of heating surface, and adding a few commonplace specifications about the 
 steel, which can be as well filled b}' a high sulphur steel as by good flange 
 stock. Many an intelligent manufacturer will point with pride to his pol- 
 ished Corliss engine, will show you model indicator cards from it, while 
 neither he nor his engineer can tell you within 25 per cent what his boilers 
 are doing. 
 
 It is not uncommon to find the boilers stowed away in some hole, so 
 close, dark and ill-ventilated that no self-respecting skilled laborer will con- 
 tinue to work in it, and a good fireman is emphatically a skilled workman, 
 having charge of an important chemical process whose proper handling, in 
 many lines of manufacture, determines whether the books will show loss or 
 profit at the end of the year. 
 
 Naturally enough, ill-designed, badly proportioned breechings or flues 
 are often found in such places, connecting into chimneys neither wide 
 enough nor high enough for the work expected of them. But within the 
 last decade more attention has been given to the boiler pla?it. Much educa- 
 tional work has been done by boiler companies, notably by one which 
 annually publishes in its catalogue much useful information and many con- 
 venient tables of data connected with steam generation, which are not else- 
 where readily available to the average steam user or his engineer. Much 
 credit is due to the large electrical companies who have boldly departed 
 from antique superstitions, and have put as much thought into their boiler 
 plants as into the other elements of their large installations. 
 
 A boiler plant consists in the main of three essential parts, each one of 
 which has its own important office in the success of the whole. 
 
 First, there is the Chimney or Stack with its Flue or Breeching, to carry 
 off the waste gases and to create the Draft, without which combustion in a 
 practical and economic sense is impossible. 
 
 Second, the Furnace or Setting, whose arrangement and dimensions de- 
 termine the important elements of quantity and economy of combustion. 
 
 Third, the Boiler, whose proportions and design must be such as enable 
 it to absorb the maximum amount of the heat produced by the furnace, 
 thus determining finally the capacity and economy of the whole plant. 
 These separate and distinct offices of ,the three component parts of a boiler 
 plant are often confounded, not only by those to whom a boiler-room is sim- 
 
 —124— 
 
ply a vague counterpart of the Black Hole of Calcutta, but even by those 
 who claim to "know all about boilers." How often is the boiler manufac- 
 turer met by the question: "Will your boiler burn slack?" or "tanbark" or 
 some other fuel desirable because cheap. Aside from the fact that the 
 boiler has usually very little to do with it, the question can only be answered 
 by exercising the Yankee privilege of asking a few more. F. i. "How 
 much draft have you?" or "What are the dimensions of your chimney?" 
 the answer will generally be "a splendid draft," or "we have a fine big 
 chimney built only a few years ago." But this gives the boiler man but a 
 very vague idea. He wants facts ■a.nd he does not get them. The splendid 
 draft may prove to be, according to the personal equation of his informant, 
 anything from four-tenths of an inch to an inch of pressure, the chimney 
 may be anything from half to full capacity for the work in hand, and yet 
 upon an accurate knowledge of these data the correct answer to the first 
 question depends. 
 
 THE CHIMNEY. 
 
 The Chimney determines how many pounds of fuel can be burnt per 
 hour, the quantity varying with the kind of fuel in very narrow limits, and 
 also to some extent depending on atmospheric conditions. Its office is to 
 remove the waste gases whose quantity varies but little whether smoke 
 accompanies combustion or not, and to supply enough air to oxydize all 
 the fuel. The Di-aft pressure is simply the difference in weight between a 
 column of hot and therefore light gas in the chimney, and a column of air 
 outside, of the same height and area. The greater the draft pressure, the 
 greater the speed of the spent gas leaving and the fresh air entering the 
 furnace, and hence the greater the quantity of fuel v^hich. the same chimney 
 area will enable us to burn. 
 
 This pressure, as explained, depends on the height and temperature of 
 the column of waste gas; it may be increased at will either by making the 
 chimney higher or allowing the spent gas to escape at a higher tempera- 
 ture. The latter method is very wasteful and should never be resorted to 
 except where the former cannot, for some local reasons, be adopted. Of 
 course, with larger chimney area less speed will suffice for the same quan- 
 tities of gas and air, and this fact is often urged to bolster up the antique 
 superstition that a low chimney with ample area will do the same work as a 
 tall one of less diameter. If this were true, removing the roof of the boiler 
 house ought to prove a good substitute for an expensive chimney, and a 
 gas globe might conveniently replace the broken chimney of a student lamp. 
 
 It is just here that the nature of the fuel affects the matter. To cause 
 combustion the air must be brought into intimate contact with all the particles 
 of the fuel. With gas or oil this may be done with small initial draft. 
 The frictional resistafice to the passage of the air through a bed of solid fuel 
 of any kind increases with the decrease in the size of the pieces, lumps or 
 grain of the fuel. Hence a sharper draft is required for sawdust or tanbark 
 than for cordwood, for slack or pea coal than for nut or e^^g coal. But the 
 smaller the grain of the fuel the more surface is presented for the oxydizing 
 action of the air, hence the more uniform the combustion. Therefore the 
 careful fireman breaks his lump coal just before firing. 
 
 Again most coals have two rates of combustion which give best economic 
 results. One usually a very low one and hence hardly available in the very 
 limited space generally fixed by modern conditions. The other is a much 
 
 — 125— 
 
higher one, the intermediate rates being frequently very wasteful. This 
 higher rate makes more power possible in the minimum of floor area and hence 
 meets modern demands. It developes higher temperatures, and, as great 
 differences in heat favor its transmission, it makes more work possible in 
 the boiler. 
 
 Finally a strong draft in the chimney is less liable to interruptio7i by gusts 
 of wind than a sluggish one. All these considerations point to the tall 
 chimney as the source and fountain of all the energies of a modern steam 
 plant. 
 
 The smoke stacks of the Pacific Mills, Lawrence; the Boston Edison 
 Co.; the Narragansett Electric Light Co., Providence; Broadway Cable R. 
 R. New York; Clark Thread Mills, Newark; Union Depot R. R.. St. Louis; 
 Chicago Edison Co., and Anheuser-Busch Brewery, St. Louis, are good ex- 
 amples of modern practice in the matter of tall chimneys. 
 
 The forty to sixty feet smoke stacks which were "plenty high enough" 
 belo7ig to the past, with the old stone mills, the ram shackle engines with the 
 gothic ornaments, low steam and timber bed frames. 
 
 The Flue or Breeching connecting the furnace or setting to the chimney 
 properly forms part of it. It should be of equal or slightly larger area and 
 where changes in shape or direction cannot be avoided they must be made 
 easy and gradual, carefully preserving the area at all points. Abrupt turns 
 or contractions of area are known to interfere with the flow of liquids; fre- 
 quent and facile observation shows this to every one, and tables are pub- 
 lished showing the observed loss in effect by those of most common occur- 
 rence. In the case of gases the effect is even more damaging, since the 
 initial force is generally (in a chimney always) limited, while opportunities 
 for observing this action are not frequent and have to be specially created. 
 Therefore so many sharp turns and sudden changes in area are met with 
 in steam pipes and smoke flues, which, a little thought would prove, should 
 be avoided. Where one chimney serves several boilers, the branch of the 
 breeching or flue for each must be somewhat larger than its proportionate 
 part of the area of the main flue. 
 
 i^^r(r<?^^;'i?// is sometimes employed with good success. It should be 
 an adjunct merely, but cannot be made to replace a tall chimney. Com- 
 bustion will not be as perfect under pressure as under a slight vacuum. A 
 leakage of air inward through the furnace walls helps to supply hot air for 
 combustion, and to some extent reduces and counteracts losses by radia- 
 tion. But excessive forced blast which more than counterbalances the 
 draft of the chimney will increase radiation and by leakage through the 
 walls, doors, etc., outwards cause much loss. Worst of all it interferes 
 with the firema7i by making his work hard and unsatisfactory. ' 
 
 THE FURNACE. 
 
 The chimney having fixed the quantity of fuel we can burn, we must 
 arrange our furnace so that it will do the best work within this limit. We 
 must remember that the draft must be husbanded, its whole force to be called 
 on only for our maximum effort. The kind of fuel and the nature of the 
 service will determine \h& proportions of our furnace. The furnace which 
 will give excellent results on coal will be found inadequate for wood, if it 
 be proportioned for the steady and regular work of a flour mill, it must be 
 modified to meet the sudden and varying demands of an electric railway. 
 The grate must, in area, in width and shape of air spaces, in length and 
 
 —126— 
 
design of bars be adjusted to the kind of work the plant is to do, and the 
 peculiarities of the fuel. Thus a baking and clinkering coal requires few 
 and wide air spaces, a dry and friable one must have many and narrow 
 ones. The total air space of the grate must be made as large as possible 
 since it is the active ele?ne>it; the metal must be reduced in width as much 
 as is compatible with strength. The surface of the grate must be as smooth 
 and even as possible so as to offer no impediment to the use of the clinker 
 bar and other fire tools. The longer time required for the perfect combus- 
 tion of a fuel the larger must furnace, combustion chamber and flue be 
 arranged. For sufficient air, high temperature, and time and space are 
 equally important conditions of thorough combustion, and this must be 
 completed before the gases are brought in contact with the heating (or 
 here cooling) surfaces of the boiler. These rules apply to the various patent 
 grates, stokers and furnaces as well as to the standard devices of established 
 practice. And the best invention must in its application be supplemented 
 by experience, calculation and design. The walls of a good furnace should 
 have B.sfew openings, doors, etc., as possible, since every break in the bond 
 of the brickwork increases the tendency to cracks, which can never be en- 
 tirely avoided, but which cause leaks so detrimental to complete economy. 
 Double walls with air spaces between them should always be employed 
 where practicable, so that this unavoidable indraft through the cracks may 
 be heated and utilized for secondary com.bustion. 
 
 The lining of the furnace proper and the bridge wall should be made of 
 a quality of fire brick which combines great refractory power with hardness 
 and toughness to resist the abrasion due to the fire tools and the clinkers. 
 The combustion chamber and flues may be lined with a cheaper grade since 
 the heat is less and no abrasion possible. The cheap plan of using no fire 
 brick abaft the bridge wall is wasteful in the end and therefore bad prac- 
 tice. As no bond of either fireclay or mortar is absolutely reliable under fur- 
 nace temperature, long and stout anchor rods should be used to tie the 
 walls securely together. It is of course necessary to make the joints be- 
 tween the furnace and the boiler as nearly air-tight as possible. This is best 
 done by leaving joints wide enough to clear all projecting parts of the boiler, 
 such as rivet heads, etc., and then filling them with some spongy material, 
 f. i., tow or waste thoroughly saturated with fireclay. This is pliable 
 enough to follow the movements caused by alternate expansion and contrac- 
 tion without racking the brickwork or impairing the joints. By this arrange- 
 ment the boiler can be made entirely independent of the stability of the walls. 
 For all clinkering coals a cemented ashpit kept full of water is advisable. 
 
 Having now designed a furnace, capable of burning our fuel to best 
 advantage, little and slowly when the demand for power is slight, much and 
 fiercely when the full load is put on, i. e., having devised the best means 
 for waking the sleeping force in the fuel to the active energy of living Heat, 
 we want means to translate this into Mechanical Power. 
 
 THE BOILER. 
 
 The Steam Boiler furnishes the means. If we except certain dangerous 
 vapors, steani, which is the gaseous form of water, is the substance whose 
 expansive force grows most rapidly with each increment of heat. It has 
 therefore become to civilized man the almost universal means of drawing 
 active working force from the latent Sun-Energy stored up for him for ages 
 
 —127— 
 
past by provident Nature. In the f/t.-yiac-c the energy of lie at has been called 
 to life; the boiler is now to absorb this heat and to transmit it to the water 
 within. This will first rise in temperature with less than five per cent ex- 
 pansion, until a point is reached when each additional unit of heat absorbeQ 
 changes a particle of water into the vapor we call steam. This change 
 is accompanied by an immense increase in volume, and as the boiler im- 
 prisons the steam and exactly limits the space it may occupy, each new 
 particle thus changed crowds on those gone before and the imperative ten- 
 dency to occupy more space begets the expansive force or pressure oi 
 steam which our gage registers. To hold this pressure with safety, is the 
 iecond office oiihehoWex. If there be just room in the boiler above the 
 water line, to contain one pound of water converted into steam at atmos- 
 pheric pressure, the second pound thus converted crowds the first into hai) 
 this space, appropriates the other half itself and thereby adds fully fifteen 
 pounds per square inch to the originally existing pressure, and so on with 
 each succeeding pound of water which the heat absorbed changes into 
 steam. At the same time each pound of water previously converted into 
 steam must absorb a certain quantity of heat to enable it to retain its gas- 
 eous form under this increased pressure, or some portion of it will 
 fall back as waterj^ spray. Every one who has seen a teakettle boil knows 
 that the steam rises in transparent bubbles, which burst as they reach the 
 surface, scattering spray to all sides but mainly upwards. The spray, be- 
 ing water, has no expansive force, and when allowed to leave the boiler 
 with the steam not only represents so much inert matter carried along but 
 presents innumerable surfaces to invite and hasten condensation. The 
 third office of a good boiler is therefore the separation of this entrained 
 water from the steam. This is an important office and worthy of the ser- 
 ious thought of the designer; yet it is often neglected in superstitious 
 reliance on the fetich of an excessive amount of heating surface. 
 
 The water with which boilers are fed is rarely even approximately pure. 
 Salts of lime and magnesia are the most frequent impurities chemically com- 
 bined, while much extraneous matter both vegetable and mineral is carried 
 along mechanically. The latter as well as the carbonates are readily /r^«}>- 
 //<2/^^ at the boiling point at atmospheric pressure. But the sulphates oj 
 lime and magnesia require a temperature of nearly 300*^ Fahrenheit to be- 
 come insoluble and drop to the bottom; this is about the boiling point for 
 water under fifty-two pounds gage pressure. While therefore the common 
 exhaust feed water heater and the old time mud drum will, if properly pro- 
 portioned to the work remove the mud and the carbonates, they will have 
 Tjo effect whatever on the sulphates. For it is matter of common exper- 
 ience that you can almost hold your hand on the mud drum of a battery of 
 boilers while they are under 100 pounds of steam, especially where the old 
 method of feeding through the mud drum is adhered to, and an exhaust 
 feed heater cannot yield more than 212° Fahrenheit temperature. "Th.^ sul- 
 phates make the hardest scale when allowed to bake on the heating surfaces. 
 Their removal is therefore even more necessary than that of the mud or the 
 carbonates. If a mud drum or other vessel is made part of the boiler for 
 this purpose it must be placed where it will no.z&ss'axWy partake of on approx- 
 imate the steam temperature.. The best modern practice removes all these im- 
 ■turities by live steam purifiers, by chemical precipitation, or by filtration. 
 
 —129— 
 
after coagulation, before feeding the water to the boilers. But this best 
 practice is not as yet the general rule, and these means may sometimes 
 prove inadequate. Therefore a good boiler should be able to dispense with 
 them, or, when supplied, to supplement their work. 
 
 The fourth office of the boiler is then to remove all impurities from the 
 water which may have escaped other cleaning agencies, and to deposit them 
 at points where they do the least harm and can be readily removed. No 
 means are so efficient for this purpose as positive and unchecked circulation 
 through all parts of the boiler, to keep the heating surfaces swept clean; 
 and the vessel to catch the impurities must be open to the main current. 
 If it can be arranged so as to precipitate most of the foreign matter out of 
 the water before it enters into the main circulation the result will be still better. 
 
 The first office of the boiler, the absorption of the furnace heat and its 
 transmission to the water requires thin a?id homegeneous metal for the heat- 
 ng surfaces and a strong and positive circulation of the water. It is well 
 -.cnown that a tube or flue has much greater strength against internal than 
 against external pressure. It is much easier to produce and maintain cir- 
 culation through a tube than round about it. Finally it is much easier to 
 clean the inside of tubes thoroughly,than the outside when they are grouped 
 close together in a boiler. An iron tube of standard gage will stand 
 2,500 pounds to the square inch of internal pressure before rupture, and the 
 rupture in the vast majority of cases is small and local. The same tube 
 would collapse under external pressure much earlier, and once begun the 
 collapse would be practically total. 
 
 Mr. Thomas Craddock of England, found by experiment that a velocity 
 of water two miles per hour over tube heating surface doubled its efficiency in 
 heat absorption, and that this circulation became more important the less 
 the difference in temperature between the heat giving and the heat receiv- 
 ing body. Therefore in the ultimate economy of a boiler, to realize all the 
 heat possible from the escaping temperature of the gases, circulation is all 
 important. The water tube then best fulfills the first, second and fourth of- 
 fices above explained, and must therefore become a fundamental element of 
 the Modern Boiler. It is evident that for the third office, the separation 
 of the entrained water from the steam, another element must be added to 
 the water tubes. With few exceptions water tube boilers are supplied with 
 a large drum or several drums or shells for this purpose. Observation of 
 the boiling of water in an open vessel shows that the spray will, as the 
 steam bubbles burst, fly upwards a number of inches. There is reason to 
 believe that in a closed vessel under pressure it will not fly quite so far, 
 certainly not further. Steam at 100 pounds gage pressure is about seven 
 times as heavy as at atmospheric pressure, and hence occupies only one- 
 seventh of the space. The same weight of zvater evaporated per second un- 
 der the higher pressure, will rise to the surface in much smaller bubbles, or 
 in a smaller number, or most probably both. The speed with which the 
 steam rises through the v/ater depends on the difference between the weight 
 of the steam and that of the water. At atmospheric pressure the water 
 weighs 1,570 times as much, at 100 pounds gage pressure 213 times as 
 much as the steam. For these two reasons then the speed and energy with 
 which the high pressure steam rises will be much less than that observed at 
 atmospheric pressure. Under normal conditions therefore there is less dan- 
 ger of primitig or wet steam at high pressures than at lower ones. But if by 
 
 —130— 
 
accident or design a large valve be suddenly opened much entrainment fol- 
 lows. This is because the sudden lowering of the pressure in the boiler 
 temporarily increases the rate of evaporation enormously. This accounts 
 for the geyser like action of certain boilers, mainly of a vertical type, which 
 just previously have been working "like a charm," as soon as a sudden de- 
 mand causes the engine valve to reach out for full stroke steam. From 
 the above explanations it is evident that a reasonable height of steam space 
 and a large surface at the water line will prevent priming under ordinary 
 conditions, and some form of dry pipe placed well above the water line will 
 take care of moderate fluctuations. If we can further so direct the circula- 
 tion that the film of each bursting bubble is thrown in a direction contrary 
 to the steani delivery, we will have a living active force to counteract any 
 rush of spray towards the steam nozzle. As these arrangements can most 
 readily be made in a water tube boiler, this then best fulfills the third office 
 of a good modern boiler, the separation of the entrained zuater from the 
 steam. 
 
 Compare for a moment the favorite type of fire tube boiler, the horizon- 
 tal multitubular. Following the demands for a large heating surface, the 
 tubes are crowded in close together and above the center of the shell, leav- 
 ing only ohout one-ffth of its area diSstedim space, whose height is about one- 
 fourth of the diameter. A recent report(A. B. M. A. 1892) shows that this ten- 
 dency has gone so far that 30 per cent more tubes are put into boilers than 
 the best rules for tube-spacing (A. B. M. A. 1889) warrant. This means 
 that the steam space and the steam liberating sutface have been much en- 
 croached on. Not only is the water line brought up too near the steam 
 Bozzl-e, but the channel for the rising steam bubbles is so curtailed and cut 
 up that they create great commotion at the water line, and increase the ten- 
 dency to prime. The upper surface of the water is generally accepted as the 
 steam liberating surface. If all the steam were made on the surface of the 
 upper row of tubes this would be correct. But all that is made on the bot- 
 tom and sides of the shell, and on all the tubes below the top row has to 
 pass the narrow spaces between the tubes of the upper rows. These are fre- 
 quently but little over an inch wide, and have to serve for the return circu- 
 lation of the water as well as the upward rush of steam mingled with water. 
 Mr. Geo. H. Babcock, M. E.,in a very instructive lecture on the circulation 
 of water delivered at Cornell in 1890, suggests an ingenious method of ap- 
 proximately finding the speed of such rising currents. In a 60-inch boiler 
 it would probably not be far from fourteen feet per second or say about ten 
 miles an hour. Water rushing at ten miles an hour through a narrow slit 
 will do a good deal of sputtering, and when it is half steam it will be practi- 
 cally all spray. The four or five inch body of water over the top row of tubes 
 has a slight retarding influence but the real liberatifig surface for the steam 
 is nevertheless the aggregate of the narrow spaces between the upper tubes. 
 "Where there is any scale or mud present in the water, its location and ap- 
 pearance after a fortnight's run shows that the bulk of the upward circula- 
 tion in a horizontal tubular boiler is confined to a short section near the 
 bridge wall, its speed decreasing towards front and rear till it meets the 
 downward currents which are strongest near the ends of the boiler. This 
 further concentrates the steam delivery on a small portion of the liberating 
 surface. For this reason this whole type of fire tube boilers gives wet 
 steam when forced. This has lead to insistence or, more heating surface, 
 
 —131— 
 
and this again when supplied without due increase in the other important 
 ratios of tube spacing, Hberating surface and steam room, serves, as we have 
 seen, to increase the evils it is intended to remedy. It must of course 'be con- 
 ceded that in the boilers of the water tube type with either tubes or drums 
 placed vertically or nearl}^ so, the tendency to prime is even greater than in 
 the horizontal fire tube types. But in the types which have stood the test of 
 years the tubes and shells or drums are horizontal or slightly incli?ied, fully 
 half the shell is steatn space, the vertical distance from water line to steam noz- 
 zle is half the diameter or more, the upward current of circulation is deflected 
 away from the steam opening, and the liberating surface is the largesv hori- 
 zontal section oi the shell, entirely free from tubes or other obstructions. 
 Well designed boilers of this class have been forced to nearly double their 
 rated capacity without approaching the amount of entrainment considered 
 permissible in the horizontal tubular type at conservative rating. 
 
 As these advantages are obtained with shells or drums of about half the 
 diameter of fire tube boilers of the same evaporative capacity, greater safety 
 at high pressures is the result. For the thinner metal has more strength per 
 sq. in., and uniformity than thicker plate of the same quality. • The rivet 
 seams admit of more favorable proportions. Thin sheets can be better fitted 
 than thick ones, etc. Thin metal transmits heat more rapidly than 
 thick, and hence suffers less deterioration, and finally the nest of tubes 
 in a water tube boiler protects the shell from the direct and fiercest 
 heat, thus ensuring greater durabilit}^, and removing all danger of any 
 chemical action of the hot carbon or sulphur on the steel boiler plates. 
 The free circulation in a water tube boiler tends to equalize the tempera- 
 tures all over the structure, thus prevetiting those dangerous strains due to 
 unequal expansion. The old saw of "ice at the bottom, water in the mid- 
 dle, and steam on top" is but a slight exaggeration of what often occurs in 
 a fire tube boiler, and many a "mysterious" explosion may be due to such 
 a cause. These are some of the points of superiority of the boiler proper. 
 In relation to furnace and chimney there are several more. 
 
 In a firetube boiler the aggregate tube area limits the capacity of the 
 furnace, and checks the work of the clmmiey. The cogent reasons against 
 increasing it have been pointed out above. In a water tube boiler the flue 
 areas can be freely proportioned to furnace and chimney and can even be 
 adjusted to suit local conditions after the boiler is built and set, without dis- 
 arranging any important ratios. 
 
 It is well known that ashes and soot soon ctit down both heating surface 
 and flue area in fire tube boilers, and that flame entering a tube is soon ex- 
 tinguished; careful experiments have shown "that the quantities of water 
 evaporated by consecutive equal lengths of flue-tubes decrease in geometrical 
 progression.^'' (D. K. Clark.) 
 
 In water tube boilers the ashes and soot find much less chance for lodg- 
 ment, all the heating surfaces are constantly accessible, during service, for 
 inspection and cleaning; the flame is constantly regenerated since in impinging 
 against successive water tubes effete combinations are broken up and new 
 ones formed; ocular demonstration of these facts is daily possible. 
 
 Finally, it is possible to concentrate more power in a single water tube 
 boiler than in any of the fire tube types. Therefore considerations of 
 safety, durability, economy, space and accessibility point to the Water Tube 
 Boiler as naturally the basis of a modern boiler plant. 
 
 —132- 
 
y 
 
 2. 
 5' 
 
 n> 
 
 DO 
 
 o 
 
DESCRIPTION OF THE HEINE SAFETY BOILER. 
 
 The boiler is composed of the best lap welded wrought iron tubes, ex- 
 tending between and connecting the inside faces of two "water legs" which 
 form the end connections between these tubes and a combined steam and 
 water drum or "shell," placed above and parallel with them. (Boilers over 
 200-horse power have two such shells.) These end chambers are of approx- 
 imately rectangular shape, drawn in at top to fit the curvature of the shells. 
 Each is composed of a head plate and a tube sheet, flanged all around and 
 joined at bottom and sides by a butt strap of same material, strongly riv- 
 eted to both. The water legs are further stayed by holloiv stay bolts of hy- 
 draulic tubing, of large diameter, so placed that two stays support each tube 
 and hand hole and are subjected to only very slight strain. Being made 
 of heavy metal they form the strongest parts of the boiler and its natural 
 supports. The water legs are joined to the shell by flanged and riveted 
 joints and the drum is cut away at these two points to make connection 
 with inside of water leg, the opening thus made being strengthened by 
 bridges and special stays, so as to preserve the original strength. 
 
 The shells are cylinders with heads dished to form parts of a true sphere. 
 The sphere is every where as strong as the circle seam of the cylinder which 
 is well known to be twice as strong as its side seam. Therefore these 
 heads require no stays. Both the cylinder and its spherical heads are 
 therefore yrd"!? to follow their natural lines of expa?ision when put under pres- 
 sure. Where flat heads have to be braced to the sides of the shell, both 
 suffer local distortions where the feet of the braces are riveted to them, mak- 
 ing the calculations of their strength fallacious. This we avoid entirely 
 by the dished heads. To the bottom of the front head a flange is riveted in- 
 to which the feed pipe is screwed. This pipe is shown in the cut with an- 
 gle valve and check valve attached. 
 
 On top of shell near the. front end is riveted a steam nozzle or saddle, to 
 which is bolted a Tee. This Tee carries the steam valve on its branch, 
 which is made to look either to front, rear, right or left; on its top the 
 Safety Valve is placed. The saddle has an area equal to that of Stop 
 Valve and Safety Valve combined. The rear head carries a blow-off^ flange 
 of about same size as the feed flange, and a Mujihead curved to fit the head, 
 the manhole supported by a strengthening ring outside. On each side 
 of the shell a square bar, the tile-bar, rests loosely in flat hooks riveted to 
 the shell. This bar supports the side tiles whose other ends rest on the side 
 walls, thus closing in the furnace or flue on top. The top of the tile bar is 
 two inches below low water li?ie. The bars rise from front to rear at the 
 rate of one inch in twelve. When the boiler is set, they must be exactly level, 
 the whole boiler being then on an incline, i. e., with a fall of one inch 
 in twelve from front to rear. 
 
 It will be noted that this makes the height of the steam space in front 
 about two-thirds the diameter of the shell, while at the rear the water occu- 
 pies two-thirds of the shell, the whole contents of the drum being equally 
 divided between steam and water. The importance of this will be explain- 
 ed hereafter. 
 
 The tubes extend through the tube sheets into which they are expand- 
 ed with roller expanders; opposite the end of each and in the head plates 
 
 —134— 
 
H 
 a> 
 
 2. 
 5' 
 
 n> 
 CD 
 
 ^ 
 
 CO 
 o 
 
IS placed a hand hole of slightly larger diameter than the tube and through 
 which it can be withdrawn. These hand holes are closed by small cast iron 
 hand hole plates, which by an ingenious device for locking can be removed in 
 a few seconds to inspect or clean a tube. The cut opposite shows these 
 hand hole plates marked H. In the upper corner one is shown in detail, 
 H2 being the top view, H3 the side view of the plate itself, the shoulder 
 showing the place for the gasket. Hi is the yoke or crab placed outside to 
 support the bolt and nut. 
 
 Inside of the shell is located the mud drum D, placed well below the water 
 line usually paralled to and three inches above the bottom of the shell. It is 
 thus completely immersed \n the hottest water in the boiler. It is of oval section 
 slightly smaller than the manhole, made of strong sheet iron with cast 
 iron heads. It is entirely enclosed except about eighteen inches of its up- 
 per portion at the forward end, which is cut away nearly parallel to the 
 water line. Its action will be explained below. The feed pipe F enters it 
 through a loose joint in front; the blow-off pipe N is screwed tightly into its 
 rear head, and passes by a steam tight joint through the rear head of the 
 shell. Just under the steam nozzle is placed a dry pan or dry pipe A. A de- 
 flection plate L extends from the front head of the shell inclined upwards, to 
 some distance beyond the mouth or throat of the front water leg. It will 
 be noted that the throat of each water leg is large enough to be the practi- 
 cal equivalent of the total tube area, and that just where it joins the shell it 
 increases gradually in width by double the radius of the flange. 
 
 ERECTION AND WALLING IN. 
 
 In setting the boiler we place its front water leg firmly on a set of strong 
 cast iron columns, bolted and braced together by the door frames, dead- 
 plate, etc., and forming the fire front. This is the fixed end. The rear 
 water leg rests on rollers which are free to move on cast iron plates firmly set 
 in the masonry of the low and solid rear wall. Wherever the brickwork 
 closes in to the boiler broad joints are left which are filled in with tow or 
 waste saturated with fireclay, or other refractory but pliable material. 
 Thus the boiler and its walls are each free to move separately during expan- 
 sion or contraction, without loosening any joints in the masonry. On the 
 lower, and between the upper tubes, are placed light fire brick tiles. The 
 lower tier extends from the front water leg to within a few feet of the rear 
 one, leaving there an upward passage across the rear ends of the tubes for 
 the flame, etc. The upper tier closes in to the rear water leg and extends 
 forward to within a few feet of the front one, thus leaving the opening for 
 the ganes in front. The side tiles extend from side walls to tile bars and 
 close up to the front water leg and front wall, and leave open the final up- 
 take for the waste gases over the back part of the shell, which is here cov- 
 ered above water line with a row lock of firebrick resting on the tile bars. 
 The rear wall of the setting and one parallel to it arched over the shell a 
 few feet forward form the uptakes. On these and the rear portion of the 
 side walls is placed a light sheet-iron hood, from which the breeching leads 
 to the chimney. When an iron stack is used this hood is stiffened by L 
 and T irons so that it becomes a truss carjyijig the weight of such stack and 
 distributing it to the side walls. A good example of this latter style of 
 braced hood is seen in the half tone cut of the People' s Railway Co. , on 
 page 51, where the four side walls of the three 200 horse-power boilers thus 
 carry the heavy stack. In the Central Distillery Plant, (see half tone cut 
 
 —136— 
 
Hi 
 
 Hi. 
 
 No^e: 0.,-. Hollow SlQubolt with 
 Removable' PIuo., 
 
 Detail of Water-lee. Hand Hole Plates and Yokes, etc., of Heine Boilers. 
 
on page 120, three of the 300 horse- power boilers are thus equipped, while 
 the fourth boiler, put in later, carries its stack in the same way. In the 
 UnioJi Depot Ry. Plant, 1750 horse-power (see half tone cut on page 128), 
 the hood is dispensed with and a long breeching, circle top, flat bottom, 
 runs over all the boilers, its width spanning the distance between uptake 
 walls ; over each boiler is placed a stout cast iron frame, bolted to the 
 bottom of the breeching and containing a swinging damper. The Anheuser. 
 Busch Plant, 2400 horse-power (see half tone cut on page 170 has a circular 
 iron flue supported on I beams just over the rear aisle, into which short 
 necks from the hoods open from the side ; each neck contains a swinging 
 damper. We are often obliged by local circumstances to carry the breeching 
 out forward or midway of the boiler to one side. There is no difficulty of 
 adapting our flue connections to such conditions. Swinging- dampers are 
 always to ho^ preferred; sliding dampers are apt to stick, and always require 
 considerable force to move them. The cut on page 139 shows the style of setting 
 generally used by us. With moderate firing and dry coals, it will practically 
 prevent smoke. With highly bituminous coals and somewhat pushing the 
 fires some smoke will result. The bridge wall is hollow and has small slotted 
 openings in rear to deliver hot air into the half consumed gases which roll 
 over the bridge wall into the combustion chamber. It receives its air from 
 channels in the hollow side walls (controlled by small cast iron slides), 
 through a cross flue at the rear end and a number of small flues under the 
 floor of the combustion chamber, as shown in the cut. In the rear wall of 
 the combustion chamber is an arched opening, closed by a cast iron door, 
 which in turn is shielded by a dry firebrick wall easily removable. For 
 special fuels, for smoke prevention, etc., there are now to be had various 
 forms of furnaces, automatic stokers, rocking grate-bars, etc. Heine 
 boilers have been set and operated successfully with these various devices. 
 They are not all equally applicable in all localities nor adapted to the same 
 conditions. As a rule we find that our customers or their engineers under- 
 stand their local fuels and local conditions best, and we are always glad to 
 adapt our setting to such of these devices as they may select. 
 
 OPERATION. 
 
 The boiler being filled to middle water line, the fire is started on the 
 grate. The flame and gases pass over the bridge wall and under the lower 
 tier of tiling, finding in the ample combustion chamber, space, temperature 
 and air supply for complete combustion, before bringing the heat in contact 
 with the main body of the tubes. Then, when at its best, it rises through 
 the spaces between the rear ends of the tubes, between rear waterleg and 
 back end of tiling, and is allowed to expend itself on the entire tube heating 
 surface without meeting any obstruction. Ample space makes leisurely pro- 
 gress for the flames, which meet in turn all the tubes, lap round them and 
 finally reach the second uptake at the forward end of the top tier of tiling 
 with their temperature reduced tc less than 900° Fahrenheit. This 
 has been measured here, while wrought iron would melt just above the lower 
 tubes at rear end, showing a reduction of temperature of over 1,800° 
 Fahrenheit between the two points. As this space is studded with water 
 tubes swept clean by a positive and rapid circulation, the absorption of 
 this great amount of heat is explained. The gases next travel under the 
 bottom and sides of the shell and reach the uptake at just the proper tem- 
 perature to produce the draft required. This varies of course according to 
 
 —138— 
 
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 2. 
 5" 
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 DD 
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chimney, fuel, duty required, etc. With boilers running at their rated 
 capacity 4o0° Fahrenheit are seldom exceeded. Meanwhile as soon 
 as the heat strikes the tubes the circulation of the water begins. The water 
 nearest the surface of the tubes becoming warmer rises, and as the tubes 
 are higher in front this water flows towards the front water leg where it 
 rises into the shell, while colder water from the shell falls down the rear 
 water leg to replace that flowing forward and upward through the tubes. 
 
 This circulation, at first slow, increases in speed as soon as steam begins 
 to form. Then the speed with which the mingled current of steam and 
 water rises in the forward water leg will depend on the difference in weight 
 of this mixture, and the solid and slightly colder water falling down the 
 rear water leg. The cause of its motion is exactly the same as that which 
 produces draft in a chimney as explained in the discussion of "A Modern 
 Boiler Plant,'' page 116. The maximum velocity will be reached when the 
 mixture is about half steam and half water. As the area of the throat of 
 the water leg is practically equivalent to the aggregate tube area (offsetting the 
 greater amount of skin friction in the tubes against the reduced area of the 
 throat), there will be nothing to interfere with Wiefree action of gravity and 
 the full speed will be maintained as long as steam is being made. This circu- 
 lation must be well borne in mind. It is forward through the tubes, upward 
 through the front water leg, to the rear in the shell, and down through the 
 rear water leg. At the forward throat of the shell the channel slightly en- 
 larges by reason of two outward flanges of the water leg. This greatly 
 facilitates the liberation of the steam, and is the best form of orifice. (Bate- 
 man's experiments, Proc. Inst. Mech. Eng'rs, 1866, gives this form of orifice 
 95 per cent of theoretical capacity.) The deflection plate L assists in 
 directing the circulation of the water to the rear. Thus the steam bubbles 
 obtain a trend towards the rear, throwing the spray in a direction away 
 from the flow of steam. It also has the effect of increasing the liberating 
 surface. For each section of this moving surface of water, as it is deliver- 
 ing its load of steam, sweeps rapidly to the rear, making room for the next 
 section, thus constantly presenting a fresh surface for this work. 
 
 The shallowness of the water at the front of the shell makes it easier 
 for the steam to pass through; its depth at the rear ensures a solid body of 
 water for replenishing the rear water leg and tubes. The height of the 
 steam space in front removes the nozzle far out of reach of any spray; the 
 deflection plate catches and deflects any sudden spurt, while finally the dry 
 pan or dry pipe draws the steam from a large area, from three sides, thus 
 preventing any local disturbance. These appliances make it possible to run 
 the Heine Boiler 50 per cent above rating with less than otie-ffth of one per 
 cent entrainment. 
 
 The action of the mud drum is as follows: The feed water enters it 
 through the pipe F about one-half inch above its bottom; even if it has 
 previously passed the best heaters it is colder than the water in the boiler. 
 Hence it drops to the bottom, and, impelled by the pump or injector, 
 passes at a greatly reduced speed to the rear of the mud drum. As it is 
 gradually heated to near boiler temperature it rises and flows slowly in re- 
 verse direction to the open front of the mud drum; here it passes over in a 
 thin sheet and is immediately swept backward into the main body of water 
 by the swift circulation, thus becoming thoroughly mixed with it before it 
 
 —140— 
 
reaciies the tubes. During this process the mud, lime salts and other pre- 
 cipitates are deposited as a sort of semi-fluid "sludge" near the rear end of 
 the mud drum, whence it is blown off at frequent intervals through the 
 blow-off valve N. As the speed in the mud drum is only about one-fiftieth 
 of tliat in the feed water pipe, plenty of time is given for this action. Any 
 precipitates which may escape the mud drum at first, will of course form a 
 scale on the inside of the tubes, etc. But the action of expansion and 
 contraction cracks off scale on the inside of a tube much faster than on the 
 outside, and then the circulation sweeps, the small chips, like broken egg- 
 shells, upward, and as they pass over the mouth of the mud drum they drop 
 in the eddy, lose velocity in this slow current and fall to the bottom, and, 
 being pushed by the feed current to the rear end, are blown off from the 
 mud drum with other refuse. On opening a Heine boiler after some months 
 service, such bits of scale, whose shape identifies them, are always found 
 in the mud of the mud drum. Very little loose scale is found on the 
 bottom of the water legs; the current through the lower tubes, always the 
 swiftest, brushes too near the bottom to allow much to lodge there. 
 
 This explanation of the action of the mud drum shows how the 
 inside of the tubes may be kept clean. To keep the outside clear of soot and 
 ashes which deposit on, and sometimes even bake fast to the tubes, each 
 boiler is provided with two special nozzles with both side and front outlets, 
 a short one for the rear, a long one for the front. They are of three-eighth 
 inch gas pipe and each is supplied with steam by a one-half inch steam hose. 
 The nozzle is passed through each stay bolt in turn, and thus delivers 
 its side jets on the three or four tubes adjacent, with the full force of the 
 steam, at the short range of two inches, kfiocking the soot and ashes off com- 
 pletely, while the end jet carries them into the main draft current to lodge 
 at points in breeching or chimney base convenient for their ultimate removal. 
 An inspection of the cuts will show that the stay bolts are so located 
 that the nozzle can in turn be brought to bear on all sides of the tubes. As 
 soon as the nozzle is withdrawn from the stay bolt, this is closed air-tight 
 by a plain wooden plug. 
 
 In cleaning a boiler it is only necessary to remove every fourth or fifth 
 handhole plate in the front water leg; the water hose, supplied with a 
 short nozzle, can be entered in all the adjacent tubes, owing to the 
 ample dimensions of the water leg. In the rear water leg only one or two 
 handholes in the lower row need be opened to let the water and debris 
 escape. The others in rear water leg are frequently left imtouched for years. 
 A lamp or candle hung on a wire through the manhead may be held oppo- 
 site each tube so that it can be perfectly inspected from the front. Once or 
 twice a year, where the water is very scale bearing, it may be advisable 
 to take off all the handhole plates of the front water leg and pass a 
 scraper through all the tubes in succession. Aside from the plain cylinder 
 boiler there is no boiler so completely accessible for internal and external 
 inspection as the Heine. The ashes which deposit in the combustion 
 chamber are removed through the ashpit door in the rear wall, never allow- 
 ing it to become more than one-third full. 
 
 We furnish with each boiler a set of "Rules for operation" in a neat 
 frame, adapted to be hung up in the boiler room. 
 
 —141— 
 
SUPERIORITY OF THE HEINE SAFETY BOILER. 
 
 In the discussion of A Modern Steam Plant we have pointed out the 
 four principal offices of a good boiler, and have explained why water 
 tube boilers best fulfill the conditions of the problem. Without denying 
 the merits of other systems of construction, we claim that the Heine boiler 
 stands at the very head and front in the good qualities essential to complete 
 performance. 
 
 1st. It bestabsorbs and transmits heat; hence economy and capacity. 
 
 2d. It will hold hig^h pressures with greatest safety. 
 
 3d. It best separates the Steam from the Water, ensuring- Dryness. 
 
 4th. It is best adapted to precipitate and discharge scale and mud. 
 
 We ask a fair and critical examination of our description of the Heine 
 Boiler, to which we shall refer in elucidating the above points. 
 
 ABSORPTION AND TRANSMISSION OF HEAT. 
 
 This, the most important work of the boiler, determines its economy 
 and capacity, and must be discussed in connection with the furnace and 
 the draft. For it is not sufficient to so construct the boiler that it will 
 best absorb and transmit the heat, but it must also be so arranged that the 
 heat can best reach it, and that nothing in its design will interfere with the 
 best plan of furnace construction, nor increase unnecessarily the demands 
 on the chimney. 
 
 For absorbing and transmitting heat nothing can be better than a nest 
 of tubes placed entirely in the flue, which the hot products of combustion 
 must traverse on their way from combustion chamber to chimney, especi- 
 ally when free and unimpeded circulation of the water is provided for. 
 Mr. Babcock, in his interesting lecture on water circiUation (Cornell Uni- 
 versity, 1890), has shown with great clearness that it depends, not as some 
 have supposed, on the amount of inclination of the tubes, but *'is a func- 
 tion of the difference in density of the two columns," the one of mingled 
 steam and water, the other of solid water. The simple mode of calculation 
 he suggests for finding the velocity of circulation gives us about twelve to 
 eighteen feet as the average natural speeds for that general class of water 
 tube boilers of which the Heine is a type. The cause of the circulation 
 once understood, it is clear that any sharp turns or contractions which offer 
 resistance to the flow will retard it in two ways. First, by altering- the 
 conditions of equilibrium on which the speed depends. Second, since a 
 river can not rise higher than its source, the speed lost by such an obstacle 
 can not be regained; the loss in speed at this point will therefore be mul- 
 tiplied, at other points having larger areas, by the ratio those areas bear 
 to this contracted one. In most boilers of this class there are between the 
 tubes and the drum several points where the contents of seven, nine or 
 
 —142— 
 
even twelve tubes have to pass through an opening equal to one tube area. 
 Every such place first disturbs the conditions on which the speed depends 
 by absorbing some of the existing "head" (or difference in weight). Sec- 
 ond, the maximum speed depending on the head can exist only at the least 
 such opening, and hence in the nest of tubes the circulation will be re- 
 duced to oiie-seventli, one-niuth, or one-twelfth of the natural speed. 
 In Heine Boilers there are no such contractions of area, even the smallest 
 throat areas being 65 to 90 per cent of the aggregate tube area. 
 
 The Heine Boiler g-ains another advantage from this fact. The water 
 in the upper tubes having less "head," begins with less speed than that in 
 the lower tier; the heating surface of the upper tubes will then be somewhat 
 less active than that of the lower tubes. Since they get the first heat, 
 more steam will be made in the lower tubes, further increasing the original 
 difference in velocity. The combined effect is that the circulation through 
 the lower tubes is much faster than through the upper ones. The obstruc- 
 tions before noted will multiply this difference, since only the more rapid 
 current will there make its way at the expense of the sluggish one. Thus 
 the effectiveness of the upper tubes is largely curtailed. The full throat 
 area of the Heine Boiler, on the other hand, leaves room for all the cur- 
 rents, hence the full efficiency of the upper tubes is preserved. 
 
 In the older types of this class of water tube boilers the tubes only are 
 inclined, and therefore the return circulation in the rear has to pass through 
 small tubes several feet in length, nearly vertical. The escaping gases 
 pass around them, tending to create an upward circulation along the sur- 
 face, which must somewhat check the downward flow. Everybody daily 
 observes that water invariably "swirls" when it escapes through a small 
 round hole or a tube from a wash bowl, bath tub or barrel. We all know 
 how vexatious is the delay caused by it. This action, being independent 
 of the surrounding pressure, takes place in the short tubes just mentioned, 
 and retards the flow^. 
 
 In the Heine boiler this Is done away with. The water at the rear end 
 of the shell is about a foot deeper than in front, the openings are large and 
 rectangular, and the downward flow is through a rectangular chamber 
 equal in section to the ag-g-reg-ate tube area. Swirling is impossible and 
 the tubes are fully supplied with solid water under all circumstances. 
 
 The circulation of the water is the life of all w^ater tube boilers. 
 Craddock's experiments show how its speed multiplies the effectiveness 
 of heating surface. Details of construction which reduce it to less than 
 one-fifth its natural velocity are therefore faulty, especially when this re- 
 duced speed is found in the tubes. The Heine Boiler carefully avoids any 
 such obstructions and the natural speed of circulation is maintained 
 throughout. 
 
 Therefore the effectiveness of its heating surface for the absorption 
 and transmission of heat is much greater than that of other boilers. 
 
 All fuels require much air, great heat, space for expansion, and time 
 for their complete combustion. An arched chamber, composed entirely of 
 fire brick, would be the ideal furnace, in which combustion should be 
 completed without meeting any cooling surface, the products when at their 
 greatest temperature to be launched into and amongst the heating surfaces 
 of the boiler. The nearer a furnace can be made to approach these condi- 
 tions the better will be its work. The other extreme is the internally fired 
 
 —143— 
 
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boiler, whose performance on bituminous coals is very inferior in spite ot 
 its smaller loss by radiation. Between them lie the return tubular boilers, 
 and those water tube boilers whose furnaces are separated from their com- 
 bustion chambers by the first pass of the nest of tubes. The heating- sur- 
 faces of a boiler are such for the Avater only; in reference to the flame 
 they are cooling surfaces. Brought in contact with the gases at the be 
 ginning of combustion they lower their temperature below the required 
 point. This results in the direct loss of much of the heating power of 
 the volatile part of the fuel which escapes unburnt, and in the indirect loss 
 due to impairment of the conductivity of the heating surface owing to de- 
 posit of much soot. As the first third of the heating surface thus encoun- 
 tered absorbs between 60 and 70 per cent of the heat (Graham's experi- 
 ments, 1858), it is useless to expect secondary combustion of any practical 
 value in a combustion chamber placed beyond it, with no means of restor- 
 ing the lost temperature. This method of construction probably grew out 
 of the pretty widespread belief that heating surface placed at right angles 
 to the course of the flame was much more effective than in any other rela- 
 tive position. Even if this were true the old adage, "always catch your 
 hare before you cook him," should induce prudent men not to allow its 
 application to vitiate their furnace construction. It is probably true only 
 for radiant heat; no experiments are adduced to prove it true for currents 
 of hot gas; there it is plainly a case of "faith without works. " On the 
 other hand German experiments (Stuehlen Ing. Kal., 1892) show tube 
 heating surface parallel to the current 30 per cent more effective than 
 when placed at right angles. The Heine boiler setting approximates the 
 ideal furnace. Fire place and combustion chamber are of fire brick, except 
 that minimnm of tube surface required to support the fire brick roof, ex- 
 perience having shown that arches are too short-lived where the soda 
 of the ashes under high temperatures fluxes the fire brick. The radiation 
 from side walls and floor is arrested and utilized to pre-heat the small 
 amount of air thrown into the gases at the bridge wall. Having passed 
 the combustion chamber, flame and gases are thrown in contact w^ith the 
 w^hole of the tuhe heating surface, which they envelope and strike at all 
 angles, the main trend being parallel to the tubes. Observation shows 
 that they roll around, mix, break up, combine, etc., according to natural 
 laws, and following many causes, to the apparent neglect of some single one 
 the professor may lay down in the lecture room, or the draftsman prescribe 
 by the conventional arrow. In the Heine boiler and furnace we arrange 
 for space, time, air and heat for the best combustion, then open out into 
 an ample flue, containing all the tubes, and like the Brooklyn alderman 
 with the gondolas, "leave the rest to nature'' The small tiles on the 
 upper and lower tier of tubes make adjustments of flue areas, to suit local 
 and possibly changing requirements, possible at all times. The trend of 
 the gases is the natural one, rising gradually towards the stack. We thus 
 avoid that loss in chimney power incident to pulling hot gases downwards 
 against their bent. 
 
 Having shown that with the most free circulation of the water, we con- 
 bine the best furnace arrangement, the natural circulation of the hot gases, 
 the equal exposure of the total heating surface to them, and the least de- 
 mands on the chimney, we have explained w^hy the Heine Boiler ranks first 
 in economy and capacity. Our many customers will gladly attest the results. 
 
 —145— 
 
The facilities for observing and cleaning the heating surfaces through 
 Ihe hollow staybolts have been fully explained in the description of the 
 boiler. The effect of this on the economy and capacity must be here 
 noted. As human nature goes, the fireman will not begin to clean the 
 heating surfaces until he has to. In the Heine boiler, as he blows through 
 each staybolt in turn, the cleaned section and increased draft reward him 
 at once by a rise in the steam pressure while cleaning-. Under the old 
 plan of cleaning through side doors in the walls, cold air rushes in, and 
 the pressure drops while cleaning, and does not rise again until the work 
 is completed and the doors again closed. Furthermore, the absence of 
 these doors in the side walls of the Heine boiler makes them less liable to 
 crack and leak. 
 
 SAFETY AT HIGH PRESSURES. 
 This depends on the qualities of the materials, the workmanship, the 
 proper arrangement of the parts, avoidance of unequal expansion and con- 
 traction, and accessibility for inspection, cleaning and repairs. 
 
 We use no cast iron in any parts subject to tensile stress. In this we 
 follow the rule laid down by the AMERICAN BOILER MANUFACT- 
 URER'S ASSOCIATION (Proceedings 1889): 
 
 CAST IRON— Should be of soft, gray texture and high degree of ductil- 
 ity. To be used only for hand-hole plates, crabs, yokes, etc., 
 and manheads. It is a dangerous metal to be used in mud 
 drums, legs, necks, headers, manhole rings, or any part of a 
 boiler subject to tensile strains; its use should be prohib- 
 ited for such parts." 
 For shells, water legs and drums we use a first-class flange steel made 
 for us and inspected before it leaves the steel works under the following: 
 
 SPECIFICATIONS FOR BOILER PLATES FOR HEINE SAFETY 
 
 BOILERS. 
 
 STEEL.— Homogeneous Steel made hy the OPEN HEARTH process, 
 and having the following qualities: 
 
 TENSILE STRENGTH.— 55,000 to 62,000 lbs. per square inch. 
 
 ELASTIC LIMIT.— Not under 32,000 lbs. per square inch. 
 
 ELONGATION.— 20 per cent for plates ft inch thick or less, 22 J^ per cent 
 for plates over ft inch and under ^ inch thick, 25 per cent 
 for plates 3/^ inch thick and over. 
 
 TEST SECTION.— To be 8 inches long, planed or milled edges; its crosL 
 sectional area shall not be less than one-half of one square 
 inch, nor shall its width ever be less than the thickness of the 
 plate. Every third test piece to be of the shape and dimen- 
 sions prescribed by the rules of the United States Board of 
 Supervising" Inspectors of Steamboats. 
 
 BENDING TEST.— Steel up to ^ inch thickness must stand hot and cold 
 bending double, and being hammered down on itself; above 
 that thickness, it must bend round a mandrel of diameter one 
 and one-half times the thickness of plate down to 180° . All 
 without showing signs of distress. 
 
 NICKED SAMPLE.— When a sample is broken, after being nicked, the 
 appearance of laminations or cold shuts, shall cause the re- 
 jection of the plates represented by the sample. 
 
 —146— 
 
AXiL TESTS. — To be made at the steel mill by the inspectors of the Roberx 
 W. Hunt & Co. Bureau of Inspection and Tests. 
 
 CHEMICAL TESTS— Will be required, and if they show more than ^0.04 
 per cent Phosphorus, or more than 0.03 per cent Sulphur, the 
 plates will be rejected. 
 
 This is the same as the standard adopted by the Americal Boiler Man- 
 ufacturers' Association, except that we have increased the requirements 
 for elongation somewhat; we have further added the tests on the section 
 used by the United States Board of Supervising Inspectors, to meet the 
 requirements of cities prescribing the "Marine" tests. It is well known 
 that the same steel will show higher t. s. on the "Marine" section than on 
 the 8 inch section, but the latter is best for showing the elongation. 
 
 The tubes are the standard American wrought iron boiler tubes, all 
 tested by hydrostatic pressure at the tube mills. They are intended to be 
 the weakest parts of the structure. As already explained, a tube giving 
 way from internal pressure suffers a local rupture merely; the boiler will 
 require several minutes to empty itself through a tube, resulting in a 
 gradual though rapid decrease of pressure, an extinguishing of the fire, and 
 no explosion. 
 
 The staybolts are made of best butt-welded hydraulic tubing. The 
 threads on them are therefore cut into solid metal all around, which 
 would be doubtful were lap-welded or built up tubing used. They are so 
 proportioned that in testing to rupture they part in the solid metal but 
 do not strip the thread. The ends are carefully peaned over. 
 
 The rivets are according to American Boiler Manufacturer's Association 
 standard, which we quote: 
 
 **KIVETS to be made of good charcoal iron, or of a very soft, mild steel 
 running between 50,000 and 60,000 pounds tensile strength 
 and showing an elongation of not less than 30 per cent in 
 eight inches, and having the same chemical composition as 
 specified for plates." 
 In all the processes of manufacture wc follow the best boiler shop prac- 
 tice of the United States as laid down by the American Boiler Manufactur- 
 ers' Association, as for instance in the rule for flanging: 
 ''FliANGING to be done at not less than a good, red heat. Not a single 
 blow to be given after the plate is cooled down to less than 
 cherry red by daylight. After flanging, all plates should be 
 annealed by uniform cooling from an even dull red heat for 
 the whole sheet in the open air." 
 Having built up our boiler of the very best materials, and by the best 
 methods of workmanship, we erect it in such a way that there can be no 
 unequal expansion strains. 
 
 The entirely free and unchecked circulation of water and fire has been 
 fully explained; this equalizes temperatures not only when in full opera- 
 tion, but as soon as the fire is lit. This can be verified by feeling the ends 
 cf shell and water legs when starting fires. Besides this there is another 
 
 —147— 
 
equalizing tendency. The shell will stretcli more than the tubes from 
 the internal pressure; the lower tubes receiving g^reater heat, will expand 
 
 more from this cause. The two tendencies counterbalance beautifully, as 
 can be verified by delicate measurements on any Heine boiler while cold 
 and while hot and under heavy pressure. 
 
 Our method of supporting the boiler on the water legs, the front one 
 on a fixed support, the rear one on rollers, gives freedom for expansion 
 without undue stress on any part. The weight of the boiler filled with 
 water is thus carried on its strongest pai'ts. Most sectional boilers can 
 not be thus supported, having in place of the water legs, loose, many- 
 jointed constructions incapable of supporting any extra weight. 
 
 It is evident that ours is a much better way to support a boiler than to 
 hang it from a gallows frame by bolts or links. For these concentrate 
 strains equal to the whole weight of boiler and water on two points of the 
 shell, thus disturbing that equilibrium of stress obtained by giving it the 
 C3dindrical form. Another signal advantage of the Heine boiler is that it 
 is completed and thoroughly tested in the boiler shop before shipment. 
 
 Our style of setting, with horizontal travel of the gases, has two further 
 advantages over the up and down method. 
 
 1st. The cold air which rushes into the furnace when the doors are 
 opened for firing is drawn to the rear, away from the tube joints, in place 
 of up and among them. 
 
 2nd. The hot gases do not reach the shell until after passing the 
 entire tube heating surface, being then no longer hot enough to injure a 
 rivet joint; in the up and down type they make their first turn under a 
 rivet joint of the shell, after traversing only a third of the tube surface, 
 and in what is considered a combustion chamber hot enough to regenerate 
 the flame. Hence our shells are safer! 
 
 In all water tube boilers access must be had to each tube through some 
 form of hand hole plate. Some have each group of two, three or more 
 tubes controlled by a hand hole plate, some each single tube. Of course 
 the larger each such plate the more danger of cracks, leakage of joints, 
 etc. Elsewhere we have explained why only a few hand hole plates of 
 each set have to be removed for washing out a Heine boiler. But besides 
 this our hand hole plates are much safer than others in general use. A 
 typical form for sectional boilers is shown below. T T are the ends of the 
 
 —148- 
 
tubes and the joints are made outside as at J. J. on the cap C. On the 
 inside is merely a yoke Y to hold up the bolt B. This of course necessi- 
 tates another joint j under the nut. These joints have to be made tight 
 while the boiler is cold; this requires a nice exercise of judgment, since 
 strain enough must be put on the bolt both to counterbalance the internal 
 pressure of the boiler when steam is raised, and enough more to keep the 
 joint tight then. In other words, the stretch of the bolt has to be antici- 
 pated and more strain added. And this double strain is always on the 
 bolt whether the boiler is under steam or idle. It will not do to tighten 
 up on the bolt when the boiler is under steam. For leakage around the 
 threads will soon fill the hollow cap of the nut, which at any additional 
 turn of the nut will crack it open by hydrostatic pressure. If we have a 
 hand hole of 4^ inches diameter we have an area of 15.9 square inches to 
 cover. At 125 pounds steam pressure we have 1,987 pounds pressure 
 under the cap and about 150 pounds more under the nut to counteract be- 
 fore any strain becomes available to make the joints tight. It has often 
 happened that a cracked nut has caused a cap to blow off, scalding the at- 
 tendants. 
 
 With the Heine boiler the case is reversed; the single joint at J 
 is an inside one, this pressure of 1,987 pounds makes the joint, so that 
 
 the bolts can be drawn up when under steam, receiving but a trifling strain. 
 It is clear that this is the safe plan, while the other is not. We have thus 
 shown that in materials, workmanship, general design, settings, and in de- 
 tails of construction the Heine boiler is the safest. 
 
 SEPARATION OF WATER; DRYNESS OF STEAM. 
 
 In describing the functions of a boiler in a modern steam plant we have 
 shown to what causes the entrainment of water is due. The description 
 of the Heine boiler shows how the entirely unchecked circulation tends 
 away from the steam nozzle. The steam bubbles, lighter than the water, 
 pass through it on some diagonal course, a resultant from their own verti- 
 cal trend and the backward flow of the water. This throws the spra}- 
 away from the vapor with a momentum about two hundred times that of 
 the steam which flows towards the nozzle, with about one -fourth of the 
 
 —149— 
 
speed it attains in the steam pipe. The function of the dry pipe or dry 
 pan is well understood. Add this, and the action just described, to the fact 
 that the inclination of our shell removes the water line further from the 
 steam nozzle than in other boilers, and the reason why our steam is always 
 dry becomes clear. An active agency for drying the steam, present at ah 
 times in the boiler, more vigorous the more the boiler is pushed, ensures 
 dry steam always. On forcing- tests we have shown steam six times as dry 
 as our competitors. This has a decisive influence on the every day econ- 
 omy of a steam plant. 
 
 PRECIPITATION AND DISCHARGE OF SCALE AND MUD. 
 
 The Heine Boiler was originally developed under the difficult condi- 
 tions of boiler practice in the great Mississippi Valley. The problem was 
 not only the economic utilization of the highly bituminous coals, low in 
 calorific value as they are high in ash and volatile matter, but also the 
 making of steam from water strongly impregnated witli mineral salts 
 and frequently carrying a brown mixture of the sacred soils of several 
 great States. 
 
 The faults of the old style of mud drum were here but too apparent. 
 The various ingenious coil devices choked up the faster, the more effective 
 they were. The "Spray Feeds" wet the steam in the exact ratio of their 
 efficiency in scale precipitation. Tlie Heine mud di'um, holding the in- 
 coming feed water suspended for a time in an almost quiescent state, while 
 subject to the external contact of a rapid current of the hottest water in 
 the boiler, furnishes time, checked velocity and heat to induce precipi- 
 tation. The necessity of a high temperature to make the mineral salts in- 
 soluble has been before explained. Evidence of it is found in every boiler. 
 It is well known that any reduction in velocity favors the dropping of 
 sediment. Instead of checking the speed of circulation in the tubes 
 where the precipitates do harm, the Heine boiler provides this mud drum 
 where no fire can get at them to bake them into scale, but where they can 
 be collected and blown off at such intervals as their amount prescribes. 
 
 The fact that we have successfully replaced tvi^o-flue boilers in local- 
 ities where return tubulars were tabooed on account of bad water proves 
 the practical efficiency of our free circulation and submerged mud drum. 
 
 —150- 
 

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 cr 
 
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 O 
 
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 -152— 
 
Table No. 71. 
 Diameters, Circumferences and Areas of Circles. 
 
 Advancing by lOths. | 
 
 Advancing by 8ths. 
 
 E 
 
 i i 
 
 E 
 
 E 
 
 3 
 
 «' 
 
 E 
 
 E 
 
 3 
 
 rt 
 
 E 
 
 E 
 3 
 
 w 
 
 eI 
 
 e 
 
 3 
 
 «" 
 
 E 
 
 E 
 3 
 
 IS 
 
 5 
 
 U 0) 
 
 < 
 
 6 
 
 u 
 
 < 
 
 5 
 
 
 
 < 
 
 5 
 
 
 
 < 
 
 IS 
 
 Q 
 
 u 
 U 
 
 < 
 
 Q 
 
 U 
 
 2: 
 < 
 
 0,0 
 
 0,00U00 
 
 0,000000 
 
 8,0 
 
 25,133 
 
 50,2655 
 
 16,0'50,265 
 
 201,062 
 
 
 
 0,000 
 
 0,0000 
 
 10 1 
 
 31,42 
 
 78,540 
 
 20 
 
 62,83 
 
 314,16 
 
 0,1 
 
 0,31416 
 
 0,007854 
 
 1 
 
 25,447 
 
 51,5300 
 
 1:50,580 
 
 203,583 
 
 Vs 
 
 0,393 
 
 0,0123 
 
 V8 
 
 31,81 
 
 80,516 
 
 V8 
 
 63,2'^ 
 
 318,10 
 
 0,2 
 
 0,62832 
 
 0,031416 
 
 2 
 
 25,701 
 
 52,8102 
 
 2|50,894 
 
 206,120 
 
 Vi 
 
 0,785 
 
 0,0491 
 
 Vi 
 
 32,20 
 
 82,516 
 
 Vi 
 
 63,62 
 
 322,06 
 
 0,3 
 
 0,94248 
 
 0,070686 
 
 3 
 
 26,075 54,1061 
 
 3 51,208 
 
 208,672 
 
 % 
 
 1,178 
 
 0,1104 
 
 % 
 
 32,,59 
 
 84,541 
 
 % 
 
 64,01 
 
 320,05 
 
 0,4 
 
 1,2566 
 
 0,125664 
 
 4 
 
 26,389 
 
 55,4177 
 
 4 51,522 
 
 211,241 
 
 V2 
 
 1,571 
 
 0,1963 
 
 V2 
 
 32,99 
 
 86,590 
 
 V2 
 
 64,40 
 
 330,06 
 
 0,5 
 
 1,5708 
 
 0,196350 
 
 5 
 
 26,704 
 
 56,7450 
 
 5 51,836 
 
 213,825 
 
 B/8 
 
 1,903 
 
 0,3068 
 
 5/8 
 
 33,38 
 
 88,664 
 
 % 
 
 64,80 
 
 3:j4,io 
 
 0,6 
 
 1,8850 
 
 0,282743 
 
 6 
 
 27,018 
 
 58,0880 
 
 6 52,1.50 
 
 216,424 
 
 3/4 
 
 2,356 
 
 0,4418 
 
 3/4 
 
 33,77 
 
 90,763 
 
 % 
 
 6.5,19 
 
 338,16 
 
 0,7 
 
 2,1991 
 
 0,384845 
 
 7 
 
 27,332 
 
 59,44R8 
 
 7 52,465 
 
 219,040 
 
 7/fe 
 
 2,749 
 
 0,6013 
 
 7/fe 
 
 34,16 
 
 92,886 
 
 7/fe 
 
 65,58 
 
 342,25 
 
 0,8 
 
 2,5133 
 
 0,502655 
 
 8 
 
 27,646 
 
 60,8212 
 
 8 52,779 
 
 221.671 
 
 
 
 
 
 
 
 
 
 
 0,9 
 
 2,8274 
 
 0,636173 
 
 9 
 
 27,960 
 
 62,2114 
 
 9 53,093 
 
 224,318 
 
 1 
 
 3,142 
 
 0,7854 
 
 11 
 
 34,56 
 
 95,033 
 
 21 
 
 65,97 
 
 346.3S 
 
 
 
 
 
 
 
 
 
 Vs 
 
 3,534 
 
 0,9940 
 
 V8 34,95 
 
 97,205 
 
 Vs 
 
 66,37 
 
 350,50 
 
 1.0 
 
 3,1416 
 
 0,78540 
 
 9,0 
 
 28,274 
 
 63.6173 
 
 17,0 53.407 
 
 226,980 
 
 Vi 
 
 3,927 
 
 1,2272 
 
 14 35,34 
 
 99,402 
 
 14 
 
 66,76 
 
 a54,66 
 
 1 
 
 3,4558 
 
 0,95033 
 
 1 
 
 28,588 
 
 65,03''8 
 
 1 
 
 53,721 
 
 229,658 
 
 % 
 
 4,320 
 
 1,4849 
 
 S/fe 35,74 
 
 101 ,6a 
 
 i/8 
 
 67,15 
 
 358,84 
 
 2 
 
 3,7699 
 
 1,13097 
 
 2 
 
 28,903 
 
 66,4761 
 
 2 
 
 54,035 
 
 232,352 
 
 V2 
 
 4,712 
 
 1,7671 
 
 V2 36,13 
 
 103,87 
 
 V2 
 
 67,54 
 
 363,05 
 
 3 
 
 4,0841 
 
 1,32732 
 
 3 
 
 29,217 
 
 67,9291 
 
 3 
 
 54,350 
 
 235,062 
 
 % 
 
 5,105 
 
 2,0739 
 
 % 36,52 
 
 106,14 
 
 % 
 
 67,94 
 
 367,28 
 
 4 
 
 4,3982 
 
 1,53938 
 
 4 
 
 29,531 
 
 69,3978 
 
 4 
 
 54,664 
 
 237,787 
 
 3/4 
 
 5,498 
 
 2,4053 
 
 3/4 36,91 
 
 108,43 
 
 % 
 
 68,33 
 
 371,54 
 
 5 
 
 4,7124 
 
 1,76715 
 
 5 
 
 29,845 
 
 70,8822 
 
 5 
 
 54,978 
 
 240,528 
 
 % 
 
 5,890 
 
 2,7612 
 
 % 37,31 
 
 110,75 
 
 1/8 
 
 68,72 
 
 375,83 
 
 6 
 
 7 
 8 
 9 
 
 5,0265 
 5,3407 
 5,6549 
 5,9690 
 
 2,01062 
 2,26980 
 2,51469 
 2,83529 
 
 6 
 
 7 
 8 
 9 
 
 30,159 
 30,473 
 30,788 
 31,102 
 
 72,3823 
 73,8981 
 75.4296 
 76,9769 
 
 6 
 
 7 
 8 
 9 
 
 55,292 
 55,606 
 55,920 
 56,235 
 
 243,285 
 246,057 
 248.846 
 251,649 
 
 2 
 
 V8 
 
 6,283 
 6,676 
 7,069 
 7,461 
 
 3,1416 
 3,5466 
 3,9761 
 4.4301 
 
 12 
 
 Vs 
 
 37,70 
 38,09 
 38,48 
 38,88 
 
 113,10 
 115,47 
 
 117,86 
 120,28 
 
 22 
 V8 
 Vi 
 % 
 
 69,12 
 69,51 
 69,90 
 70,29 
 
 380,13 
 384,46 
 388,82 
 393,20 
 
 2,0 
 1 
 2 
 3 
 
 6,2832 
 6,5973 
 6,9115 
 
 7,2257 
 
 3,14159 
 3.46361 
 3,80133 
 4,15476 
 
 10,0 
 1 
 2 
 3 
 
 31,416 
 31,730 
 32,044 
 32,358 
 
 78,5398 
 80,1185 
 81,7128 
 83,3229 
 
 18,0 
 1 
 2 
 3 
 
 56,549 
 56,863 
 57,177 
 57,491 
 
 254,469 
 257,304 
 260,155 
 263,022 
 
 1/2 
 5/8 
 a/4 
 
 7/8 
 
 7,854 
 8,247 
 8,639 
 9,032 
 
 4,9087 
 5,4119 
 5,9396 
 6,4918 
 
 V2 
 6/8 
 3/4 
 7/3 
 
 39,27 
 39,66 
 40,06 
 40,45 
 
 122.72 
 125,19 
 127,68 
 130,19 
 
 V2 
 
 % 
 % 
 
 1/8 
 
 70,69 
 71,08 
 71,47 
 71,86 
 
 397,61 
 402,04 
 406,49 
 410,9T 
 
 4 
 5 
 6 
 
 7 
 8 
 
 7,5398 
 7,8540 
 8,1681 
 8,4823 
 8,7965 
 9,1106 
 
 4,52389 
 4,90874 
 5 30929 
 5,72555 
 6,15752 
 6,60520 
 
 4 
 5 
 6 
 7 
 8 
 9 
 
 32,673 
 32,987 
 33,301 
 33,615 
 33,929 
 34,243 
 
 84,9487 
 86,5901 
 88,2473 
 89,9202 
 91,6088 
 93,3132 
 
 4 
 6 
 6 
 
 7 
 8 
 9 
 
 57,805 
 58,119 
 58,434 
 58,748 
 59,062 
 59,376 
 
 265.904 
 268,803 
 271,716 
 274.646 
 277.591 
 280,552 
 
 3 
 
 V8 
 
 Vi 
 
 % 
 
 V2 
 
 5/8 
 
 9,425 
 9,817 
 10,210 
 10,603 
 10,996 
 11,388 
 
 7,0686 
 7,6699 
 8,2958 
 8,9462 
 9,6211 
 10,321 
 
 13 
 
 3/8 
 V2 
 % 
 
 40,84 
 41,23 
 41,63 
 42,02 
 42,41 
 42,80 
 
 132,73 
 135,30 
 137,89 
 140,50 
 143,14 
 145,80 
 
 23 
 
 Vs 
 Vi 
 
 3/8 
 V2 
 5/8 
 
 72,26 
 72,65 
 73,U4 
 73,43 
 73,83 
 74,22 
 
 415,48 
 420,00 
 424,56 
 429,13 
 433,74 
 438,36 
 
 3,0,9,4248 
 19,7389 
 
 7,06858 
 7,54768 
 
 11,0 
 
 1 
 
 34,558 
 34,872 
 
 95.0332 
 96,7689 
 
 19,0 
 1 
 
 59,690 
 60,004 
 
 283,529 
 286,521 
 
 iV4 
 
 11,781 
 12,174 
 
 11,045 
 11,793 
 
 7/& 
 
 43.20 
 43,59 
 
 148,49 
 151,20 
 
 3/4 
 
 1/8 
 
 74,61 
 75,01 
 
 443,01 
 447,69 
 
 2 10,053 
 
 8,04248 
 
 2 
 
 35,186 
 
 98,5203 
 
 2 
 
 60 319 
 
 289,529 
 
 4 
 
 12,57 
 
 12,566 
 
 14 
 
 43,98 
 
 153,94 
 
 24 
 
 75,40 
 
 452,39 
 
 3 10,367 
 
 8,55299 
 
 3 
 
 35,500 
 
 100,287 
 
 3 
 
 60,633 
 
 292,553 
 
 V8 
 
 12,96 
 
 13,364 
 
 Vs 
 
 44,37 
 
 156,70 
 
 V8 
 
 75,79 
 
 457,11 
 
 4! 10,681 
 
 9,07920 
 
 4 
 
 35.814 
 
 102,070 
 
 4 
 
 60,947 
 
 295,592 
 
 lA 
 
 13,35 
 
 14,186 
 
 % 
 
 44,77 
 
 159,48 
 
 Vi 
 
 76,18 
 
 461,86 
 
 5 10,996 
 
 9,62113 
 
 5 
 
 36,128 
 
 103,869 
 
 5 
 
 61,261 
 
 298.648 
 
 % 
 
 13,74 
 
 15,033 
 
 3/8 
 
 45,16 
 
 162,30 
 
 % 
 
 76,58 
 
 466,64 
 
 6!ll,310 
 
 10,1788 
 
 6 
 
 36,442 
 
 105,683 
 
 6 61,575 
 
 301,719 
 
 V2 
 
 14,14 
 
 15,904 
 
 V2 
 
 45,55 
 
 165,13 
 
 V2 
 
 76,97 
 
 471,44 
 
 7111,624 
 
 10,7521 
 
 7 
 
 36,757 
 
 107,513 
 
 7 61,889 
 
 304,805 
 
 5/8 
 
 14,53 
 
 16,800 
 
 5/8 
 
 45,95 
 
 167,99 
 
 % 
 
 77,36 
 
 476,26 
 
 811,938 
 
 11,3411 
 
 8 
 
 37,071 
 
 109,359 
 
 8 
 
 62,204 
 
 307,907 
 
 3/4 
 
 14,92 
 
 17,721 
 
 3/4 
 
 46,34 
 
 170,87 
 
 % 
 
 77,75 
 
 481,11 
 
 9 12,252 
 
 11,9459 
 
 9 
 
 37,385 
 
 111,220 
 
 9 
 
 62,518 
 
 311,026 
 
 7/8 
 
 15,32 
 
 18,665 
 
 7/fe 
 
 46,73 
 
 173,78 
 
 7/8 
 
 78,15 
 
 485,98 
 
 4,0 12,566 
 
 12,5664 
 
 12,0 
 
 37,699 
 
 113,097 
 
 20,0 
 
 62,832 
 
 314,159 
 
 5 
 
 15,71 
 
 19,635 
 
 15 
 
 47,12 
 
 176,71 
 
 25 
 
 78,54 
 
 490,87 
 
 1 12,881 
 
 13,2025 
 
 1 
 
 38,013 
 
 114,990 
 
 1 
 
 63,146 
 
 317,309 
 
 V8 
 
 16,10 
 
 20,629 
 
 Vs 
 
 47,52 
 
 179,67 
 
 Vs 
 
 78,93 
 
 495,79 
 
 2 
 
 13,195 
 
 13,8544 
 
 2 
 
 38,327 
 
 116,899 
 
 2 
 
 63,460 
 
 320,474 
 
 Vi 
 
 16,49 
 
 21,648 
 
 Vi 
 
 47,91 
 
 182,65 
 
 Vi 
 
 79.33 
 
 500,74 
 
 3 
 
 13,509 
 
 14,5220 
 
 3 
 
 38,642 
 
 118,823 
 
 3 
 
 63,774 
 
 323,655 
 
 3/8 
 
 16,89 
 
 22,691 
 
 3/8 
 
 48,30 
 
 185,66 
 
 3/8 
 
 79,72 
 
 505,71 
 
 4 
 
 13,823 
 
 15,2053 
 
 4 
 
 38,956 
 
 120,763 
 
 4 
 
 64,088 
 
 326,851 
 
 V2 
 
 17,28 
 
 23.758 
 
 V2 
 
 48,69 
 
 188,69 
 
 V2 
 
 80,11 
 
 510,71 
 
 5 
 
 14,137 
 
 15,9043 
 
 5 
 
 39,270 
 
 122,718 
 
 5 
 
 64,403 
 
 330,064 
 
 5/817,67 
 
 24,850 
 
 5/8 
 
 49,09 
 
 191,75 
 
 % 
 
 80,50 
 
 515,72 
 
 6 
 
 14,451 
 
 16,6190 
 
 6 
 
 39,584 
 
 124,690 
 
 6 
 
 64,717 
 
 333 292 
 
 3/4' 18,06 
 
 25,967 
 
 % 
 
 49,48 
 
 194,83 
 
 3/4 
 
 80,90 
 
 520,77 
 
 7 
 
 14,765 
 
 17,3494 
 
 7 
 
 39,898 
 
 126,677 
 
 7 
 
 65,031 
 
 336,535 
 
 % 18,46 
 
 27,109 
 
 % 
 
 49,87 
 
 197,93 
 
 7/S 
 
 81,29 
 
 525,84 
 
 8 
 
 1^5,080 
 
 18,0956 
 
 8 
 
 40,212 
 
 128,680 
 
 8 
 
 65 345 
 
 339.795 
 
 
 
 
 
 
 
 
 
 9 
 
 15,394 
 
 18,8574 
 
 9 
 
 40,527 
 
 130,698 
 
 9 
 
 65,659 
 
 343,070 
 
 6 18,85 
 V8 19,24 
 
 28,274 
 29,465 
 
 16 
 
 Vs 
 
 50,27 
 50,66 
 
 201,06 
 
 204,22 
 
 26 
 
 Vs 
 
 81,68 
 
 82,07 
 
 530,93 
 536,05 
 
 5,0 15,708 
 
 19,6350 
 
 13,0 
 
 40,841 
 
 132,732 
 
 21,0 
 
 65,973 
 
 346,361 
 
 JA 19,63 
 
 30,680 
 
 Vi 
 
 51,05 
 
 207,39 
 
 Vi 
 
 82,47 
 
 541,19 
 
 1 16,022 
 
 20,4282 
 
 1 
 
 41,155 
 
 134,782 
 
 1 
 
 66,288 
 
 349,667 
 
 3/8 20,03 
 
 31,919 
 
 3/8 
 
 51,44 
 
 210,60 
 
 3/8 
 
 82,86 
 
 546,35 
 
 2 16,336 
 
 21,2372 
 
 2 
 
 41,469 
 
 136,848 
 
 2 
 
 66,602 
 
 352,989 
 
 V2 20,42 
 
 33,183 
 
 V2 
 
 51,84 
 
 213.82 
 
 V2 
 
 83,25 
 
 551,55 
 
 3 16,650 
 
 22,0618 
 
 3 
 
 41,783 
 
 138,929 
 
 3 
 
 66,916 
 
 356.327 
 
 % 20,81 
 
 34,472 
 
 6/8 
 
 52,23 
 
 217,08 
 
 % 
 
 83,64 
 
 556,76 
 
 4i 16,965 
 
 22,9022 
 
 4 
 
 42,097 
 
 141,026 
 
 4 
 
 67,230 
 
 359,681 
 
 3/4 21,21 
 
 35,786 
 
 3/4 
 
 52,62 
 
 220,35 
 
 3/4 
 
 84,04 
 
 562,00 
 
 5 
 
 17,279 
 
 23,7583 
 
 5 
 
 42,412 
 
 143,139 
 
 5 
 
 67,544 
 
 363.050 
 
 % 21,60 
 
 37,122 
 
 % 
 
 53,01 
 
 223,65 
 
 7/fe 
 
 84,43 
 
 567,27 
 
 6 
 7 
 8 
 9 
 
 17,593 
 17,907 
 18,221 
 18,535 
 
 24,6301 
 25,5176 
 26,4208 
 27,3397 
 
 6 
 
 7 
 8 
 9 
 
 42,726 
 43,040 
 43,354 
 43,668 
 
 145,267 
 147.411 
 149,571 
 151,747 
 
 6 
 
 7 
 8 
 9 
 
 67 858 
 68,173 
 68,487 
 68,801 
 
 366,435 
 369.836 
 373,253 
 376,685 
 
 7 21,99 
 V8 22,38 
 Vi 22,78 
 3/8 23,17 
 
 38,485 
 39,871 
 41,282 
 42,718 
 
 17 
 
 V8 
 
 Vi 
 
 3/8 
 
 53,41 
 53,80 
 54,19 
 54,59 
 
 226,98 
 230,33 
 233,71 
 237,10 
 
 27 
 Vs 
 Vi 
 
 S/8 
 
 84,82 
 85,22 
 85,61 
 86,00 
 
 572,56 
 577,87 
 583,21 
 588,57 
 
 6,0 
 1 
 2 
 3 
 
 18,850 
 19,164 
 19,478 
 19,792 
 
 28,2743 
 29,2247 
 30,1907 
 31,1725 
 
 14,0 
 1 
 2 
 3 
 
 43,982 
 44,296 
 44,611 
 44,925 
 
 153,938 
 156,145 
 158,368 
 160 606 
 
 22,0 
 1 
 2 
 3 
 
 69,115 
 
 69,429 
 69,743 
 70,058 
 
 380,133 
 383,596 
 387,076 
 390,571 
 
 1/2 23,56 
 5/8123,95 
 3/4 24,35 
 % 24,74 
 
 44,179 
 45,664 
 47,173 
 
 48,707 
 
 V2 
 
 7A 
 
 54,98 
 55,37 
 55,76 
 56,16 
 
 240,53 
 243,98 
 247.45 
 250,95 
 
 V2 
 6/8 
 3/4 
 
 1/8 
 
 86.39 
 86,79 
 
 87,18 
 87,57 
 
 593,96 
 599,37 
 604,81 
 610,27 
 
 4 
 
 20,106 
 
 32,1699 
 
 4 
 
 45,239 
 
 162,860 
 
 4 
 
 70,372 
 
 394,081 
 
 8 25,13 
 
 50,265 
 
 18 
 
 56,55 
 
 254,47 
 
 28 
 
 87,96 
 
 615,75 
 
 5 
 
 20,420 
 
 33,1831 
 
 5 
 
 45,553 
 
 165,130 
 
 5 
 
 70,686 
 
 397,608 
 
 V8 25,53 
 
 51,849 
 
 Vs 
 
 56,94 
 
 258,02 
 
 Vs 
 
 88,36 
 
 621.26 
 
 6 
 
 20,735 
 
 34,2119 
 
 6 
 
 45,867 
 
 167,415 
 
 6 
 
 71,000 
 
 401,150 
 
 Vi 25,92 
 
 53,456 
 
 14 
 
 57,33 
 
 261,59 
 
 Vi 
 
 88,75 
 
 626,80 
 
 7 
 
 21,049 
 
 35,2565 
 
 7 
 
 46,181 
 
 169,717 
 
 7 
 
 71,314 
 
 404,708 
 
 3/8:26,31 
 
 55,088 
 
 3/8 
 
 57,73 
 
 265,18 
 
 3/8 
 
 89,14 
 
 632,36 
 
 8 
 
 21,363 
 
 36,3168 
 
 8 
 
 46,496 
 
 172.034 
 
 8 
 
 71,628 
 
 408,281 
 
 1/2126,70 
 
 56,745 
 
 V2 
 
 58,12 
 
 268,80 
 
 V2 
 
 89,54 
 
 637.94 
 
 S 
 
 21,677 
 
 37,3928 
 
 S 
 
 46,8101174,366 
 
 9 
 
 71,942 
 
 411.871 
 
 %l 27.10 
 
 58,426 
 
 5/8 
 
 58,51 
 
 272.45 
 
 % 
 
 89,93 
 
 643,55 
 
 
 
 
 
 
 
 
 
 %! 27,49 
 
 60,132 
 
 % 
 
 58.90 
 
 276,12 
 
 ^4 
 
 90,32 
 
 649,18 
 
 7,0 
 
 21,991 
 
 38,4845 
 
 15,0 
 
 47,124 
 
 176,715 
 
 23,0 
 
 72,257 415,476 
 
 1/8 
 
 27,88 
 
 61,862 
 
 1/8 
 
 59,30 
 
 279,81 
 
 1/8 
 
 90,71 
 
 654,84 
 
 1 
 
 22,305 
 
 39,5919 
 
 1 
 
 47,438 
 
 179,079 
 
 1 
 
 72,571 419,096 
 
 
 
 
 
 
 
 
 
 
 2 
 
 22,619 
 
 40,7150 
 
 2 
 
 47,752 
 
 181,458 
 
 2 
 
 72,885422,733 
 
 9 
 
 28,27 
 
 63,617 
 
 19 
 
 59,69 
 
 283,53 
 
 29 
 
 91,11 
 
 660,52 
 
 2 
 
 22,934 
 
 41,8539 
 
 3 
 
 48,066 
 
 183,854 
 
 3 
 
 73,1991426,385 
 
 V8 
 
 28,67 
 
 65,397 
 
 V8 
 
 60,08 
 
 287,27 
 
 Vs 
 
 91,50 
 
 666,23 
 
 ' 
 
 23,248 
 
 43,0084 
 
 4 
 
 48,381 
 
 186,265 
 
 4 
 
 73,513 430,053 
 
 Vi 
 
 29,06 
 
 67,201 
 
 V4 
 
 60,48 
 
 291,04 
 
 Vi 
 
 91,89 
 
 671,96 
 
 
 23,562 
 
 44,1786 
 
 E 
 
 48,695 
 
 188,692 
 
 5 
 
 73,827|433,736 
 
 3/8 
 
 29,45 
 
 69,029 
 
 3/8 
 
 60,87 
 
 294,83 
 
 % 
 
 92.28 
 
 677,71 
 
 
 23,876 
 
 45.3646 
 
 6 
 
 49,009 
 
 191,134 
 
 6 
 
 74,142,437,435 
 
 V2 
 
 29,85 
 
 70,882 
 
 V2 
 
 61,26 
 
 298,65 
 
 V2 
 
 92,68 
 
 683,49 
 
 
 24,190 
 
 46,5663 
 
 7 
 
 49,323 
 
 193,593 
 
 7 
 
 74,456 441,150 
 
 % 
 
 30.24 
 
 72,760 
 
 % 
 
 61,65 
 
 302.49 
 
 % 
 
 93,07 
 
 689.30 
 
 
 24,504 
 
 47,7836 
 
 8 
 
 49,637 
 
 196.067 
 
 8 
 
 74,770 444,881 
 
 % 
 
 30,63 
 
 74,662 
 
 3/4 
 
 62,05 
 
 306,35 
 
 % 
 
 93,46 
 
 695.13 
 
 _£ 
 
 24,819 
 
 49,0167 
 
 9'49,9d1 1198,557 
 
 9i75,084'448.627 
 
 7/S 
 
 31,02 76,589 
 
 7/fe 
 
 62,44 310,24 
 
 1/8 
 
 93.86 
 
 700.98 
 
 -153— 
 
Table No. 72. 
 
 Diameters and Circumferences of Circles, and the Contents 
 in Gallons at One Foot in Depth. 
 
 Diameter. 
 
 ClRCUM. 
 
 Area 
 
 Gallons. 
 1 Ft. 
 
 Diameter. 
 
 CiRCUM. 
 
 Area 
 
 Gallons. 
 1 Ft. 
 Depth. 
 
 Ft. 
 
 In. 
 
 Ft. 
 
 In. 
 
 in sq. 
 feet. 
 
 Depth. 
 
 Ft. 
 
 In. 
 
 Ft. 
 
 In. 
 
 in feet. 
 
 4 
 
 
 12 
 
 6>4" 
 
 12.56 
 
 93.97 
 
 13 
 
 6 
 
 42 
 
 4% 
 
 143.13 
 
 1070.45 
 
 4 
 
 1 
 
 12 
 
 9% 
 
 13.09 
 
 97.93 
 
 13 
 
 9 
 
 43 
 
 2>4 
 
 148.48 
 
 1108.06 
 
 4 
 
 2 
 
 13 
 
 1 
 
 13.63 
 
 101.97 
 
 
 
 
 
 
 
 4 
 
 3 
 
 13 
 
 ^Vs 
 
 14.18 
 
 103.03 
 
 14 
 
 
 43 
 
 11% 
 
 153.93 
 
 1151.21 
 
 4 
 
 4 
 
 13 
 
 7>4 
 
 14.74 
 
 110.29 
 
 14 
 
 3 
 
 44 
 
 ^% 
 
 169.48 
 
 1192.69 
 
 4 
 
 5 
 
 13 
 
 io>^ 
 
 15.32 
 
 114.57 
 
 14 
 
 6 
 
 45 
 
 6% 
 
 165.13 
 
 1234.91 
 
 4 
 
 6 
 
 14 
 
 1% 
 
 15.90 
 
 118.93 
 
 14 
 
 9 
 
 46 
 
 4 
 
 170.87 
 
 1277.86 
 
 4 
 
 7 
 
 14 
 
 m 
 
 16.49 
 
 123.38 
 
 
 
 
 
 
 
 4 
 
 8 
 
 14 
 
 7% 
 
 17.10 
 
 127.91 
 
 15 
 
 
 47 
 
 1% 
 
 176.71 
 
 1321.54 
 
 4 
 
 9 
 
 14 
 
 11 
 
 17.72 
 
 132.52 
 
 15 
 
 3 
 
 47 
 
 10% 
 
 182.65 
 
 1365.96 
 
 4 
 
 10 
 
 15 
 
 2M 
 
 18.34 
 
 137.21 
 
 15 
 
 6 
 
 48 
 
 8M 
 
 188.69 
 
 1407.51 
 
 4 
 
 11 
 
 15 
 
 6^ 
 
 18.98 
 
 142.05 
 
 15 
 
 9 
 
 49 
 
 5% 
 
 194.82 
 
 1467.00 
 
 5 
 
 
 15 
 
 8K 
 
 19.63 
 
 146.83 
 
 16 
 
 
 50 
 
 3K 
 
 201.06 
 
 1503.62 
 
 6 
 
 1 
 
 15 
 
 ll^-'B 
 
 20.29 
 
 151.77 
 
 16 
 
 3 
 
 51 
 
 0>2 
 
 207.39 
 
 1550.97 
 
 6 
 
 2 
 
 16 
 
 2M 
 
 20.96 
 
 156.78 
 
 16 
 
 6 
 
 51 
 
 10 
 
 213.82 
 
 1599.06 
 
 6 
 
 3 
 
 16 
 
 5^ 
 
 21.64 
 
 161.88 
 
 16 
 
 9 
 
 52 
 
 7^ 
 
 220.35 
 
 1647.89 
 
 5 
 
 4 
 
 16 
 
 9 
 
 22.34 
 
 167.06 
 
 
 
 
 
 
 
 6 
 
 5 
 
 17 
 
 0>8^ 
 
 23.04 
 
 172.33 
 
 17 
 
 
 53 
 
 4% 
 
 226.98 
 
 1697.45 
 
 5 
 
 6 
 
 17 
 
 3>4 
 
 23.75 
 
 177.67 
 
 17 
 
 3 
 
 54 
 
 2>8 
 
 233.70 
 
 1747.74 
 
 6 
 
 7 
 
 17 
 
 &H 
 
 24.48 
 
 183.09 
 
 17 
 
 6 
 
 64 
 
 11% 
 
 240.52 
 
 1798.76 
 
 5 
 
 8 
 
 17 
 
 9^8 
 
 25.21 
 
 188.60 
 
 17 
 
 9 
 
 65 
 
 9>8 
 
 247.45 
 
 1850.53 
 
 6 
 
 9 
 
 18 
 
 0% 
 
 25.96 
 
 194.19 
 
 
 
 
 
 
 
 5 
 
 10 
 
 18 
 
 3% 
 
 26.72 
 
 199.86 
 
 18 
 
 
 56 
 
 ^% 
 
 254.46 
 
 1903.02 
 
 5 
 
 11 
 
 18 
 
 7>8 
 
 27.49 
 
 205.61 
 
 18 
 
 3 
 
 57 
 
 4 
 
 261.58 
 
 1956.25 
 
 
 
 
 
 
 
 18 
 
 6 
 
 68 
 
 1% 
 
 268.80 
 
 2010.21 
 
 6 
 
 
 18 
 
 10>8 
 
 28.27 
 
 211.44 
 
 18 
 
 9 
 
 58 
 
 10% 
 
 276.11 
 
 2064.91 
 
 6 
 
 3 
 
 19 
 
 7>2 
 
 30.67 
 
 229.43 
 
 
 
 
 
 
 ■^ 
 
 6 
 
 6 
 
 20 
 
 4% 
 
 33.18 
 
 248.15 
 
 19 
 
 
 59 
 
 8% 
 
 283.62 
 
 2120.34 
 
 6 
 
 9 
 
 21 
 
 2>8 
 
 35.78 
 
 267.61 
 
 19 
 
 3 
 
 60 
 
 5% 
 
 291.03 
 
 2176.51 
 
 
 
 
 
 
 
 19 
 
 6 
 
 61 
 
 3M 
 
 298.64 
 
 2233.29 
 
 7 
 
 
 21 
 
 11% 
 
 38.48 
 
 287.80 
 
 19 
 
 9 
 
 62 
 
 o>^ 
 
 306.35 
 
 2291.04 
 
 7 
 
 3 
 
 22 
 
 9>i 
 
 41.23 
 
 308.72 
 
 
 
 
 
 
 
 7 
 
 6 
 
 23 
 
 6% 
 
 44.17 
 
 330.38 
 
 20 
 
 
 62 
 
 9% 
 
 314.16 
 
 2349.41 
 
 7 
 
 9 
 
 24 
 
 4>8 
 
 47.17 
 
 352.76 
 
 20 
 
 3 
 
 63 
 
 7/^8 
 
 322.06 
 
 2408.61 
 
 
 
 
 
 
 
 20 
 
 6 
 
 64 
 
 4% 
 
 330.06 
 
 2468.35 
 
 8 
 
 
 25 
 
 1>^ 
 
 60.26 
 
 375.90 
 
 20 
 
 9 
 
 65 
 
 2>4 
 
 338.16 
 
 2628.92 
 
 8 
 
 3 
 
 25 
 
 11 
 
 53.45 
 
 399.76 
 
 
 
 
 
 
 
 8 
 
 6 
 
 26 
 
 ^K 
 
 56.74 
 
 424.36 
 
 21 
 
 
 65 
 
 11^ 
 
 346.36 
 
 2590.22 
 
 8 
 
 9 
 
 27 
 
 5^ 
 
 60.13 
 
 449.21 
 
 21 
 
 3 
 
 66 
 
 9 
 
 354.65 
 
 2662.25 
 
 
 
 
 
 
 
 21 
 
 6 
 
 67 
 
 &% 
 
 363.06 
 
 2715.04 
 
 9 
 
 
 28 
 
 3>4 
 
 63.61 
 
 475.75 
 
 21 
 
 9 
 
 68 
 
 3% 
 
 371.54 
 
 2778.54 
 
 9 
 
 3 
 
 29 
 
 0>8 
 
 67.20 
 
 502.55 
 
 
 
 
 
 
 
 9 
 
 6 
 
 29 
 
 10>8^ 
 
 70.88 
 
 530.08 
 
 22 
 
 
 69 
 
 1% 
 
 380.13 
 
 2842.79 
 
 9 
 
 9 
 
 30 
 
 ^yi 
 
 74.66 
 
 658.35 
 
 22 
 
 3 
 
 69 
 
 10% 
 
 388.82 
 
 2907.76 
 
 
 
 
 
 
 
 22 
 
 6 
 
 70 
 
 8% 
 
 397.60 
 
 2973.48 
 
 10 
 
 
 31 
 
 5 
 
 78.54 
 
 587.35 
 
 22 
 
 9 
 
 71 
 
 6% 
 
 406.49 
 
 3039.92 
 
 10 
 
 3 
 
 32 
 
 2% 
 
 82.51 
 
 617.08 
 
 
 
 
 
 
 
 10 
 
 6 
 
 82 
 
 11^4 
 
 86.59 
 
 647.65 
 
 23 
 
 
 72 
 
 3 
 
 415.47 
 
 3107.10 
 
 10 
 
 9 
 
 33 
 
 9K 
 
 90.76 
 
 678.27 
 
 23 
 
 3 
 
 73 
 
 0>2 
 
 424.55 
 
 3175.01 
 
 
 
 
 
 
 
 23 
 
 6 
 
 73 
 
 9% 
 
 433.73 
 
 3243.65 
 
 11 
 
 
 34 
 
 ^% 
 
 95.03 
 
 710.69 
 
 23 
 
 9 
 
 74 
 
 7>4 
 
 443.01 
 
 3313.04 
 
 11 
 
 3 
 
 35 
 
 4>8' 
 
 99.40 
 
 743.36 
 
 
 
 
 
 
 
 11 
 
 6 
 
 36 
 
 1>2 
 
 103.86 
 
 776.77 
 
 24 
 
 
 75 
 
 4% 
 
 452.39 
 
 3383.15 
 
 11 
 
 9 
 
 36 
 
 10% 
 
 108.43 
 
 810.91 
 
 24 
 
 3 
 
 76 
 
 2>^ 
 
 461.86 
 
 3454.00 
 
 
 
 
 
 
 
 24 
 
 6 
 
 76 
 
 11% 
 
 471.43 
 
 3625.69 
 
 12 
 
 
 37 
 
 8% 
 
 113.09 
 
 848.18 
 
 24 
 
 9 
 
 77 
 
 •9 
 
 481.10 
 
 3597.90 
 
 12 
 
 3 
 
 38 
 
 5% 
 
 117.85 
 
 881.39 
 
 
 
 
 
 
 
 12 
 
 6 
 
 39 
 
 3>i 
 
 122.71 
 
 917.73 
 
 25 
 
 
 78 
 
 ^K 
 
 490.87 
 
 3670.95 
 
 12 
 
 9 
 
 40 
 
 0% 
 
 127.67 
 
 954.81 
 
 25 
 
 3 
 
 79 
 
 3% 
 
 500.74 
 
 3744.74 
 
 
 
 
 
 
 
 25 
 
 6 
 
 80 
 
 IK 
 
 510.70 
 
 3819.26 
 
 13 
 
 
 40 
 
 10 
 
 132.73 
 
 992.62 
 
 25 
 
 9 
 
 80 
 
 10% 
 
 620.76 
 
 3894.52 
 
 13 
 
 3 
 
 41 
 
 7)-2 
 
 137.88 
 
 1031-17 
 
 
 
 
 
 
 
 -154— 
 
TABLE NO. 73. 
 
 Wrought Iron, Steel, Copper and Brass Plates. 
 
 Birmingham Gauge. 
 
 No. of 
 Gauge. 
 
 0000 
 
 000 
 
 00 
 
 
 
 1 
 
 2 
 3 
 4 
 5 
 6 
 7 
 8 
 9 
 
 10 
 11 
 12 
 13 
 14 
 15 
 16 
 17 
 18 
 19 
 20 
 21 
 22 
 23 
 24 
 25 
 20 
 27 
 28 
 29 
 30 
 31 
 32 
 33 
 34 
 35 
 36 
 
 Thickness, Inches. 
 
 0.454 or Vie fulL- 
 
 0.425 
 
 0.38 or 3/8 fulL-_ 
 
 0.34 orVs full-- 
 
 0.3 
 
 0.284 
 
 0.259 or 1/4 full- 
 
 0.238 
 
 0.22 .-_ 
 
 0.203 orV.5 fulL- 
 
 0.18 orVi6 light 
 
 0.165 or Vu light- 
 
 0.148 or Vr full- 
 
 0.134 
 
 0.12 or Vs light- 
 
 0.109 
 
 0.095 or Vio light 
 
 0.083 
 
 0.072 
 
 0.065 
 
 0.058 
 
 0.049 or V20 light 
 
 0.042 
 
 0.035 
 
 0.032 
 
 0.028 
 
 0.025 orV« 
 
 0.022 
 
 0.02 orVso 
 
 0.018 
 
 0.016 
 
 0.014 
 
 0.013 
 
 0.012 
 
 0.01 or Vioo 
 
 0.009 
 
 0.008 
 
 0.007 
 
 0.005 orVsoo 
 
 0.004 orVsoo 
 
 1.00 inch thick---. 
 
 Weight Per Square Foot, Lbs. 
 
 Iron. 
 
 18.2167 
 17.0531 
 15.2475 
 13.6425 
 12.0375 
 11.3955 
 10.3924 
 9.5497 
 8.8275 
 8.1454 
 7,2225 
 6.6206 
 5.9385 
 5.3767 
 4.8150 
 4.3736 
 3.8119 
 3.3304 
 2.8890 
 2.6081 
 2.3272 
 1.9661 
 1.6852 
 1.4044 
 1.2840 
 1.1235 
 1.0031 
 0,8827 
 0.8025 
 0.7222 
 0.6420 
 0.5617 
 0.5216 
 0.4815 
 0.4012 
 0.3611 
 0.3210 
 0.2809 
 0.2006 
 0.1605 
 
 Steel. 
 
 41.5696 
 
 18.4596 
 17.2805 
 15.4508 
 13.8244 
 12.1980 
 11.5474 
 10.5309 
 9.6771 
 8.9452 
 8.2540 
 7.3188 
 6.7089 
 6.0177 
 5.4484 
 4.8792 
 4.4319 
 3.8627 
 3.3748 
 2.9275 
 2.6429 
 2.3583 
 1.9923 
 1.7077 
 1.4231 
 1.3011 
 1.1385 
 1.0165 
 0.8945 
 0.8132 
 0.7319 
 0.6506 
 0.5692 
 0.5286 
 0.4879 
 0.4066 
 0.3659 
 0.3253 
 0.2846 
 0.2033 
 0.1626 
 
 42.1236 
 
 Copper. 
 
 20.5662 
 19.2525 
 17.2140 
 15.4020 
 13.5900 
 12.8652 
 11.7327 
 10.7814 
 9.9660 
 9.1959 
 8.1540 
 7.4745 
 6.7044 
 6.0702 
 5.4360 
 4.9377 
 4.3035 
 3.7599 
 3.2616 
 2.9445 
 2.6274 
 2.2197 
 1.9026 
 1.5855 
 1.4496 
 1.2684 
 1.1325 
 0.9966 
 0.9060 
 0.8154 
 0.7248 
 0.6342 
 0.5889 
 0.5436 
 0.4530 
 0.4077 
 0.3624 
 0.3171 
 0.2265 
 0.1812 
 
 46.9308 
 
 Brass. 
 
 19.4312 
 18.1900 
 16.2640 
 14.5520 
 12.8400 
 12.1552 
 11.0852 
 10.1864 
 9.4160 
 8.6884 
 7.7040 
 7.0620 
 6.3344 
 5.7352 
 5.1360 
 4.6652 
 4.0660 
 3.5524 
 3.0816 
 2.7820 
 2.4824 
 2.0972 
 1.7976 
 1.4980 
 1.3696 
 1.1984 
 1.0700 
 0.9416 
 0.8560 
 0.7704 
 0.6848 
 0.5992 
 0.5564 
 0.5136 
 0.4280 
 0.3852 
 0.3424 
 0.2996 
 0.2140 
 0.1712 
 
 44.3408 
 
 -155 — 
 
Table no. 74. 
 Weight of Square and Round Iron. 
 
 Side or 
 
 Weight, 
 
 Weight, 
 
 Side or 
 
 Weight, 
 
 Weight, 
 
 Side or 
 
 Weight. 
 
 Weight, 
 
 DlAM. 
 
 Square. 
 
 Round. 
 
 DlAM. 
 
 Square. 
 
 Round. 
 
 DlAM. 
 
 Square. 
 
 Round. 
 
 fe ■ 
 
 .013 
 
 .01 
 
 2 
 
 13.52 
 
 10.616 
 
 5 
 
 84.48 
 
 66.35 
 
 Vb 
 
 .053 
 
 .041 
 
 Yt 
 
 15.263 
 
 11.988 
 
 yi 
 
 93.168 
 
 73.172 
 
 A 
 
 .118 
 
 .093 
 
 y^ 
 
 17.112 
 
 13.44 
 
 % 
 
 102.24 
 
 80.301 
 
 >€ 
 
 .211 
 
 .165 
 
 % 
 
 19.066 
 
 14.975 
 
 % 
 
 111.756 
 
 87.776 
 
 % 
 
 .475 
 
 .373 
 
 % 
 
 21.12 
 
 16.588 
 
 
 
 
 Vz 
 
 .845 
 
 .663 
 
 % 
 
 23.292 
 
 18.293 
 
 6 
 
 121.664 
 
 95.552 
 
 % 
 
 1.32 
 
 1.043 
 
 % 
 
 25.56 
 
 20.076 
 
 K 
 
 132.04 
 
 103. 70 i 
 
 X 
 
 1.901 
 
 1.493 
 
 % 
 
 27.939 
 
 21.944 
 
 % 
 
 142.816 
 
 112.16 
 
 % 
 
 2.588 
 
 2.032 
 
 3 
 
 30.416 
 
 23.888 
 
 K 
 
 154.012 
 
 120.96 
 
 1 
 
 3.38 
 
 2.654 
 
 ^ 
 
 35.704 
 
 28.04 
 
 7 
 
 165.632 
 
 130.048 
 
 ■ M 
 
 4.278 
 
 3.359 
 
 % 
 
 41.408 
 
 32.515 
 
 u 
 
 177.672 
 
 139.544 
 
 K 
 
 5.28 
 
 4.147 
 
 Va 
 
 47.534 
 
 37.332 
 
 y^ 
 
 190.136 
 
 149.328 
 
 X 
 
 6.39 
 
 5.019 
 
 
 54.084 
 
 42.464 
 
 % 
 
 203.024 
 
 159.456 
 
 % 
 
 7.604 
 
 5.972 
 
 4 
 
 
 
 
 
 
 % 
 
 8.926 
 
 7.01 
 
 >4 
 
 61.055 
 
 47.952 
 
 8 
 
 216.336 
 
 169.856 
 
 % 
 
 10 352 
 
 8.128 
 
 % 
 
 68.448 
 
 63.76 
 
 
 
 
 X 
 
 11.883 
 
 9.333 
 
 Ya 
 
 76.264 
 
 59.9 
 
 9 
 
 273.792 
 
 215.04 
 
 Table No. 75, 
 Vulgar Fractions of a Lineal Inch in Decimal Fractions. 
 
 Advancing by Thirty-seconds. 
 
 ■a 
 1 c 
 >> o 
 
 c 
 o 
 
 mals 
 Inch. 
 
 ■a 
 
 1 B 
 >> o 
 
 c 
 o 
 
 71 A 
 
 2 « 
 
 
 
 H 
 
 17 
 
 
 'G c 
 
 1 
 
 _1- 
 
 0.03125 
 
 0.53125 
 
 2 
 
 1 
 
 0.0625 
 
 18 
 
 tV 
 
 0.5625 
 
 8 
 
 4^ 
 
 0.09375 
 
 19 
 
 \% 
 
 0.59375 
 
 4 
 
 * 
 
 0.125 
 
 20 
 
 f 
 
 0.625 
 
 5 
 
 5 
 ■J 2" 
 
 0.15625 
 
 21 
 
 4^ 
 
 0.65625 
 
 6 
 
 tV 
 
 0.1875 
 
 22 
 
 W 
 
 0.6875 
 
 7 
 
 -^^ 
 
 0.21875 
 
 23 
 
 2 3 
 
 3 2 
 
 0.71875 
 
 8 
 
 \ 
 
 0.25 
 
 24 
 
 % 
 
 0.75 
 
 9 
 
 9 
 
 0.28125 
 
 25 
 
 ■1* 
 
 0.78125 
 
 10 
 
 A 
 
 0.3125 
 
 26 
 
 1^ 
 
 0.8125 
 
 11 
 
 -u 
 
 0.34375 
 
 27 
 
 27 
 '3 2' 
 
 0.84375 
 
 12 
 
 % 
 
 0.375 
 
 28 
 
 I 
 
 0.875 
 
 13 
 
 1 3 
 
 ■3 2' 
 
 0.40625 
 
 29 
 
 n 
 
 0.90625 
 
 14 
 
 tV 
 
 0.4375 
 
 30 
 
 \% 
 
 0.9375 
 
 15 
 
 1 5 
 '3 2' 
 
 0.46875 
 
 31 
 
 •30- 
 
 0.96875 
 
 16 
 
 h 
 
 0.5 
 
 32 
 
 1 
 
 1.000 
 
 Advancing by Odd Sixty-fourths. 
 
 1 
 o 
 
 5 
 7 
 9 
 11 
 13 
 15 
 17 
 19 
 21 
 23 
 25 
 27 
 29 
 31 
 
 Decimals 
 of an Inch. 
 
 33 
 
 0.015625 
 
 0.04687 
 
 35 
 
 0.078125 
 
 37 
 
 0.109375 
 
 39 
 
 0.140625 
 
 41 
 
 0.171875 
 
 43 
 
 203125 
 
 45 
 
 0.234375 
 
 47 
 
 0.265625 
 
 49 
 
 0.296875 
 
 51 
 
 0.328125 
 
 53 
 
 0.359375 
 
 55 
 
 0.390625 
 
 57 
 
 0.421875 
 
 59 
 
 0.453125 
 
 61 
 
 0.484375 
 
 63 
 
 0.515625 
 0.546875 
 0.578125 
 0.609375 
 0.640625 
 0.671875 
 0.703125 
 0.734375 
 0.765625 
 0.796875 
 0.828125 
 0.859375 
 0.890625 
 0.921875 
 0.953125 
 0.984375 
 
 —156- 
 
Table No. 7G. 
 Lineal Inches in Decimal Fractions of a Lineal Foot. 
 
 Lineal 
 Inches. 
 
 Lineal Foot. 
 
 Lineal 
 Inches. 
 
 Lineal Foot. 
 
 Lineal 
 Inches. 
 
 Lineal Foot. 
 
 1 
 
 0.001302083 
 
 ^l 
 
 0.15625 
 
 n 
 
 0.5416 
 
 1 
 15? 
 
 0.00260416 
 
 2 
 
 0.1666 
 
 C| 
 
 0.5625 
 
 1 
 
 0.0052083 
 
 9 1 
 
 ^ 8 
 
 0.177083 
 
 i 
 
 0.5833 
 
 1 
 8 
 
 0.010416 
 
 2 1 
 
 -" 4 
 
 0.1875 
 
 7i 
 
 0.60416 
 
 3 
 
 0.015625 
 
 O 3 
 
 -' 8 
 
 0.197916 
 
 7|- 
 
 0.625 
 
 1- 
 
 0.02083 
 
 2| 
 
 0.2083 
 
 7| 
 
 0.64583 
 
 t\ 
 
 0.0260416 
 
 2g 
 
 0.21875 
 
 8 
 
 0.66667 
 
 1 
 
 0.03125 
 
 2| 
 
 0.22916 
 
 ^h 
 
 0.6875 
 
 7 
 
 0.0364583 
 
 2§ 
 
 0.239583 
 
 8i 
 
 0.7088 
 
 1 
 
 0.0416 
 
 3 
 
 0.25 
 
 8| 
 
 0.72916 
 
 t\ 
 
 0.046875 
 
 3i- 
 
 0.27083 
 
 9 
 
 0.75 
 
 1 
 
 0.052083 
 
 3^ 
 
 0.2916 
 
 n 
 
 0.77083 
 
 i^ 
 
 0.0572916 
 
 C> 3 
 '^ 4 
 
 0.3125 
 
 n 
 
 0.7916 
 
 3 
 
 4 
 
 0.0625 
 
 4 
 
 0.33333 
 
 9|- 
 
 0.8125 
 
 it 
 
 0.0677083 
 
 4i 
 
 0.35416 
 
 10 
 
 0.83333 
 
 1 
 
 0.072916 
 
 4i 
 
 0.375 
 
 10 i- 
 
 0.85416 
 
 1 5 
 
 0.078125 
 
 4| 
 
 0.39583 
 
 10\ 
 
 0.875 
 
 1 
 
 0.0833 
 
 5 
 
 0.4166 
 
 10-1 
 
 0.89583 
 
 u 
 
 0.09375 
 
 ^4^ 
 
 0.4375 
 
 11 
 
 0.9166 
 
 u 
 
 0.10416 
 
 H 
 
 0.4583 
 
 lU 
 
 0.9375 
 
 If 
 
 0.114583 
 
 5f 
 
 0.47916 
 
 lU 
 
 0.9583 
 
 u- 
 
 0.125 
 
 6 
 
 0.5 
 
 11 1- 
 
 0.97916 
 
 1 5 
 
 0.135416 
 
 n 
 
 0.52083 
 
 12 
 
 1.000 
 
 11 
 
 0.14583 
 
 1 
 
 
 
 
 4 
 
 i 
 
 
 i 
 
 
 Thejij^st cost of a boiler is a fixed quantity. Tlie cost of operation is one 
 continuing during the life of the boiler. Given the relative cost of tubular 
 and water-tube boilers, and the cost of fuel, it is a simple arithmetical calcu- 
 lation to determine what percentage of economy there must be in water-tube 
 boilers in order to earn back their extra first cost. Of course no one who 
 understands the subject, now doubts that there is some advantage in water- 
 tube boilers in point of economy of operation and repairs. Take this per- 
 centage of economy at the minimum — say only 10% — and see how short a 
 time it takes to amount to more than the cost of the boiler. It will surprise 
 you. 
 
 —157— 
 
TABLE NO. 77. 
 
 Square Inches in Decimal Fractions of a Square Foot. 
 
 Square 
 Inches. 
 
 Square 
 Foot. 
 
 Square 
 Inches. 
 
 Square 
 Foot. 
 
 Square 
 Inches. 
 
 Square 
 Foot. 
 
 Square 
 Inches. 
 
 Square 
 Foot. 
 
 0.10 
 
 0.0006944 
 
 24.0 
 
 0.16666 
 
 65.0 
 
 0.45138 
 
 105.0 
 
 0.72916 
 
 0.15 
 
 0.0010416 
 
 25.0 
 
 0.17361 
 
 66.0 
 
 0.45833 
 
 106.0 
 
 0.73611 
 
 0.20 
 
 0.001388 
 
 26.0 
 
 0.18055 
 
 67.0 
 
 0.46527 
 
 107.0 
 
 0.74305 
 
 0.25 
 
 0.0017361 
 
 27.0 
 
 0.18750 
 
 68.0 
 
 0.47222 
 
 108.0 
 
 0.75000 
 
 0.30 
 
 0.002083 
 
 28.0 
 
 0.19444 
 
 69.0 
 
 0.47916 1 
 
 109.0 
 
 0.75694 
 
 0.35 
 
 0.0024305 
 
 29.0 
 
 0.20138 
 
 70.0 
 
 0.48611 
 
 110.0 
 
 0.76388 
 
 0.40 
 
 0.002777 
 
 30.0 
 
 0.20833 
 
 71.0 
 
 0.49306 
 
 111.0 
 
 0.77083 
 
 0.45 
 
 0.00311249 
 
 31.0 
 
 C.21527 
 
 72.0 
 
 0.50000 
 
 112.0 
 
 0.77777 
 
 0.50 
 
 0.003472 
 
 32.0 
 
 0.22222 
 
 73.0 
 
 0.50694 
 
 113.0 
 
 0.78472 
 
 0.55 
 
 0.0038194 
 
 33.0 
 
 0.22916 
 
 74.0 
 
 0.51388 
 
 114.0 
 
 0.79166 
 
 0.60 
 
 0.004166 
 
 34.0 
 
 0.23611 
 
 75.0 
 
 0.52083 
 
 116.0 
 
 0.79861 
 
 0.65 
 
 0.0045138 
 
 35.0 
 
 0.24305 
 
 76.0 
 
 0.52777 
 
 116.0 
 
 0.80555 
 
 0.70 
 
 0.004861 
 
 36.0 
 
 0.25000 
 
 77.0 
 
 0.53472 
 
 117.0 
 
 0.81249 
 
 0.75 
 
 0.0052083 
 
 37.0 
 
 0.25694 
 
 78.0 
 
 0.54166 
 
 118.0 
 
 0.81944 
 
 0.80 
 
 0.005555 
 
 38.0 
 
 0.26388 
 
 79.0 
 
 0.54861 
 
 119.0 
 
 0.82638 
 
 0.85 
 
 0.0059027 
 
 39.0 
 
 0.27083 
 
 80.0 
 
 0.55555 
 
 120.0 
 
 0.83333 
 
 0.90 
 
 0.006250 
 
 40.0 
 
 0.27777 
 
 81.0 
 
 0.56249 
 
 121.0 
 
 0.84027 
 
 0.95 
 
 0.0065972 
 
 41.0 
 
 0.28472 
 
 82.0 
 
 0.56944 
 
 122.0 
 
 84722 
 
 1.0 
 
 0.006944 
 
 42.0 
 
 0.29166 
 
 83.0 
 
 0.57638 
 
 123.0 
 
 0.85416 
 
 2.0 
 
 0.01388 
 
 43.0 
 
 0.29861 
 
 84.0 
 
 0.58333 
 
 124.0 
 
 0.86111 
 
 3.0 
 
 0.02083 
 
 44.0 
 
 0.30555 
 
 85.0 
 
 0.59027 
 
 125.0 
 
 0.86805 
 
 4.0 
 
 0.02777 
 
 45.0 
 
 0.31249 
 
 86.0 
 
 0.59722 
 
 126.0 
 
 0.87500 
 
 6.0 
 
 0.03472 
 
 46.0 
 
 0.31944 
 
 87.0 
 
 0.60416 
 
 127.0 
 
 0.88194 
 
 6.0 
 
 0.04166 
 
 47.0 
 
 0.32638 
 
 88.0 
 
 0.61111 
 
 128.0 
 
 0.88888 
 
 7.0 
 
 0.04861 
 
 48.0 
 
 0.33333 
 
 89.0 
 
 0.61805 
 
 129.0 
 
 0.89583 
 
 8.0 
 
 0.05555 
 
 49.0 
 
 0.34027 
 
 90.0 
 
 0.62500 
 
 130.0 
 
 0.90277 
 
 9.0 
 
 0.06250 
 
 50.0 
 
 34722 
 
 91.0 
 
 0.63194 
 
 131.0 
 
 0.90972 
 
 10.0 
 
 0.06944 
 
 61.0 
 
 0.35416 
 
 92.0 
 
 0.63888 
 
 132.0 
 
 0.91666 
 
 11.0 
 
 0.07638 
 
 52.0 
 
 0.36111 
 
 93.0 
 
 0.64583 
 
 133.0 
 
 0.92361 
 
 12.0 
 
 0.08333 
 
 53.0 
 
 0.36805 
 
 94.0 
 
 0.65277 
 
 134.0 
 
 0.93065 
 
 13.0 
 
 0.09027 
 
 54.0 
 
 0.37500 
 
 95.0 
 
 0.65972 
 
 135.0 
 
 0.93750 
 
 14.0 
 
 0.09722 
 
 55.0 
 
 0.38194 
 
 96.0 
 
 0.66666 
 
 136.0 
 
 0.94444 
 
 15.0 
 
 0.10416 
 
 56.0 
 
 0.38888 
 
 97.0 
 
 0.67361 
 
 137.0 
 
 0.95138 
 
 16.0 
 
 0.11111 
 
 57.0 
 
 0.39583 
 
 98.0 
 
 0.68055 
 
 138.0 
 
 0.95833 
 
 17.0 
 
 0.11805 
 
 68.0 
 
 0.40277 
 
 99.0 
 
 0.68750 
 
 139.0 
 
 0.96627 
 
 18.0 
 
 0.12500 
 
 59.0 
 
 0.40972 
 
 100.0 
 
 0.69444 , 
 
 140.0 
 
 0.97222 
 
 19.0 
 
 0.13194 
 
 60.0 
 
 0.41666 
 
 101.0 
 
 0.70138 
 
 141.0 
 
 0.97916 
 
 20.0 
 
 0.13888 
 
 61.0 
 
 0.42361 
 
 102.0 
 
 0.70833 
 
 142.0 
 
 0.98611 
 
 21.0 
 
 0.14583 
 
 62.0 
 
 0.43055 
 
 103.0 
 
 0.71527 
 
 143.0 
 
 0.99305 
 
 22.0 
 
 0.15277 
 
 63.0 
 
 0.43750 
 
 104.0 
 
 0.72222 
 
 144.0 
 
 1.0000 
 
 23.0 
 
 0.15972 
 
 64.0 
 
 0.44444 
 
 
 
 
 
 -158— 
 
Table No. 78. 
 Decimal Fractions of a Square Foot in Square Indies. 
 
 Square 
 Foot. 
 
 Square 
 Inches. 
 
 Square 
 Foot. 
 
 Square 
 Inches. 
 
 Square 
 Foot. 
 
 Square 
 Inches. 
 
 Square 
 Foot. 
 
 Square 
 Inches. 
 
 0.01 
 
 1.44 
 
 0.26 
 
 37.4 
 
 0.51 
 
 73.4 
 
 0.76 
 
 109.4 
 
 0.02 
 
 2.88 
 
 0.27 
 
 38.9 
 
 0.52 
 
 74.9 
 
 0.77 
 
 110.9 
 
 0.03 
 
 4.32 
 
 0.28 
 
 40.3 
 
 0.53 
 
 76.3 
 
 0.78 
 
 112.3 
 
 0.04 
 
 5.76 
 
 0.29 
 
 41.8 
 
 0.54 
 
 77.8 
 
 0.79 
 
 113.8 
 
 0.05 
 
 7.20 
 
 0.30 
 
 43.2 
 
 0.55 
 
 79.2 
 
 0.80 
 
 115.2 
 
 0.06 
 
 8.64 
 
 0.31 
 
 44.6 
 
 0.56 
 
 80.6 
 
 0.81 
 
 116.6 
 
 0.07 
 
 10.1 
 
 0.32 
 
 46.1 
 
 0.57 
 
 82.1 
 
 0.82 
 
 118.1 
 
 0.08 
 
 11.5 
 
 0.33 
 
 47.5 
 
 0.58 
 
 83.5 
 
 0.83 
 
 119.5 
 
 0.09 
 
 13.0 i 
 
 0.34 
 
 49.0 
 
 0.59 
 
 85.0 
 
 0.84 
 
 121.0 
 
 0.10 
 
 14.4 
 
 0.35 
 
 50.4 
 
 0.60 
 
 86.4 
 
 0.85 
 
 122.4 
 
 0.11 
 
 15.8 
 
 0.36 
 
 51.8 
 
 0.61 
 
 87.8 
 
 0.86 
 
 123.8 
 
 0.12 
 
 17.3 
 
 0.37 
 
 53.3 
 
 0.62 
 
 89.3 
 
 0.87 
 
 125.3 
 
 0.13 
 
 18.7 
 
 0.38 
 
 54.7 
 
 0.63 
 
 90.7 
 
 0.88 
 
 126.7 
 
 0.14 
 
 20.2 
 
 0.39 
 
 56.2 
 
 0.64 
 
 92.2 
 
 0.89 
 
 128.2 
 
 0.15 
 
 21.6 
 
 0.40 
 
 57.6 
 
 0.65 
 
 93.6 
 
 0.90 
 
 129.6 
 
 0.16 
 
 23.0 
 
 0.41 
 
 58.0 
 
 0.66 
 
 95.0 
 
 0.91 
 
 131.0 
 
 0.17 
 
 24.5 
 
 0.42 
 
 60.5 
 
 0.67 
 
 96.5 
 
 0.92 
 
 132.5 
 
 0.18 
 
 25.9 
 
 0.43 
 
 61.9 
 
 0.68 
 
 97.9 
 
 0.93 
 
 133.9 
 
 0.19 
 
 27.4 
 
 0.44 
 
 63.4 
 
 0.69 
 
 99.4 
 
 0.94 
 
 135.4 
 
 0.20 
 
 28.8 
 
 ' 0.45 
 
 64.8 
 
 0.70 
 
 100.8 
 
 0.95 
 
 136.8 
 
 0.21 
 
 30.2 
 
 0.46 
 
 66.2 
 
 0.71 
 
 102.2 
 
 0.96 
 
 138.2 
 
 0.22 
 
 31.7 " 
 
 0.47 
 
 67.7 
 
 0.72 
 
 103.7 
 
 0.97 
 
 139.7 
 
 0.23 
 
 33.1 
 
 0.48 
 
 69.1 
 
 0.73 
 
 105.1 
 
 0.98 
 
 141.1 
 
 0.24 
 
 34.6 
 
 0.49 
 
 70.6 
 
 0.74 
 
 106.6 
 
 0.99 
 
 142.6 
 
 0.25 
 
 36.0 
 
 0.50 
 
 72.0 
 
 0.75 
 
 108.0 
 
 1.00 
 
 144.0 
 
 How many large modern boiler plants are now constructed with old 
 style flue and tubular boilers — boilers in which circulation is in spite of, and 
 not because of, their design and construction ? Among the big new installa- 
 tions there are twenty water-tube plants now to every one of the old style. 
 Yet many small boiler users still fail to grasp the fact that the economy of 
 wa+*^r-tuhe boilers is "a condition " and not "a theory." 
 
 —159— 
 
Table No. 79. 
 French Measures of Length with U. S. Equivalents. 
 
 10 millimetres 
 
 10 centimetres 
 
 10 decimetres "1 
 
 100 centimetres > 
 
 1000 millimetres J 
 
 10 metres 
 
 10 decametres 
 
 10 hectometres 
 
 10 kilometres 
 
 
 Metres. 
 
 II. S. Equivalents. 
 
 1 millimetre 
 
 1 centimetre 
 
 0.001 
 
 0.01 
 
 0.1 
 
 1.0 
 
 10.0 
 
 100.0 
 
 1000.0 
 
 10000.0 
 
 0.03937 inch. 
 3937 inch 
 
 1 decimetre 
 
 1 METRE 
 
 1 decametre 
 
 I hectometre 
 
 1 KILOMETRE 
 
 3.93704 inches. 
 
 f 39.3704 inches. 
 1 3.2809 feet. 
 
 32.8087 feet. 
 328.0869 feet. 
 3280.869 feet 
 
 1 myriametre 
 
 6.21377 miles. 
 
 TABLE No. 80. 
 
 French Measures of Surface with U. S. Equivalents. 
 
 1 ?q, 
 1 sq, 
 1 sq 
 
 1 sq 
 
 1 sq, 
 
 1 sq. 
 
 100 sq. hectometres 1 sq. 
 
 100 sq. kilometres il sq. 
 
 100 sq. millimetres 
 
 100 sq. centimetres 
 
 100 sq. decimetres 1 
 
 10000 sq. centimetres-- J 
 
 100 sq. metres 
 
 100 sq. decametres- 
 
 millimetre - 
 centimeter- 
 decimetre-- 
 
 METRE--- 
 decametre - 
 hectometre - 
 kilometre-- 
 myriametre 
 
 Square Metres 
 
 0.000001 
 
 0.0001 
 
 0.01 
 
 1.0 
 100.0 
 10,000.0 
 1,000,000.0 
 
 ioo,ooo,ooo.r 
 
 U. S. Equivalents. 
 
 0.00155 sq. inches. 
 
 0.155 sq. inches. 
 
 15.5003 sq. inches. 
 
 10.7641 sq. feet. 
 
 1.1960 sq. yards, 
 f 1076.41 sq. feet. 
 1 119.601 sq. yards, 
 f 11960.11 sq. yards. 
 \ 2.4711 acres, 
 f 1196014 sq. yards. 
 10.38611 sq. miles. 
 
 38.611 sq. miles. 
 
 TABLE No. 81. 
 
 French Measures of Weight with U. S. Avoirdupois 
 
 Equivalents. 
 
 10 milligrammes 
 
 10 centigrammes 
 
 10 decigrammes 
 
 10 grammes _____ 
 
 10 decagrammes 
 
 10 hectagrammes 
 
 IlO kilogrammes 
 
 10 quintals "\ 
 
 1000 kilogrammes / 
 
 1 milligramme _- 
 1 centigramme -_ 
 1 decigramme — 
 1 GRAMME 
 
 1 decagramme--- 
 
 1 hectagramme -- 
 
 1 kilogramme — 
 L metric quintal - 
 
 1 millier or tonne 
 
 Grammes. 
 
 0.001 
 0.01 
 0.1 
 1.0 
 
 10.0 
 
 100.0 
 1000.0 
 
 U. S. Equivalents. 
 
 0.0154 grains. 
 0.1543 grains. 
 1.5432 grains. 
 15.4323 grains. 
 154.3235 grains. 
 0.3527 ounces. 
 1643.2349 grains. 
 3.5274 ounces. 
 2.2046 pounds. 
 220.4621 pounds. 
 2204.6212 pounds. 
 19.6841 cwt. 
 0.9842 tons. 
 
 -160— 
 
Table No. 8^.. 
 French Measures of Volume with U. S. Equivalents. 
 
 1000 cu. millimetres 
 1000 cu. centimetres 
 
 1000 cu. decimetres- 
 1000 cu. metres 
 
 1 cu. millimetre 
 1 cu. centimetre 
 
 1 cu. decimetre 
 
 1 cu. METRE -- 
 1 cu. decametre 
 
 Cubic Metres. 
 
 0.000000001 
 0.000001 
 
 0.001 
 
 1.0 
 
 1000 
 
 U. S Equivalents. 
 
 O.OOOOBl cu. inches. 
 
 0.061025 cu. inches. 
 / 61.02524 cu. inches. 
 I 0.0353156 cu. feet. 
 r35.3156cu.feet. 
 1 1.308 cu. yards. 
 
 1308.0 cu. yards. 
 
 TABLE NO. S3. 
 
 French Liquid Measure with U. S. Equivalents. 
 
 
 
 Litres. 
 
 U. S. Equivalents. 
 
 10 centilitres 
 
 r 1 centilitre \ 
 1 10 cu. centimetres / "" 
 
 1 decilitre -- - - 
 
 0.01 
 
 0.1 
 
 1.0 
 10.0 
 
 ion 
 
 r 0.61025 CU. inches. 
 
 \ 0.0845 gills. 
 
 f 6.1025 cu. inches. 
 
 10.2114 pints. 
 
 f 61.02524 cu. inches. 
 
 10.2642 gallons, 
 
 2.6418 gallons. 
 
 26.418 gallons. 
 
 10 decilitres 
 
 10 litres 
 
 r 1 LITRE 1 
 1 1 cu. decimetre / 
 1 decalitre 
 
 1 hectolitre 
 
 10 decalitres 
 
 ».^ 
 
 
 
 I 
 
 THE FAMOUS SCHICHAU ENGINE. 
 
 Now owned by the C. C. Washburn Flouring Mills Co. 
 
 Steam supplied by Heine Boilers. 
 
 —161— 
 

 Number of 
 Threads 
 
 per Inch of 
 Screw. 
 
 T-<MHN-b<l-*M 
 
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 No. 84. 
 
 d Water 
 
 1 -5 
 
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 <J 
 
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Bowling Green Office Building, 
 
 NEW YORK. 
 
 Equipped with 750 H. P. Heine Safety Boilers. 
 
LIST OF HEINE BOILER PLANTS. 
 
 HOTELS, OFFICES AND PUBLIC BUILDINGS. 
 
 National Guard Armory., St. L,ouis 1 Boiler, 40 H. P. 
 
 Harmonie Club, St. Louis 1 " 15 
 
 Shaw Building, St. Louis 1 " 50 
 
 Mitchell Building, St. Louis 1 " 45 
 
 Missouri State University, Columbia, Mo 2 " 120 
 
 St. Louis Exposition, St. Louis 4 " 1000 
 
 House of Refuge, St. Louis 2 " 110 
 
 Montesano Hotel, St. Louis 1 " 15 
 
 Palace Hotel, San Francisco, Cal 4 " 260 
 
 McVicker's Theatre, Chicago, 111 2 " 260 
 
 Roe Building, St. Louis , 2 " 250 
 
 Good Samaritan Hospital, St. Louis 1 " 20 
 
 Lake View School House, Chicago, 111 2 " 75 
 
 State University, Madison, Wis .7. 2 " 110 
 
 Minneapolis Industrial Exposition, Minneapolis, Minn 4 " 1000 
 
 Centropolis Hotel, Kansas City 2 " 150 
 
 Inter-State Industrial Exposition, Chicago, 111 1 " 250 
 
 University of Denver, Denver, Colo., first order 1 " 90 
 
 University of Denver, Denver, Colo., second order 1 " 200 
 
 Boston Heating Co., Boston, Mass., first order 10 " 1000 
 
 Boston Heating Co., Boston, Mass., second order 2 " 200 
 
 San Jose Insane Asylum, San Jose, Cal 2 " 220 
 
 Cincinnati Exposition, Cincinnati, Ohio 2 " 400 
 
 Denver Republican, Denver, Colo 1 " 80 
 
 Cathedral of St. John, Denver, Colo 1 " 80 
 
 Railroad Building, Denver, Colo 1 " 110 
 
 Arkansas State Lunatic Asylum, Little Rock, Ark 2 " 150 
 
 Western Pennsylvania Exposition, Pittsburg, Pa 2 " 500 
 
 Houser Building, St. Louis 2 " 240 
 
 Hospital for the Insane, Fergus Falls, Minn 1 " 120 
 
 Southern Illinois Penitentiary, Chester, 111 2 " 600 
 
 Insane Asylum, Agnew, Cal 2 " 220 
 
 Railroad Building, Denver, Colo., second order 1 " 110 
 
 Court House, Evansville, Ind 2 " 190 
 
 Wm. Kirkup & Son, Cincinnati, Ohio 2 " 220 
 
 Pabst Opera House, Milwaukee, Wis 2 " 240 
 
 Arapahoe County Jail, Denver, Colo 3 " 360 
 
 C. D. McPhee, Denver, Colo 2 " 150 
 
 Broadway Theatre, Denver, Colo., first order 2 " 240 
 
 Boatmen's Bank Building, St. Louis 2 " 240 
 
 Broadway Theatre, Denver, Colo., second order 1 " 120 
 
 Samuel Cupples Real Estate Co., St. Louis 2 " 740 
 
 The Neave Building Co., Cincinnati, Ohio 2 " 240 
 
 First National Bank, Duluth, Minn 2 " 80 
 
 John Shillito Co., Cincinnati, Ohio, first order 1 " 250 
 
 John Shillito Co., Cincinnati, Ohio, second order 2 " 400 
 
 John M. Smyth, Chicago, 111 2 " 500; 
 
 University of Michigan, Ann Arbor, Mich 2 " 300 
 
 Hospital for the Insane, Fergus Falls, Minn., second order 1 " 120 
 
 Palace Hotel, San Francisco, Cal., second order 3 " 525 
 
 Royal Victoria Hospital, Montreal, Can 2 " 160 
 
 R. H. Macy & Co., New York 3 " 600 
 
 Henry C. Brown, Palace Hotel, Denver, Colo 4 " 520 
 
 Jas. G. Fair Building, San Francisco, Cal 1 " 175 
 
 Hospital for the Insane, Fergus Falls, Minn., third order 1 " 120 
 
 Jackson County Court House, Kansas City .-.. 3 " 360 
 
 Equitable Building, Des Moines, Iowa 2 " 300 
 
 Freehold Building, Toronto, Can 1 " 120 
 
 Confederation Building, Toronto, Can 2 " 200 
 
 John Doty Engine Co., Toronto, Can 1 " HO 
 
 Athletic Club Building, Chicago, 111 2 " 300 
 
 World's Columbian Exposition, Chicago, 111 '8 " 3000 
 
 Windsor Hotel, Montreal, Can 1 " 150 
 
 Betz Building, Philadelphia, Pa 3 " 500 
 
 Mercantile Club, St. Louis 2 " 300 
 
 The Johnson Building, Cincinnati, Ohio 2 " 240 
 
 The First National Bank, Pittsburg, Pa 2 " 100 
 
 Jackson County Court House, Kansas City, second order 1 " 120 
 
 Emma Spreckels Building, San Francisco, Cal 2 " 150 
 
 Mallinckrodt Building, St. Louis 2 " 300 
 
 -166— 
 
World's Columbian Exposition, Chicaj^o, 111., second order 4 Boiler, 1500 H.P. 
 
 Odd Fellows' Temple, Cincinnati, Ohio 3 " 450 '' 
 
 Occidental Hotel, San Francisco, Cal 2 " 150 
 
 New Planters' House, St. Louis 2 " 600 
 
 Young Men's Christian Association Building, Chicago 2 " 500 " 
 
 Gruenewald Building, New Orleans 2 " 100 
 
 Hospital for the Insane, Fergus Falls, Minn., fourth order 1 " 120 
 
 Pennsylvania State College, State College, Pa 1 " 150 
 
 Hotel Majestic, New York City 4 " 1000 || 
 
 Carnegie Steel Co., Pittsburg, Pa., first order 2 " 250 
 
 Carnegie Steel Co., Pittsburg, Pa., second order 1 " 255 
 
 Central Park Apartment Building, New York City 2 " 500 
 
 California Midwinter International Exposition, San Francisco .. S " 3000 
 
 City and County Building, Salt L^ke City, Utah 3 " 225 '| 
 
 Southern Illinois Penitentiary, Chester, 111., second order 1 " 300 
 
 La Banque du Peuple, Montreal, Can 2 " 125 
 
 St. Vincent's Institute, Normandy, Mo 2 " 400 " 
 
 Marquette Building, Chicago, 111 4 " 1000 |' 
 
 Merchants' Exchange, St. Louis 3 " 360 
 
 Fergus Falls State Hospital, Fergus Falls, Minn., fifth order.... 1 " 120 
 
 City of Chicago Electric Light Station, Chicago, 111 3 " 1500 " 
 
 Bennett & Wright, Parliament Building, Victoria, B. C 2 " ^^^ \[ 
 
 New Planters' House, St. Louis, second order 1 " 200 
 
 Equitable Building, Denver, Colo 3 " 750 
 
 Samuel Cupples Real Estate Co., St. Louis, second order 1 " 150 |' 
 
 Jackson Bros. Building, Pittsburg, Pa 2 " 200 
 
 Maine State College, Orona, Me 1 " 85 
 
 Cornell University, Ithaca, N. Y 1 " 100 " 
 
 First National Bank Building, Chicago, 111 2 " 408 " 
 
 North Sub-district School, Pittsburg, Pa 2 " 130 |' 
 
 University of Missouri, Columbia, Mo 1 " 200 
 
 Winnebago Building, Chicago, 111 3 " 375 |' 
 
 Bowling Green Building, New York 3 " 540 
 
 Central Kentuckj' Lunatic Asylum, Lakeland, Ky 1 " 300 
 
 Y. M. C. A. Building, St. Louis 1 " 120 |' 
 
 First National Bank Building, Pittsburg, Pa 1 " 150 |' 
 
 Colorado Telephone Co., Denver, Colo 1 " 60 
 
 W. U. Telegraph Co. Building, Chicago, 111 1 " ^50 || 
 
 Lindell Real Estate Co., St. Louis 3 " 450 || 
 
 Fergus Falls State Hospital, Fergus Falls, Minn., sixth order.. 1 " 120 
 
 New City Hall, St. Louis 2 " ^^^ [[ 
 
 Uihlein Building, Milwaukee, Wis 2 " 360 
 
 Windsor Hotel, New York 2 " 356 '' 
 
 C. S. Movev Mercantile Co., Denver, Colo 2 " 120 " 
 
 Y. M. C. A^, Philadelphia, Pa 2 " 154 ^^ 
 
 Massillon State Hospital, Massillon, Ohio 4 " 1000 '| 
 
 Davis Building, St. Louis, Mo 4 " 600 
 
 Hotel Chamberlain, Old Point Comfort, Va 1 " 302 '| 
 
 Quincy House, Boston, Mass 1 " 210 '| 
 
 Fullerton Building, St. Louis, Mo 2 " ^^^ \, 
 
 Arkansas State Lunatic Asylum, Little Rock, Ark., second order, 1 " ^'^ ,i 
 
 California Hotel, San Francisco 1 " 140 
 
 Hospital St. Jean de Dieu Insane Asylum, Quebec 1 " ^^ ,, 
 
 Municipal and County Buildings, Toronto, Ont 4 " 700 '| 
 
 Forresters' Temple, Toronto 2 " 240 
 
 IRON AND STEEL MANUFACTURERS. 
 
 St. Louis Stamping Co., St. Louis , 1 Boiler, 40 H.P. 
 
 Troy Steel and Iron Co., Troy, N. Y., first order 2 " ^'^^ [[ 
 
 Troy Steel and Iron Co., Troy, N. Y., second order 8 " 2560 
 
 Risdon Iron Works, San Francisco, Cal 3 " 600 
 
 Tudor Iron Works, St. Louis 2 " 500 " 
 
 Scherpe & Koken, St. Louis 1 " 30 " 
 
 Shoenberger & Co., Pittsburg, Pa 1 " 250 " 
 
 Oliver Bros. & Phillips, Pittsburg, Pa., first order 2 " 500 " 
 
 Edgar Thompson Steel Works, Braddock, Pa 2 " 500 
 
 Union Steel Co., Chicago, 111 2 " 500 || 
 
 Jas. P. Witherow, Pittsburg, Pa 2 " 250 
 
 Troy Steel and Iron Co., Troy, N. Y., third order 1 " 125 " 
 
 Belleville Nail Co., Belleville, 111 5 || 1250 || 
 
 Racine Hardware Co., Racine, Wis 1 " 150 
 
 Robt. Hare Powel's Sons, Saxton, Pa 3 |'^ 750 j| 
 
 Valentine Ore Land Association, Belief onte. Pa 3 " 375 || 
 
 Troy Steel and Iron Co., Troy, N. Y., fourth order 2 " 180 
 
 —167— 
 
Chicago Steel Works, Chicago, 111 1 Boiler 
 
 Troy Steel and Iron Co., Troy, N. Y., fifth order 3 
 
 North Branch Steel Co., Danville, Pa 4 
 
 Oliver Bros. & Phillips, Pittsburg, Pa., second order 1 " 
 
 Henry Disston & Sons, Philadelphia, Pa., first order 1 " 
 
 Springfield Iron Co., Springfield, 111 3 " 
 
 H. R. Worthington, Brooklyn, N. Y 2 
 
 Henry Disston & Sons, Philadelphia, Pa., second order 3 " 
 
 Oliver Bros. & Phillips, Pittsburg, Pa., third order 1 " 
 
 Missouri Malleable Iron Co., St. Louis 1 " 
 
 Helmbacher Forge and Rolling Mill Co., St. Louis 1 " 
 
 Chester Rolling Mills, Chester, Pa 5 " 
 
 Van Zile, McCormack & Co., Albany, N. Y 1 
 
 Troy Steel and Iron Co., Troy, N. Y., sixth order 2 " 
 
 Muskegon Iron and Steel Co., Muskegon, Mich 1 " 
 
 Muskegon Iron and Steel Co., Muskegon, Mich., second order, 1 " 
 
 Monterey Foundry Co., Monterey, Mex 1 
 
 Van Zile, McCormack & Co., Albany, N. Y., second order 1 " 
 
 Kilmer Mfg. Co., Newburgh, N. Y 5 
 
 The Johnson Co., Johnstown, Pa 2 " 
 
 Strom Mfg. Co., Chicago, 111 1 
 
 Keystone Rolling Mill Co., Pittsburg, Pa 1 " 
 
 St. Louis Shovel Co., St. Louis 1 " 
 
 U. S. Iron and Tin Plate Mfg. Co., Demmler, Pa 1 
 
 Shoenberger, Speer & Co., Pittsburg, Pa 1 " 
 
 Missouri Malleable Iron Co., St. Louis, second order 2 " 
 
 Elba Iron Works, Pittsburg, Pa 1 
 
 Keystone Rolling Mill Co., Pittsburg, Pa., second order 1 " 
 
 Scherpe & Koken Arch. Iron Works Co., St. Louis, 2d order .. 2 " 
 
 The Johnson Co., Johnstown, Pa., second order .. 2 " 
 
 Addyston Pipe and Steel Co., Addyston, Ohio 1 
 
 Helmbacher Forge & Rolling Mill Co., St. Louis, second order, 1 
 
 U. S. Iron and Tin Plate Mfg. Co., Demmler, Pa., second order, 1 
 
 Tudor Iron Works, St. Louis, second order 2 " 
 
 Illinois Steel Co., Joliet, 111 4 
 
 U. S. Iron and Tin Plate Mfg. Co., Demmler, Pa., third order.. 4 
 
 Illinois Steel Co., Chicago, 111., second order 4 " 
 
 S. T. Williams & Co., Muscatine, Iowa 1 
 
 Jas. McKinney & Son, Albany, N. Y 1 " 
 
 Williams Rolling Mills, Muscatine, Iowa, second order 1 " 
 
 Tudor Iron Works, East St. Louis, third order 2 " 
 
 Session's Foundry Co., Bristol, Conn 3 " 
 
 Illinois Steel Co., Joliet, 111., third order 2 
 
 Illinois Steel Co., Joliet, 111., fourth order 4 
 
 Jones & Laughlin, L't'd, Pittsburg, Pa 1 " 
 
 Schoenberger Steel Co., Pittsbiirg, Pa., second order 1 " 
 
 Koken Iron Works, St. Louis, second order 1 " 
 
 Inland Steel Co., Chicago Heights, 111 1 " 
 
 ARTIFICIAL ICE AND REFRIGERATOR COMPANIES 
 
 Texarkana Ice Co., Texarkana, Ark 2 Boiler, 
 
 Bohlen-Huse Machine and Lake Ice Co., Memphis, Tenn 1 " 
 
 Griesedieck Artificial Ice Co., St. Louis, first order 1 " 
 
 H. H. Bodeman, St. Louis 1 " 
 
 Griesedieck Artificial Ice Co., St. Louis, second order 1 " 
 
 Springfield Ice and Refrigerator Co., Springfield, Mo 1 " 
 
 H. Henke & Co., Houston, Tex 1 " 
 
 Union Ice Mfg. Co., Pittsburg, Pa 2 
 
 New York Hygeia Ice Co., New York, N. Y 2 
 
 St. Joseph Artificial I. and C. S. Co., St. Joseph, Mo 1 
 
 Union Ice Mfg. Co., Pittsburg, Pa., second order 1 " 
 
 H. Henke & Co., Houston, Tex., second order 1 " 
 
 New York Hygeia Ice Co., New York, N. Y., second order 1 " 
 
 H. Henke Artificial Ice Co., Houston, Tex., third order 1 
 
 FLOUR MILLS. 
 
 Del Monte Flour Mill, San Francisco, Cal . 1 Boiler, 
 
 Chas. Tiedemann, Collinsville, 111 1 
 
 Little Rock Milling and Elevator Co., Little Rock, Ark 1 
 
 Parson's Flour Mills, San Francisco, Cal 1 " 
 
 Capitol Flour Mills, Los Angeles, Cal., first order 1 " 
 
 Texas Star Flour Mills, Galveston, Tex 1 
 
 J. B. Thro & Co., St. Charles, Mo 1 
 
 Eisenmayer Milling and Elevator Co., Halstead, Kan 1 " 
 
 Hardesty Bros., Columbus, Ohio 1 " 
 
 —168— 
 
 150 H.P. 
 
 375 
 1280 
 
 250 
 
 200 
 
 750 
 
 300 
 
 750 
 
 250 
 
 150 
 
 250 
 1250 
 
 150 
 
 640 
 
 200 
 
 250 
 65 
 
 150 
 
 750 
 
 500 
 
 120 
 
 150 
 
 200 
 
 250 
 
 300 
 
 300 
 
 150 
 
 375 
 
 120 
 
 500 
 
 300 
 
 375 
 
 375 
 
 500 
 1000 
 
 400 
 1000 
 
 300 
 60 
 
 120 
 
 750 
 
 405 
 
 500 
 1000 
 
 500 
 
 300 
 
 175 
 
 150 
 
 150 H.P. 
 
 110 " 
 
 250 " 
 
 120 " 
 
 250 " 
 
 120 " 
 
 120 " 
 
 600 " 
 
 750 " 
 
 150 " 
 
 300 " 
 
 300 " 
 
 375 " 
 
 300 " 
 
 180 H.P. 
 
 125 
 170 
 145 
 140 
 200 
 110 
 200 
 200 
 

 
 CK 
 
Lyon, Clement & Greenleaf, Ligonier, Ind 1 Boiler, 
 
 Koppitz & Smith, Pacific, Mo 1 
 
 Capitol Milling Co., Los Angeles, Cal., second order 1 " 
 
 Colorado Milling and Elevator Co., Denver, Colo 1 " 
 
 The H. C. Cole Milling Co., Chester, 111 1 " 
 
 G. Ziebold & Son, Red Bud, 111 1 '* 
 
 Glenn Bros., Hillsboro, 111 1 '' 
 
 Boney & Harper, Wilmington, N. C 1 " 
 
 Blish Milling Co., Seymour, Ind 1 " 
 
 Franz Huning, Glorietta Mills, Albuquerque, N. M 1 " 
 
 Taylor Bros. & Co., Quincy, 111 2 " 
 
 Farmers' Union and Milling Co., Stockton, Cal 2 " 
 
 R. T. Davis Mill Co., St. Joseph, Mo 1 " 
 
 The Cerealine Mfg. Co., Indianapolis, Ind 1 
 
 The Cerealine Mfg. Co., Indianapolis, Ind., second order 1 " 
 
 Plymouth Roller Mill Co., LeMars, Iowa 1 " 
 
 The Cerealine Mfg. Co., Indianapolis, Ind., third order 1 " 
 
 McDaniel & Co., Franklin, Ind 1 " 
 
 Blish Milling Co., Seymour, Ind., second order 1 
 
 The Cerealine Mfg. Co., Indianapolis, Ind., fourth order 1 
 
 The Russell & Miller M. Co., West Superior, Wis 2 
 
 R. T. Davis Mill Co., St. Joseph, Mo., second order 1 " 
 
 Metcalf, Miller & Co., Palmyra, Mo 1 " 
 
 J. S. Clark, Troy, Kan 1 " 
 
 Ballard & Ballard, Louisville, Ky 1 
 
 Blish Milling Co., Seymour, Ind., third order 1 
 
 Taylor Bros., Quincy, 111., second order 1 
 
 150 H.P. 
 
 60 
 
 * * 
 
 250 
 
 " 
 
 150 
 
 ( I 
 
 120 
 
 " 
 
 120 
 
 " 
 
 225 
 
 " 
 
 80 
 
 ( ( 
 
 500 
 
 " 
 
 500 
 
 " 
 
 250 
 
 ( ( 
 
 375 
 
 " 
 
 250 
 
 ( i 
 
 250 
 
 " 
 
 375 
 
 1 < 
 
 150 
 
 ( I 
 
 250 
 
 ( ( 
 
 120 
 
 ( 1 
 
 500 
 
 " 
 
 250 
 
 I i 
 
 120 
 
 (1 
 
 75 
 
 ( ( 
 
 250 
 
 ( ( 
 
 225 
 
 " 
 
 250 
 
 ( ( 
 
 2400 H. P. Plant of Heine Boilers at Anheuser-Busclii Brewery, 
 ST. LOUIS, MO. 
 
 170 — 
 
C. C. Washburn Flouring Mill Co 3 Boiler, 
 
 W. R. Klinger, Hermann, Mo 1 " 
 
 C. C. Washburn Flouring Mill Co., Minneapolis, Minn., second 
 
 order 3 " 
 
 V. Bachmann, Indianapolis, Ind 1 " 
 
 BREWERIES AND DISTILLERIES. 
 
 Anheuser-Busch Brewing Association, St. Louis, first order 1 Boiler, 
 
 L. Hoster Brewing Co., Columbus, Ohio, first order 1 " 
 
 Hyde Park Brewing Co., St. L/Ouis 1 " 
 
 L. Hoster Brewing Co., Columbus, Ohio, second order 1 " 
 
 Denver Brewing Co., Denver, Colo 1 " 
 
 National Brewery, San Francisco, Cal 2 " 
 
 J. G. Sohn & Co., Cincinnati, Ohio, first order 1 " 
 
 L. Hoster Brewing Co., Columbus, Ohio, third order 1 " 
 
 Anheuser-Busch Brewing Association, St. Louis, second order.... 4 " 
 
 J. B. Wathen & Bro. Co. (distillery), Louisville, Ky., first order, 1 " 
 
 Anheuser-Busch Brewing Association, St. Louis, third order 1 " 
 
 Anheuser-Busch Brewing Association, St. Louis, fourth order..., 1 " 
 
 Anheuser-Busch Brewing Association, St. Louis, fifth order 4 " 
 
 J. G. Sohn & Co., Cincinnati, Ohio, second order 1 " 
 
 Fleischman & Co. (distillery), Cincinnati, Ohio 1 " 
 
 San Antonio Brewing Association, San Antonio, Tex 1 " 
 
 Christ Moerlein Brewing Co., Cincinnati, Ohio, first order 1 " 
 
 Cincinnati Brewing Co., Hamilton, Ohio 1 " 
 
 Albert Braun Brewing Association, Seattle, Wash 2 " 
 
 J. B. Wathen & Bro. (distillery), Louisville, Ky., second order, 1 " 
 
 Allen-Bradley Co. (distillery), Louisville, Ky., first order 1 " 
 
 Allen-Bradley Co. (distillery), Louisville, Ky., second order .... 1 " 
 
 Christ Moerlein Brewing Co., Cincinnati, Ohio, second order... 4 " 
 
 The Central Distilling Co., St. Louis 3 " 
 
 St. Louis Brewing Ass'n, St. Louis 1 " 
 
 Allen-Bradley Co., Louisville, Ky., third order 1 " 
 
 Cincinnati Brewing Co., Hamilton, Ohio, second order 1 " 
 
 Christ Moerlein Brewing Co., Cincinnati, Ohio, third order. 1 " 
 
 Standard Brewery, Chicago, 111 2 " 
 
 Barthomolay Brewing Co., Rochester, N. Y 3 " 
 
 L. Hoster Brewing Co., Columbus, Ohio, fourth order 1 " 
 
 Central Distilling Co., St. Louis, second order 1 " 
 
 Lazcano Y. Gonzalez (distillery), Cardenas, Cuba 1 " 
 
 Wainwright Brewery Co., Pittsburg, Pa 1 " 
 
 Mutual Distilling Co., Uniontown, Ky 1 " 
 
 Salvador Vidal (distillery), Cardenas, Cuba 2 " 
 
 Mihalovitch, Fletcher & Co., Cincinnati, Ohio 1 " 
 
 The Allen-Bradley Co., Louisville, Ky., fourth order 1 " 
 
 Keystone Brewing Co., Pittsburg, Pa 1 " 
 
 The L. Hoster Brewing Co., Columbus, Ohio, fifth order 1 " 
 
 Beadleston & Woerz Brewing Co., New York, N. Y 2 " 
 
 The L. Hoster Brew'ing Co., Columbus, Ohio, sixth order 1 " 
 
 M. Winter & Bro., Pittsburg, Pa 1 
 
 R. C. Sibley, East Cambridge, Mass 2 " 
 
 Bay State Distillery Co., East Cambridge, Mass 1 " 
 
 San Antonio Brewing Association, San Antonio, Tex., 2d order, 2 " 
 
 J. Walker Brewing Co., Cincinnati, Ohio 1 " 
 
 L. Hoster Brewing Co., Columbus, Ohio, seventh order 2 " 
 
 American Brewing Association, Houston, Tex 1 
 
 Galveston Brewing Co., Galveston, Tex 2 " 
 
 Christian Moerlein Brewing Co., Cincinnati, Ohio, fourth order, 1 " 
 
 Bergner & Engel Brewing Co., Philadelphia, Pa 2 " 
 
 Richmond Brewery, Richmond, Va •. 1 " 
 
 Anheuser-Busch Brewing Association, St. Louis, sixth order 1 
 
 SUGAR PLANTATIONS. 
 
 D. H. Cunningham, Sugarland, Tex 1 Boiler, 
 
 J. DeMier, Santa Rosa Plantation, Cuba 4 " 
 
 J. DeMier, Santa Rosa Plantation, Cuba, second order 2 " 
 
 J. DeMier, Santa Joaquin Plantation, Cuba, third order 2 " 
 
 Casanova Brothers, Carolina Plantation, Cuba 2 
 
 Henry Heidegger, Matanzas, Cuba 1 
 
 Carlos, Booth & Co 1 
 
 Henry Heidegger, Matanzas, Cuba, second order 1 
 
 Casanova Brothers, Carolina Plantation, Cuba, second order 2 
 
 "Vicente Cagigal & Compartes, Central GerardoP. Havana, Cuba, 2 " 
 
 J. DeMier, Havana, Cuba, fourth order 1 
 
 —171— 
 
 1000 H.P. 
 100 " 
 
 1536 ' ' 
 120 " 
 
 200 H.P. 
 
 250 
 
 200 
 
 320 
 
 200 
 
 160 
 
 150 
 
 300 
 1200 
 
 300 
 
 200 
 
 200 
 1200 
 
 150 
 
 250 
 
 150 
 
 300 
 
 200 
 
 240 
 
 300 
 
 250 
 
 250 
 1200 
 
 900 
 
 300 
 
 300 
 
 300 
 
 300 
 
 400 
 
 750 
 
 300 
 
 300 
 
 200 
 
 250 
 
 375 
 
 240 
 
 100 
 80 
 
 250 
 
 300 
 
 500 
 
 250 
 
 375 
 
 500 
 
 500 
 
 300 
 
 200 
 
 600 
 
 300 
 
 500 
 
 300 
 
 500 
 
 120 
 
 300 
 
 300 H 
 1000 
 600 
 600 
 600 
 250 
 60 
 300 
 600 
 750 
 300 
 
CABLE AND ELECTRIC STREET RAILROAD COMPANIES. 
 
 St. Louis Cable and Western R. R., St. Louis 1 Boiler, 225 H.P. 
 
 Central Passenger R. R. Co. (electric), Louisville, Ky., 1st order 2 " 400 " 
 
 People's R'y Co. (cable), St. Louis 3 " 600 " 
 
 Union Depot R. R. Co. (electric), St. Louis, first order 3 " 750 " 
 
 Colorado Springs Rapid Transit R'y Co., Colorado Springs, Colo., 2 " 300 " 
 
 Arlington Heights Electric R'y Co., Fort Worth, Tex 2 " 240 " 
 
 Rochester R'y Co. (electric), Rochester, N. Y 4 " 800 " 
 
 GlenwoodandGreenlawnStreetR'y Co., Columbus, O., Istorder, 1 " 120 " 
 
 Street Railway Construction Co., Denver, Colo 3 " 375 " 
 
 Union Depot R. R. Co. (electric), St. Louis, second order 2 " 500 " 
 
 Central Passenger R. R. Co., Louisville, Ky., second order 2 " 400 " 
 
 Glenwood and Greenlawn Street R'y Co., Columbus, O., 2d order, 1 " 120 " 
 
 City Electric Street R'y Co., Little Rock, Ark 3 " 750 " 
 
 Dubuque Electric R'y, Light and Power Co., Dubuque, Iowa 1 " 300 " 
 
 Central Passenger R. R. Co., Louisville, K}'., third order 1 " 200 " 
 
 Oakland, San Leandro and Haywards Electric R'y Co., Oak- 
 land, Cal 2 " 160 " 
 
 Broadway and Seventh Ave. R. R. Co. (cable). New York City, 18 " 4500 " 
 
 Johnstown Passenger R'y Co., Johnstow'n, Pa 2 " 400 " 
 
 Union Depot R. R. Co. (electric), St. Louis, third order 2 " 500 " 
 
 Salt Lake Rapid Transit Co., Salt Lake City, Utah 1 " 200 " 
 
 Oakland, San Leandro and Haywards Electric R'y Co., Oak- 
 land, Cal., second order 1 " 140 " 
 
 Jersey City and Bergen R'y, Jersey City, N. J 2 " 600 " 
 
 Barre Sliding R'y Co., Chicago, 111 , 4 " 1500 " 
 
 Chicago and North Shore Electric R'y Co., Chicago, 111 3 " 750 " 
 
 Chicago and South Side Rapid Transit Co., Chicago, 111 2 " 300 " 
 
 Altoona and Logan Valley Electric R'y Co., Altoona, Pa 2 " 400 " 
 
 Pennsylvania R. R. Co., for Atlantic City Electric R'y, 5th order, 1 " 200 
 
 Northern Central R'y Co., Canton, Baltimore, Md 1 " 200 " 
 
 Ft. Worth and Arlington Heights St. R'y Co., Ft. Worth, Tex., 
 
 second order 1 " 120 
 
 Union Depot R. R. Co., St. Louis, Mo., fourth order 4 " 1000 " 
 
 East St. Louis Electric Street R'y Co., East St. Louis, 111 3 " '^^^ [\ 
 
 Jersey City and Bergen R'y Co., Jersey City, N. J., 2d order... 3 " 900 
 
 Jersey Consolidated Traction Co., Newark, N. J 1 " 300 
 
 Jersey Consolidated Traction Co., Newark, N.J , second order, 1 " 300 
 
 Jersey Consolidated Traction Co., Newark, N. J., third order.... 1 " 250 
 
 Allegheny Traction Co., Pittsburg, Pa 2 " 500 " 
 
 Hartford Street Railway Co., Hartford, Conn 6 " 2250 " 
 
 Union Depot R. R. Co., St. Louis, fifth order 2 " 1000 " 
 
 Otis Engineering and Construction Co., Inclined Road, Lake 
 
 George, N. Y 1 " 160 " 
 
 St. Charles Street R'y Co., New Orleans, La 3 " 615 || 
 
 Orleans R'y Co., New Orleans, La 2 " 510 
 
 Louisville R'y Co., Louisville, Ky., fourth order 1 " 200 
 
 Bergen County Traction Co., Bergen Co., N. J 2 " 500 
 
 Luzerne, Dallas and Harvey's Lake R'y Co., Wilkesbarre, Pa.. 3 " 1005 
 
 Hartford Street R'y Co., Hartford, Conn., second order 2 " 600 
 
 Lynchburg & Rivermont Street R'y Co., Lynchburg, Va 2 " 400 
 
 Toledo Traction Co., Toledo, O 2 " 1000 " 
 
 J. G. Brill, for Cape Town, Africa 3 " 900 || 
 
 Second Avenue Traction Co., Pittsburg, Pa., second order 2 " 740 
 
 Englewood & Chicago Electric Street R'y Co., Chicago, 111 3 " 600 " 
 
 Fort Pitt Traction Co., Allegheny, Pa 1 " 250 " 
 
 Toledo Traction Co., Toledo, O., second order 2 " 1000 
 
 Philadelphia and Reading Co., Philadelphia, Pa 1 " 425 
 
 Tamalpais Electric Ry. Co., California 1 " 105 
 
 RICE AND OIL MILLS. 
 
 Howard Oil Co., Houston, Tex., first order 2 Boiler, 500 H.P. 
 
 Howard Oil Co., Houston, Tex., second order 1 " 250 
 
 Galveston Oil Co., Galveston, Tex •. 2 " 500 " 
 
 H. Shumaker Oil Mills, Navasota, Tex 1 " 250 " 
 
 Meridian Oil Mills and Mfg. Co., Meridian, Miss 1 " 250 " 
 
 Wilmington Oil Mills, Wilmington, N. C ' 1 " 250 " 
 
 Independent Cotton Oil Co., New Orleans, La 1 " 250 " 
 
 Capitol City Oil Works, Jackson, Miss., first order 1 " 150 
 
 Union Oil Co., New Orleans, La 3 " 750 || 
 
 Capitol City Oil Mills, Jackson, Miss., second order.. 1 " 150 
 
 Crescent City Rice Mill Co., New Orleans, La 1 " 150 " 
 
 A. Socola Rice Mills, New Orleans, La 1 " 150 " 
 
 Mississippi Cotton Oil Co., Meridian, Miss., second order 1 " 375 
 
 National Cotton Oil Co., Houston, Tex., third order 1 " 250 
 
 —172— 
 
National Cotton Oil Co., Galveston, Tex., second order 1 Boiler, 250 H.P. 
 
 National Cotton Oil Co., Denison, Tex 2 " 750 " 
 
 Union Oil Co., Vidalia, La 1 " 375 " 
 
 National Cotton Oil Co., Texarkana, Ark 1 " 375 " 
 
 Atlantic Refining Co., Pt. Breeze, Pa 2 " 750 " 
 
 ELECTRIC LIGHT, 
 
 POWER AND GAS COMPANIES. 
 
 Boiler, 
 
 Springfield Electric Light Co., Springfield, Mo 1 
 
 St. Louis Gas Light Co., St. Louis 1 
 
 Evanston Electric Light Co., Evanston, 111 2 
 
 Forest City Electric Light Co., Rockford, 111 1 
 
 Des Moines Edison Light Co., Des Moines> la., first order 1 
 
 Allegheny County Light Co., Pittsburg, Pa 3 
 
 Des Moines Edison Light Co., Des Moines, la., second order... 1 
 
 Columbus Electric Light & Power Co., Columbus, O., 1st order, 1 
 
 70 H.P. 
 
 90 
 140 
 110 
 200 
 960 
 150 
 250 
 
 • Station C, Edison Light and Power Co., 
 
 SAN FRANCISCO, CAL. 
 
 Contains 1500 H. P. Heine Boilers. 
 
 Troy Gas Light Co., Troy, N. Y 1 Boiler, 80 H. 
 
 Colorado Electric Co., Denver, Colo., first order 4 " 600 
 
 Little Rock Electric Light Co., Little Rock, Ark 1 " 200 
 
 Colorado Electric Co., Denver, Colo., second order 1 " 150 
 
 Boston Edison Co., Boston, Mass 2 " 500 
 
 Chicago Edison Co., Chicago, 111., first order 4 " 1340 
 
 Brush Electric Light and Power Co., Galveston, Tex 1 " 200 
 
 Columbus Electric Light & Power Co., Columbus, O., 2d order, 1 " 300 
 
 Colorado Electric Co., Denver, Colo., third order 1 " 300 
 
 —174- 
 
Columbus Electric Light & Power Co., Columbus, O., 3d order, 1 Boiler, 300 H.P. 
 
 Colorado Electric Co., Denver, Colo., fourth order 1 " 150 " 
 
 Pueblo Gas and Electric Ivight Co., Pueblo, Colo 1 " 200 " 
 
 Cedar Rapids Electric Light and Power Co., Cedar Rapids, la., 1 " 125 " 
 
 Little Rock Electric Light Co., Little Rock, Ark., 2d order 1 " 300 " 
 
 Litchfield Electric Light and Power Co., Litchfield, 111 1 " 150 " 
 
 Boston Edison Co., Boston, Mass., second order 1 " 300 " 
 
 Laclede Gas Co., St. Louis 3 " 942 " 
 
 Hill City Electric Light and Power Co., Vicksbnrg, Miss 1 " 200 " 
 
 University Park Railway and Electric Co., Denver, Colo 1 " 110 " 
 
 Hibbard Electric Supply Manufacturing Co., Montreal, Can 1 " 200 " 
 
 Columbus Electric Light & Power Co., Columbus, O., 4th order 1 " 300 " 
 
 Des Moines Edison Light Co., Des Moines, la., third order 1 " 200 " 
 
 H. A. & T. C. Gooch, Louisville, Ky 1 " 150 " 
 
 Detroit Electric Light and Power Co., Detroit, Mich 2 " 720 " 
 
 Chicago Edison Co., Chicago, 111., second order 4 " 1464 " 
 
 Citv Electric Light Co., Kalamazoo, Mich 1 " 125 " 
 
 D. C. Hartwell, Ouray, Colo 1 " 200 " 
 
 Milwaukee Power and Lighting Co., Milwaukee, Wis 1 " 320 " 
 
 Citizens' Gas Light and Heating Co., Bloomington, 111 1 " 150 " 
 
 Edison General Electric Co., New York 1 " 250 " 
 
 Western Electrical Construction Co., Denver, Colo., 1st order .. 1 " 200 " 
 
 Western Electrical Construction Co., Denver, Colo., 2d order.... 2 " 400 " 
 
 Electricnl Improvement Co., San Francisco, Cal 2 " 200 " 
 
 Gooch Electric Light Co., Louisville, Ky 1 " 256 " 
 
 Columbus Electric Light & Power Co., Columbus, O., 5th order, 1 " 300 " 
 
 Craig & Son, St. Cunegard, Montreal, Electric Station 1 " 150 " 
 
 St. Jean Baptiste Electric Co., Canada, first order 1 " 150 " 
 
 Cedar Rapids El. L't and P. Co., Cedar Rapids, la., 2d order... 2 " 300 " 
 
 Ann Arbor T. H. Electric Co., Ann Arbor, Mich 1 " 150 " 
 
 Chicago Edison Co., Chicago, 111., third order 3 " 1125 " 
 
 Denver Consolidated Electric Co., Denver, Colo., 7th order 2 " 400 " 
 
 Vallejo Electric Light and Power Co., Vallejo, Cal 2 " 150 " 
 
 San Francisco Gas Co., San Francisco, Cal 2 " 350 " 
 
 Denver Consolidated Electric Co., Denver, Colo., eighth order, 2 " 400 " 
 
 Forest City Electric L't and Power Co., Rockford, 111., 2d order, 1 " 300 " 
 
 J. DeMier, Santa Rosa, Cuba 1 " 60 " 
 
 Denver Consolidated Electric Co., Denver, Colo., ninth order ..1 " 200 " 
 
 Brookfield Electric Light Co., Brookfield, Mo 1 " 150 " 
 
 St. Jean Baptiste Electric Co., Canada, second order 2 " 500 " 
 
 Petaluma Electric Light and Power Co., Petaluma, Cal 2 " 150 " 
 
 Edison Electric Illuminating Co., New York 1 " 375 " 
 
 Washington Gas Light Co., Washington, D. C 2 " 500 " 
 
 Temple Electric Co., Montreal, Canada 2 " 400 " 
 
 Citv Electric Light Co., Kalamazoo, Mich , second order 1 " 150 " 
 
 Salt Lake City Gas Co., Salt Lake City, Utah 2 " 750 " 
 
 Forest City Electric L't and Power Co., Rockford, 111., 3d order, 1 " 300 " 
 
 Denver Consolidated Electric Co., Denver, Colo., tenth order.... 1 " 200 " 
 
 Siemens & Halske Electric Co., Chicago, 111 2 " 300 " 
 
 Cedar Rapids EL L't and P. Co., Cedar Rapids, la., 3d order ..1 " 200 " 
 
 Edison Electric Illuminating Co., New York, second order 1 " 375 
 
 Pennsylvania R. R. Co,, for Pittsburg U. D. Elec. Light Plant, 2 " 500 " 
 
 Chicago Edison Co., Chicago, 111., fourth order 1 " 500 
 
 Pennsylvania R. R. Co., for Jersey City Depot Elec. Light Plant, 3 " 1125 
 
 Mutual Light and Power Co., Montgomery, Ala 3 " 600 
 
 Toronto Electric Light Co., Toronto, Ont 2 " 520 " 
 
 East River Gas Co., Long Island City, N. Y 4 " 600 " 
 
 Chicago Edison Co., Chicago, 111., fifth order 7 " 3500 |' 
 
 Chicago Edison Co., Chicago, 111., sixth order 1 " 200 
 
 Chicago Edison Co., Chicago, 111., seventh order 1 " 375 
 
 Chicago Edison Co., Chicago, 111., eighth order 1 " 500 
 
 Channon & Wheeler, Quincy, 111 : 2 " 620 " 
 
 Bridge Mill Power Co., Pawtucket, R. 1 2 " 610 " 
 
 Chicago Edison Co., Chicago, 111., ninth order 2 " 1148 
 
 Woonsocket Electric Machine and Power Co., Woonsocket, R. I., 2 " 320 
 
 Dayton Electric Light Co., Dayton, 3 " 750 || 
 
 Denver Consolidated Electric Co., Denver, Colo., 11th order 1 " 375 
 
 Kalamazoo Electric Co., Kalamazoo, Mich 1 " 375 
 
 Brookline Gas Co., Bo.ston, Mass 2 " 400 " 
 
 The T. Eaton Co., Toronto, Ont 2 " 300 " 
 
 Salt Lake & Ogden Gas & Elec. L't Co. , Salt Lake City, 2d order, 1 1 1 ^"^^ \\ 
 
 Laclede Gas Light Co., St. Louis, second order 1 " 300 '' 
 
 A. Von Rosenzweig, Mexico City, Mexico 3 " 375 
 
 Edison Illuminating Co., St. Louis 15 " 5600 
 
 General Electric Co., Schenectady, N. Y 1 '|. 108 '| 
 
 United Gas Improvement Co., Sioux City, la 1 " 255 
 
 —175— 
 
Edison Light and Power Co., San Francisco, Cal., first order... 4 Boiler, 1500 H.P. 
 
 T. Baton & Co., Toronto, Ont., second order 1 " 150 
 
 J. J. Vandergrift, Pittsburg, Pa 2 " 500 
 
 Kdison Liglit and Power Co., San Francisco, second order 2 " 750 
 
 Brookline Gas Light Co., Boston, Mass 2 " 400 
 
 Cedar Rapids Elec. Light and P. Co., Cedar Rapids, la., 4tli order, 1 " 200 
 
 Indianapolis Gas Co., Cicero, Ind 4 " 1372 
 
 Logansport & Wabash Valley Gas Co., Windfall, Ind 1 " 343 
 
 Mutual Light & Power Co., Montgomery, Ala., second order .... 1 " 200 
 
 Somerville Electric Light Co., Somerville, Mass 2 " 510 
 
 New Omaha T. H. Elec. Light Co., Omaha, Neb 1 " 375 
 
 Chicago Edison Co., tenth order 1 " 574 
 
 Chelsea Gas Light Co., Chelsea, Mass 1 " 225 
 
 Salena, Va., Electric Light Plant 1 " 125 
 
 Newton and Watertown Gas Light Co., Newton, Mass 1 " 305 
 
 New Omaha T. H. Electric Light Co., Omaha, Neb., 2d order.. 1 " 375 
 
 Citizens Electric Light and Power Co., East St. Louis, 111 1 " 250 
 
 Pennsylvania Heat, Light and Power Co., Philadelphia, Pa 2 " 750 
 
 Toronto Electric Light Co., second order 1 " 250 
 
 Peorra Water Works, 
 
 PEORIA, ILL. 
 
 Contains 1200 H. P. Heine Boilers. 
 
 WATER WORKS. 
 
 Stockton Water Works, Stockton, Cal 1 Boiler, 25 H.P. 
 
 Spring Valley Water Co., San Francisco, Cal 3 " 600 
 
 Houston Water Works, Houston, Tex., first order 2 " 220 
 
 Lawrence Water Works, Lawrence, Kan 2 " 180 
 
 National Water Works Co., Kansas City, Mo ■ 4 " 800 
 
 Texarkana Water Co., Texarkana, Ark 2 " 160 
 
 Millbury Water Co., Mill bury, Mass., first order 1 " 100 
 
 Millbury Water Co., Milibury, Mass., second order 1 " 85 
 
 Sheboygan Water Co., Sheboygan, Wis 2 " 150 
 
 Grafton Water Co., Grafton, Dak 1 " 50 
 
 City Water Co., Chattanooga, Tenn 1 " 250 
 
 Norristown Water Co., Norristown, Pa 3 " 300 
 
 —176— 
 
Cincinnati Water Co., Cincinnati, O 2 Boiler, 
 
 Jefferson City Water Co., Jefferson City, Mo 2 
 
 Memphis Artesian Water Co., Memphis, Tenn 6 " 
 
 St. Joseph Water Co., St. Joseph, Mo 2 
 
 Montreal Water Co., Montreal, Can 3 " 
 
 Houston Water Works, Houston, Tex., second order 1 " 
 
 Peoria Water Works, Peoria, 111 6 " 
 
 Cit}' Water Co., Chattanooj^a, Tenn., second order 1 " 
 
 Iv. & W. B. Bull, Quincy, 111 1 
 
 L. & W. B. Bull, Ouincy, 111., second order 1 
 
 Sheboygan Water Co., Sheboygan, Wis., second order 1 
 
 Houston Water Works, Houston, Tex., third order 1 " 
 
 St. Joseph Water Co., St. Joseph, Mo., second order 1 " 
 
 H. D. Campbell & Sons, Traverse City, Mich 1 
 
 Olympic Salt Water Co., San Francisco 2 " 
 
 Mahanoy City Water Works, Mahanoy City, Pa 1 " 
 
 St. Clair Water Co., Pittsburg, Pa 3 " 
 
 Spring Valle}^ Water Co., San Francisco, Cal., second order 1 " 
 
 Maysville Water Co., Maysville, Ky 2 " 
 
 Worcester Engineering Co., Millburj' (Water Co.), Mass 1 " 
 
 Worcester Fngineering Co., Millburv (Water Co.), Mass 1 " 
 
 City Water Board, Wheeling, W. Va 2 
 
 Cit}' Water Board, Wheeling, W. Va., second order 2 " 
 
 Tyler Water Co., Tyler, Tex 1 
 
 MINING, COAL AND SMELTING COMPANIES. 
 
 Quartz Mountain Mining Co., San Francisco, Cal 1 Boiler, 
 
 Santa Anna Mining Co., Oposura, Mex 2 " 
 
 La Plata Mining and Smelting Co., Leadville, Colo 1 " 
 
 Philadelphia Smelting and Refining Co., Pueblo, Colo 3 " 
 
 Cannon Coal Co., Denver, Colo 1 " 
 
 Alaska Treadwell Gold Mining Co., Douglas Island, Alaska 2 " 
 
 Silver Age Mining Co., Idaho Springs, Colo 1 " 
 
 Boston and Montana C. C. and S. M. Co., Great Falls, Mont ... 2 
 
 Alaska Treadwell G. M. Co., Alaska, second order 1 " 
 
 Madison Coal Co., St. Louis 1 '' 
 
 W. Y. O. D. Mining Co., San Francisco, Cal 1 " 
 
 Kilpatrick Bros. & Collins (coal mines), Cambria, Wyoming ... 1 " 
 
 Magnetic Iron Ore Co., Carthage, N. Y 2 " 
 
 De Lamar Gold Mining Co., De Lamar, Nev 1 " 
 
 Solva}' Process Co., Syracuse, N. Y . 4 " 
 
 Hocking Valley Coal Co., Nelsonville, O. 2 " 
 
 St. Joe Lead Co., Bonne Terre, Mo., first order 1 " 
 
 Paymaster Mining Co., Ogilvy, Cal 1 " 
 
 St. Joe Lead Co., Bonne Terre, Mo., second order.. 1 " 
 
 St. Joe Lead Co., Bonne Terre, Mo., third order 1 " 
 
 Chas. Wagner, Mexico 1 " 
 
 Desloge Consolidated Lead Co., Bonne Terre, Mo 2 " 
 
 Omaha and Grant Smelting Works, Denver, Colo 3 " 
 
 St. Joe Lead Co., Bonne Terre, Mo., fourth order 1 " 
 
 Globe Smelting and Refining Co., Denver, Colo 1 " 
 
 Ocean Coal Co., Horatio, Pa 3 " 
 
 Owsley & Cowan, Butte, Mont 2 " 
 
 Arizona Copper Co., Clifton, Ariz 2 " 
 
 De Lamar Gold Mining Co., De Lamar, Nev., second order 1 " 
 
 E. G. Stoiler, Unity Tunnel, Silverton, Colo 1 
 
 J. R. De Lamar, Milford, Utah 2 
 
 Independence Mine, Victor, Colo 1 " 
 
 Independence Mine, Victor, Colo., second order 1 " 
 
 Anaconda Copper Mining Co., Anaconda, Mont 2 " 
 
 Independence Mine, Victor, Colo., third order 1 " 
 
 Solvay Process Co., Sharon, Pa., second order 2 
 
 Anaconda Copper Mining Co., Anaconda, Mont., second order, 2 " 
 
 Mountain Copper Co 1 " 
 
 Canadian Gold Field Co 2 " 
 
 International Coal Mining Co 1 " 
 
 IRON FURNACES. 
 
 De Bardeleben Coal and Iron Co., Birmingham, Ala., 1st order, 5 Boiler, 
 
 Sheffield Iron Co., Sheffield, Ala., first order 3 
 
 Lady Ensley Furnace Co., Sheffield, Ala., first order 3 " 
 
 Mexican Iron Mountain Mfg. Co., Durango, Mex 2 " 
 
 Pulaski Iron Co., Pulaski Cit}', Va., first order 3 " 
 
 Ashland Iron and Steel Co., Ashland, Wis 3 " 
 
 Cameron Coal Co., Cameron, Pa., first order 3 " 
 
 —177— 
 
 600 H.P. 
 290 
 900 
 260 
 600 
 230 
 1200 
 250 
 250 
 250 
 150 
 150 
 250 
 150 
 150 
 300 
 480 
 120 
 200 
 
 85 
 
 85 
 400 
 400 
 130 
 
 165 H.P. 
 180 
 110 
 360 
 150 
 400 
 100 
 300 
 200 
 200 
 150 
 300 
 300 
 120 
 1000 
 400 
 375 
 
 75 
 375 
 375 
 120 
 600 
 750 
 375 
 200 
 600 
 400 
 300 
 120 
 
 60 
 250 
 300 
 300 
 750 
 300 
 500 
 750 
 200 
 160 
 150 
 
 1250 H.P. 
 750 
 750 
 300 
 960 
 450 
 750 
 
Cameron Coal Co., Cameron, Pa., second order 1 Boiler, 
 
 New River Mineral Co., New River Depot, Va 2 " 
 
 Pulaski Iron Co., Pulaski City, Va., second order 1 " 
 
 Sheffield Iron Co., Sheffield, Ala., second order 1 " 
 
 Lady Ensley Furnace Co., Sheffield, Ala., second order 1 " 
 
 De Bardeleben Coal and Iron Co., Birmingham, Ala., 2d order, 7 " 
 
 Pulaski Iron Co., Pulaski City, Va., third order 1 " 
 
 PACKING HOUSES. 
 
 Armour Packing Co., Kansas City, Mo., first order 1 Boiler, 
 
 Armour Packing Co., Kansas City, Mo., second order 1 " 
 
 Kansas City Packing Co., Kansas City, Mo 1 " 
 
 Fort Worth Packing Co., Fort Worth, Tex., first order 1 "■ 
 
 Fort Worth Packing Co., Fort Worth, Tex., second order 1 " 
 
 Roth -Meyer Packing Co., Cincinnati, Ohio 3 " 
 
 N. K. Fairbank & Co., St. Louis, first order 2 " 
 
 N. K. Fairbank & Co., Chicago, 111., first order 1 " 
 
 N. K. Fairbank & Co., St. Louis, second order 1 " 
 
 N. K. Fairbank & Co., Chicago, 111., second order 2 " 
 
 Nelson Morris & Co., Chicago, 111 2 " 
 
 K. C. Packing Co., Schwartzschild-Sultzberger Co., 2d order.... 2 " 
 
 Swift & Co., Kansas City, Mo 2 " 
 
 N. K. Fairbank & Co., Chicago, 111., fourth order 1 " 
 
 St. Louis Dressed Beef and Provision Co., St. Louis 1 " 
 
 Swift & Co., East St. Louis, 111., second order 1 " 
 
 MISCELLANEOUS. 
 
 Chicago Corset Co., Aurora, 111 2 Boiler, 
 
 Phoenix Chair Co., Sheboygan, Wis., first order 2 " 
 
 H. E. Roth, Sheboygan, Wis 1 " 
 
 Julius Berkey Felt Boot Co., Grand Rapids, Mich 1 " 
 
 P. B. Mathiason & Co., Bone Black Works, St. Louis 2 " 
 
 W. T. Coleman & Co., Borax Works, San Francisco, Cal 1 " 
 
 California Powder Mills 1 " 
 
 W. S. Townsend, Candy Manufacturer, San Francisco, Cal 1 " 
 
 California Jute Mills, Oakland, Cal 2 
 
 M. P. Robinson, Honolulu, Sandwich Islands 1 " 
 
 Springfield Wagon Co., Springfield, Mo 1 " 
 
 G. B. Kane & Co., Chicago, 111 1 || 
 
 Union Tobacco Works, Louisville, Ky 1 
 
 Houston & Texas Central R'yj Houston, Tex., first order 1 " 
 
 J. J. Langles & Co., New Orleans, La 1 
 
 Chicago Copper Refining Co., Chicago, 111., first order 1 
 
 R. L. McDonald & Co., St. Joseph, Mo 1 " 
 
 James Roy & Co., Troy, N. Y. 2 " 
 
 Chicago Corset Co., Aurora, 111., second order 1 " 
 
 Hueter Bros. & Co., San Francisco, Cal 1 " 
 
 Houston & Texas Central R'y, Houston, Tex., second order..... 1 
 
 Brittain, Richardson & Co., St. Joseph, Mo 1 " 
 
 Orr's Paper Mills, Troy, N. Y 1 
 
 Benecia Agricultural Works, Benecia, Cal 1 
 
 A. H. Belo & Co., Galveston, Tex 1 " 
 
 King Kalakua, Honolulu, Sandwich Islands 1 " 
 
 J. G. Johnson & Co., Spuyten Duyval, N. Y 1 " 
 
 Kiddel & Stewart, Denver, Colo 1 " 
 
 Tim Wallerstein & Co., Troy, N. Y 1 " 
 
 B. J. Johnson & Co., Milwaukee, Wis 1 
 
 Carteret Chemical Co., Newark, N.J 1 " 
 
 John Mouat Lumber Co., Denver, Colo 1 " 
 
 Forest Paper Co., Yarmouthville, Me 2 " 
 
 Cumberland Mills, Cumberland, Me 2 
 
 Kansas City, Fort Scott & Gulf R. R., Springfield, Mo 1 
 
 Los Angeles Machinery Depot, Los Angeles, Cal 1 
 
 A. Bering & Bro., Houston, Tex 1 
 
 Wm. H. Bungee, Chicago, 111 1 " 
 
 Phcenix Chair Co., Sheboygan, Wis., second order 1 
 
 Dallas Cotton and Woolen Mills, Dallas, Tex 2 " 
 
 Loomis Gas Machinery Co., Philadelphia 1 
 
 Sommer, Richardson & Co., St. Joseph, Mo 1 
 
 Charles Stern, Los Angeles, Cal 1 
 
 La Constancia Woolen Mills, Durango, Mex 1 
 
 A. C. Melchert, Albany, N. Y 1 
 
 Arkadelphia Cotton Mills, Arkadelphia, Ark 1 " 
 
 Spring Grove Cemetery, Cincinnati, O 1 
 
 —178— 
 
 250 H.P. 
 
 300 " 
 
 320 " 
 
 250 " 
 
 250 " 
 
 2240 ' ' 
 
 320 " 
 
 300 H.P. 
 
 300 " 
 
 300 " 
 
 300 " 
 
 300 " 
 
 300 " 
 
 600 " 
 
 500 " 
 
 500 " 
 
 1000 " 
 
 500 " 
 
 600 " 
 
 740 " 
 
 250 " 
 
 375 " 
 
 370 " 
 
 120 H.P 
 
 450 " 
 
 30 " 
 
 140 " 
 
 180 " 
 
 65 " 
 
 65 " 
 
 130 " 
 
 220 " 
 
 75 " 
 
 110 " 
 
 20 " 
 
 70 " 
 
 200 " 
 
 55 " 
 
 120 " 
 
 80 " 
 
 180 " 
 
 110 " 
 
 80 " 
 
 200 " 
 
 90 " 
 
 125 " 
 
 100 " 
 
 50 " 
 
 80 " 
 
 90 " 
 
 110 " 
 
 50 " 
 
 110 " 
 
 150 " 
 
 110 " 
 
 300 " 
 
 300 " 
 
 150 " 
 
 75 " 
 
 110 " 
 
 75 " 
 
 150 " 
 
 400 " 
 
 110 " 
 
 110 " 
 
 165 " 
 
 75 " 
 
 150 " 
 
 150 " 
 
 80 " 
 
Gilbert & Walker, Honolulu, Sandwich Islands 
 
 Meier & Kruse, Honolulu, Sandwich Islands 
 
 Crocker Chair Co., Sheboygan, Wis 
 
 Mexican Central Railway 
 
 Christian Peper Tobacco Factory, St. Louis 
 
 Chicago Copper Refining Co., Chicago, 111., second order 
 
 Seeger & Guernsey, N. Y., for Senor Pechado, Toluca, Mex 
 
 American Mfg. Co., vSheboygan, Wis 
 
 Gutta Percha and Rubber Mfg. Co., California 
 
 Williamette Pulp Paper Co., Oregon City, Ore 
 
 A. Meinicke & Son, Milwaukee, Wis 
 
 Louisiana Furniture Mfg. Co., New Orleans, La 
 
 Rockford Hosier}^ and Mitten Co., Rockford, 111 
 
 Beckett Paper Co., Hamilton, O 
 
 Western Wheel Works, Chicago, 111 
 
 A. H. Andrews & Co., Chicago, 111 
 
 Publishers, Geo. Knapp & Co., St. Louis Republic, St. Louis... 
 Seeger & Guernse}^ New York City and City of Mexico, Mex... 
 
 Aug. Beck & Co., Chicago, 111 
 
 L. H. Prentice & Co., Chicago, 111 
 
 Orrs & Co., Troy, N. Y., second order 
 
 Tompkins Paper Stock Co., Troy, N. Y 
 
 Tim Co., Collar and Shirt Factory, Troy, N. Y 
 
 Albany Card Paper Co., Albany, N. Y 
 
 Wm. Angus & Co., East Angus, P. Quebec , 
 
 D. L. Parish Laundrj' Co., St. Louis 
 
 Temple Co., Muskegon, Mich 
 
 Williamette Paper Co., Oregon City, Ore., second order 
 
 Roj-al Pulp and Paper Co., Fast Angus, P. Quebec 
 
 Western Wheel Works, Chicago, 111., second order 
 
 Heath & Milligan Mfg. Co., Chicago, 111 
 
 McCormick Har^^ester Machine Co., Chicago, 111 
 
 American Wood Paper Co., Manayunk, Pa 
 
 Publishers, George Knapp & Co., St. Louis, second order 
 
 Courier-Journal Co., Louisville, Ky 
 
 Bausch & Lomb Opt. Co., Rochester, N. Y 
 
 Denver Paper Mills Co., Denver, Colo , 
 
 Cortina, Pichardo & Co., Toluca, Mex 
 
 Phoenix Furniture Co., Grand Rapids, Mich 
 
 Dominion Cotton Mills Co., Canada 
 
 Robert White & Co., Canada 
 
 Montreal Carriage Leather Co 
 
 Sewerage Works, Stockton, Cal 
 
 Bastion & Valiquetto, Canada 
 
 Eagle Automatic Can Co., San Francisco, Cal 
 
 Orrs & Co., Troy, N. Y., third order 
 
 Bottsford Paper Mill Co., Kalamazoo, Mich 
 
 Edward E. Barton, Hutchison, Kan 
 
 Pennsylvania R. R. Co., for Renova, Pa., shops, first order 
 
 Pennsylvania R. R. Co., for Pittsburg shops, second order 
 
 Thos. D. W^hitaker, Phillipsburg, N. J 
 
 The Iowa Farming Tool Co., Fort Madison, Iowa 
 
 W. A. Elmendorf, Chicago, 111 
 
 Pennsylvania R. R. Co., for Jersey City, third order 
 
 The Burkey & Gay Furniture Co., Grand Rapids, Mich 
 
 Pennsylvania R. R. Co., Broad St. Station, Phil., Pa., 4th order, 
 
 Hubbard & Co., Pittsburg, Pa 
 
 National Starch Mfg. Co., Glen Cove, N. Y 
 
 Northwestern Terre Cotta Co., Chicago, 111 
 
 Buffalo Brass Co., Buffalo, N. Y 
 
 Mallinckrodt Chemical Works, St. Louis 
 
 Ferris Wheel, World's Columbian Exposition, Chicago, 111 
 
 Smith & Barnes Piano Co., Chicago, 111 
 
 Beaver & Co., Soap W^orks, Daj-ton, Ohio 
 
 National Carbon Co., Cleveland, Ohio 
 
 L. Waterbury & Co., Brooklyn, N. Y 
 
 Sterrit & Thomas, Pittsburg, Pa 
 
 C. L. Colman, Lumber, La Crosse, Wis 
 
 St. Louis Dried Grains Co 
 
 Lannett Cotton Mills, West Point, Ga 
 
 Jno. D. Spreckles Bro., San Francisco, Cal 
 
 Sterling White Lead Co., Pittsburg, Pa 
 
 Duryea Starch Co., Glen Cove, Long Island 
 
 ^tna Paper Co., Dayton, Ohio 
 
 Wm. Deering & Co., Chicago, 111 
 
 Boiler, 
 
 55 H.P. 
 
 55 
 300 
 150 
 200 
 100 
 
 75 
 200 
 100 
 300 
 150 
 150 
 120 
 250 
 600 
 250 
 120 
 
 80 
 130 
 150 
 250 
 125 
 120 
 150 
 150 
 
 80 
 250 
 200 
 300 
 400 
 200 
 375 
 500 
 120 
 240 
 500 
 300 
 
 75 
 150 
 450 
 150 
 
 75 
 
 80 
 
 50 
 100 
 450 
 400 
 500 
 600 
 500 
 250 
 250 
 
 20 
 1125 
 300 
 900 
 250 
 150 
 150 
 
 60 
 375 
 750 
 200 
 200 
 1000 
 800 
 
 50 
 120 
 200 
 900 
 
 30 
 250 
 200 
 300 
 750 
 
 -179- 
 
Missouri State Penitentiary, Jefferson City, Mo 4 Boiler, 1500 H.P. 
 
 Wm. Campbell & Co. , New York Cit}' 1 " 200 
 
 Peerless Brick Co., Philadelphia, Pa 1 " 120 
 
 Whitaker Cement Co., Phillipsburg, N. J., second order 1 " 250 
 
 National Ivead Co., St. Louis 1 " 250 
 
 Wilmington Cotton Mills, Wilmington, N. C 1 " 250 
 
 Heath & Milligan Mfg. Co., Chicago, 111., second order 1 " 200 
 
 Hamilton Power Co., Montreal, Canada 2 " 240 
 
 W. G. Warden, Philadelphia, Pa 5 " 750 
 
 J. Iv. Ketterlinus, Philadelphia, Pa 2 " 180 
 
 Theo. Kuntz, Cleveland, Ohio 2 " 400 
 
 Rockford Mitten and Hosiery Co., Rockford, 111., 2d order 2 " 400 
 
 Bearing Harvester Co., Chicago, 111., second order 2 " 928 
 
 Heath & Milligan Mfg. Co., 
 
 CHICAGO, ILL. 
 
 Contains 400 H. P. Heine Boilers. 
 
 Leona Cotton Mills, Monterey, Mex 1 Boiler, 100 H.P. 
 
 Deering Harvester Co., Chicago, 111., third order 1 " 250 
 
 J. Home & Co., Pittsburg, Pa 2 " 240 
 
 Pennsylvania R. R. Co., Philadelphia, Pa., sixth order 1 " 500 
 
 Pennsj'lvania R. R. Co., Jersey City, N. J., seventh order 1 " 337 
 
 Partridge & Netcher, Boston Store, Chicago, 111 1 " 325 
 
 Mississippi River Dredge Boat "Beta" 4 " 1333 
 
 —180— 
 
Northwestern Terra Cotta Co., Chicago, 111., second order 1 Boi 
 
 R. H. White & Co., Boston, Mass 3 
 
 New Orleans Sewerage Co., New Orleans, La 2 
 
 National Sewing Machine Co., Belvedere, 111 1 
 
 Ansonia Brass and Copper Co., Ansonia, Conn 4 
 
 Kaufmann Bros., Pittsburg, Pa 1 
 
 Griffin Mfg. Co., Griffin, Ga 2 
 
 Warren Mfg. Co., Warren, R. 1 4 
 
 Eastman's Co., New York City 1 
 
 Russell & Co., Massillon, Ohio 2 
 
 Burlington Elevator Co., St. Louis 3 
 
 Woonsocket Worsted Mills, Woonsocket, R. 1 2 
 
 Northwestern Terra Cotta Co., Chicago, 111., third order 1 
 
 Arlington Mfg. Co., Arlington, N. J 2 
 
 J. W. Peters Fish & Oyster Co., St. Louis 1 
 
 Rockford Sugar Works, Rockford, 111 3 
 
 Mallinckrodt Chemical Co., St. Louis, second order I 
 
 New Brittain Knitting Co., New Brittain, Conn 1 
 
 Pennsylvania R. R. Co., Philadelphia, Pa., eighth order 2 
 
 Proximity Mfg. Co., Greensboro, N. C 2 
 
 Louis Reibold, Dayton, Ohio 2 
 
 Fleischmann & Co., Greenspoint, N. Y 4 
 
 Frank Jones, Portsmouth, N. H 3 
 
 Pennsylvania R. R. Co., Philadelphia, Pa., ninth order 1 
 
 Drummond Mfg. Co., Louisville, Ky 1 
 
 Sormova Co., Nijni Novgorod, Russia 1 
 
 U. S. Dredge Boat Delta 4 
 
 Wm. A. Talcott, Rockford, 111 2 
 
 Deering Harvester Co., Chicago, 111., third order 2 
 
 Struller, Meyer & Julia Co., City of Mexico 1 
 
 R. H. & C. B. Reeves, Camden, N. J 1 
 
 S. Ishida, Yokohama, Japan 2 
 
 Van Zile & Chrysler, Albany, N. Y I 
 
 Sterling White Lead Co., New Kensington, Pa., second order.... 1 
 
 Chas. F. Joy, St. Louis 1 
 
 Booth & Son, California 2 
 
 Job Mills, California 1 
 
 H. P. Faye & Co., California 1 
 
 K. Cohn & Co., California 1 
 
 Chelsea Jute Mills, Greensport, N. Y 3 
 
 INational Sewing Machine Co., Belvidere, 111., second order 1 
 
 ler, 
 
 150 H. 
 
 630 
 
 200 
 
 150 
 1020 
 
 150 
 
 300 
 1220 
 
 250 
 
 400 
 
 510 
 
 320 
 
 200 
 
 250 
 90 
 
 900 
 
 500 
 
 305 
 1000 
 
 500 
 
 300 
 
 880 
 
 600 
 
 500 
 80 
 
 250 
 1000 
 
 170 
 
 873 
 75 
 
 150 
 
 500 
 
 100 
 
 250 
 
 250 
 
 200 
 
 120 
 
 100 
 
 105 
 1515 
 
 250 
 
 —181— 
 
INDEX, 
 
 Page. 
 
 Absorption and transmission of heat in Heine Boilers 142 
 
 Advantages of oil as a fuel 32, 36 
 
 Air consumed in combustion of fuel 13, 111 
 
 necessary for ventilation. Amount of. Table 50 87 
 
 heating of 83 
 
 Allegheny Traction Co. (Illustration) 69 
 
 American Coals. Composition of, Table 12 , 20, 21 
 
 Analyses of gases, Tables 22, 23, 29, 32 45, 47, 49, 54 
 
 of petroleum, Table 19 32 
 
 of petroleum oil. Table 20 32 
 
 of water. Table 33 60 
 
 Analysis of water 57 
 
 of wood. Table 15 26 
 
 Anheuser-Busch Brewery (Illustration) 123 
 
 Asphalt -.-. 25 
 
 Composition of 26 
 
 Athletic Club Building (Illustration) ' 151 
 
 Bagasse 29 
 
 Bends. Loss of head due to 66 
 
 Beta Dredge Boat (Illustration) 35 
 
 Betz Building (Illustration) 73 
 
 Boilers. Cast-iron end connections (Illustration) 148 
 
 Effect of oil in 61 
 
 Energy stored in. Table 47 80, 82 
 
 Relation to radiating surface 88 
 
 Rating of „ 68, 79 
 
 Boiler. Horse power 79 
 
 Boiler Plant. A modern 124 
 
 A modern, the boiler .127 
 
 A modern, the chimney 125 
 
 A modern, the furnace 126- 
 
 Boiler Tests. Code of rules for 99 
 
 Starting and stopping the test 99- 
 
 Starting and stopping the test, standard method 99 
 
 Starting and stopping the test, alternate method 99 
 
 During the test , 101 
 
 During the test, conditions 101 
 
 During the test, records 101 
 
 During the test, priming tests 101 
 
 Analyses of gases , 102' 
 
 Measurement of air supply 102 
 
 Form of record. Table 58 102 
 
 Reporting the trial. Table 59 102, 103, 104 
 
 Boiler to contents of building. Relation of. Table 52 88 
 
 to radiating surface. Relation of 88^ 
 
 Boiler Tubes. Standard sizes, Table 87 164 
 
 Boiling points of substances. Table 4 8^ 
 
 Bowling Green Building (Illustration) 165 
 
 Bridge Mill and Power Co. (Illustration) 30' 
 
 British and foreign coals. Composition of. Table 13 22 
 
 British thermal unit 5 
 
 Broad Street Station, Philadelphia (Illustration) 81 
 
 Broadway and Seventh Avenue Cable Railway Boilers (Illustration) 90' 
 
 Brown's Palace Hotel (Illustration) : 16 
 
 Buildings heated by steam 83 
 
 Calorific values of different gases 45 
 
 Cape Town Tramways Co. (Illustration) 94- 
 
 Carnegie Building (Illustration) 23 
 
 Cast-iron end connections on sectional boilers (Illustration) 148 
 
 Central Distillery (Illustration) 120': 
 
 Circles. Diam. and circum. and contents at one foot depth. Table 72 154 
 
 —182— 
 
**>*' 
 
 *r^ 
 
 «,.-r- 
 
 Vv. 
 
 •fP** **«fr 
 
 'V 
 
 tx 
 
 
 
 
 
 V. 
 
 V. 
 
 V. 
 
 '^^ 
 
 *>«». 
 
 w 
 
 
 --J 1^ IT' ^- T^' -r^ IT 
 
 I 
 
 --•.~ >» 
 
 Marquette Building, 
 
 CHICAGO, ILL. 
 
 Contains looo H. P. of Heine Boilers. 
 
Page. 
 
 Circles. Diam. and circum., Table 71 153 
 
 Chimneys and draft 109 
 
 Chimney. Formulae 116 
 
 Gases, weight and volume, Table 65 112 
 
 Gases, velocit}' 114 
 
 Chimney at Omaha and Grant S. and R. Wks. (Illustration) 110 
 
 Chimney. Example of an iron (Illustration) 113 
 
 Chimney of the Union Depot Ry. Co. (Illustration) 117 
 
 Chimney, sizes of. Table 68 ...119 
 
 City and County Building (Illustration) 56 
 
 Coal. A short histor}- of 17 
 
 Classification of 19 
 
 Combustion of 24 
 
 Composition of American, Table 12 20, 21 
 
 Composition of British and Foreign, Table 13 22 
 
 Composition of French, Table 14 24 
 
 Coal Mined in the United States, Table 11 19 
 
 Coal. Weights and measures of 19 
 
 Wood equivalent of 28 
 
 Combustible. Fvap. power of one pound of 14 
 
 Heating power of one pound of 14 
 
 Combustion 13 
 
 Air consumed in 13 
 
 Conditions for complete 13 
 
 data, Table 8 : 13 
 
 and volume of products. Temp, of, Table 10 16 
 
 of coal 24 
 
 of fuel. Air consumed 13 
 
 of gas. Resultant gases. Table 25 48 
 
 Volume of gaseous products of 14 
 
 Condensation. Cylinder, Table 46 77 
 
 Loss due to cylinder. Tables 44, 45 76 
 
 of steam in pipes 106 
 
 of steam in uncovered pipes. Table 60 106 
 
 of steam in covered pipes, Table 61 106 
 
 Condensers 93 
 
 Amount of water required b}^ 95 
 
 Contents of buildings. Relation of boiler to. Table 52 88 
 
 Cost of fuel gases, Tables 28, 31 49, 52 
 
 Covering for pipes, Table 61 107 
 
 Cylinder condensation. Table 46 77 
 
 Ivoss due to, Tables 44, 45 76 
 
 Decimals of a square foot in square inches, Table 78 159 
 
 Denver Cons. Flee. Light Co. (Illustration) 108 
 
 Description of Heine Boiler 134 
 
 Draft 109 
 
 reduction by friction. Table 69 119 
 
 Dredge Boat Beta (Illustration) 35 
 
 Dryness of steam in Heine Boiler 149 
 
 Duty of pumping engines 91, 92 
 
 Edison Illuminating Co. Station (Illustration) 173, 174 
 
 Effect of oil in boilers 61 
 
 Electrical unit of power 5 
 
 Energy stored in steam boilers. Table 47 80, 82 
 
 Engines. Comparison of 79 
 
 Duty of pumping 91, 92 
 
 Horse power of 95 
 
 Schichau (Illustration) 161 
 
 Weight of feed water required for. Tables 38, 39, 55 68, 69, 92 
 
 Equitable Building (Illustration) 105 
 
 Erection of Heine Boilers 136 
 
 Evaporative power of one pound combustible, Table 9 14, 15 
 
 of different gases. Tables 24, 26, 30 47, 48, 50 
 
 Expansion of solids, Table 6 10 
 
 in Heine Boilers 148 
 
 N. K. Fairbank's Works (Illustration) 18 
 
 Factors of Evaporation, Table 70 152 
 
 Forresters' Temple (Illustration) 67 
 
 Friction in flues 119 
 
 Fusible plugs. Table 5 8 
 
 Feed Pipes. Loss of pressure in, Table 36 65 
 
 —184— 
 
Page. 
 
 Feed Pipes. Rate of flow of water in, Table 35 64 
 
 Size of boiler 65 
 
 Feed Pump. Example of pressure on ])lunger of 66 
 
 Feed Water. Per cent of savinj^ by heating, Table 40 70 
 
 Feed water required for engines. Weight of, Tables 38, 39 68, 69 
 
 Firing. Modes of 25 
 
 Fractions of an inch in decimals. Table 75 156 
 
 French coals. Composition of, Table 14 24 
 
 French and English units of power. Relation of, Table 2 6 
 
 compound units of power. Relation of. Table 3 6 
 
 French and U. S. measures of length, Table 79 160 
 
 measures of liquid, Table 82 161 
 
 measures of surface. Table 80 160 
 
 measures of volume, Table 83 161 
 
 measures of weight, Table 81 160 
 
 Fuel. Advantages of oil as a 32 
 
 Air consumed in combustion of .* 13 
 
 Conditions for complete combustion of 13 
 
 Gas 44 
 
 Gas. Cost of. Table 28 49 
 
 Heat evolved by various. Table 9 15 
 
 Liquid 31 
 
 Oil as a 32 
 
 Saving by heating feed water. Table 40 70 
 
 Tests with 36, 43 
 
 Gas. Analysis of natural. Table 32 54 
 
 Analysis of water. Table 29 , 49 
 
 Composition of fuel. Tables 22, 23 45, 46 
 
 Cost of fuel, Table 28 : 49 
 
 Cost of water. Table 31 52 
 
 Estimate of cost of fuel 52 
 
 Fuel 44 
 
 Natural 52, 53 
 
 Oxygen absorbed and CO2 produced by. Table 27 48 
 
 Relative values of fuel. Table 21 45 
 
 Resultant gases of combustion of. Table 25 48 
 
 Test of water. Table 30 50 
 
 Gas. Water evaporated by. Table 26 48 
 
 Water evaporated by. Table 24 47 
 
 Gases produced from combustion of one pound wood. Table 16 28 
 
 Velocity in chimney 114 
 
 Gases. Weight and volume of chimney, Table 65 112 
 
 Grand Republic Mills (Illustration) 12 
 
 Heat 5 
 
 and power, units and relation of. Tables 1, 2, 3 6 
 
 as a form of energy 5 
 
 evolved.by various fuels, Table 9 15 
 
 Measures of 5 
 
 Heat of expansion. Latent 7 
 
 Heat of combustion of straw and tan bark 31 
 
 Heat. Sensible and latent 7 
 
 Specific, Table 7 11 
 
 Heat transformations 6 
 
 Heat transmitted by radiating surfaces. Table 51 87 
 
 per square foot of surface. Table 48, diagram 84 
 
 per square foot of brick wall, Table 49 85 
 
 Heath & Milligan Mfg. Co. (Illustration) 180 
 
 Heating air 83 
 
 buildings by steam 83 
 
 feed water. Per cent of saving. Table 40 70 
 
 liquids by steam 88 
 
 water by steam 89 
 
 power of one pound of combustible 14 
 
 Heine Safety Boiler (Illustration) 135 
 
 Heine Boilers at Anheuser-Busch Brewery (Illustration) 170 
 
 at Allegheny Traction Co. (Illustration) 69 
 
 at Broadway and Seventh avenue Power House (Illustration) 90 
 
 at Central Distillery (Illustration) 120 
 
 at People's Railway Power House (Illustration) 51 
 
 at Union Depot Railway Plant (Illustration) 128 
 
 at World's Fair (Illustration) 4 
 
 at Orleans Traction Co. (Illustration) 21 
 
 —185— 
 
Page. 
 
 Heine Boilers at Chicago Pvdison Station (Illustration) 9 
 
 being moved (Illustration) 44, 62, 94, 104 
 
 over puddling furnace (Illustration) 144 
 
 Heine Boiler. 150 horse power (Illustration) 78 
 
 375 horse power (Illustration) 133 
 
 500 horse power (Illustration) 54 
 
 Absorption and transmission of heat in : 142 
 
 Description of 134 
 
 Dryness of steam in 149 
 
 Erection and walling in of .136 
 
 Expansion in 148 
 
 Longitudinal section of (Illustration) 139 
 
 Operation of 138 
 
 Precipitation and discharge of impurities in 150 
 
 Safety at high pressures 146 
 
 ^ Section of water leg (Illustration) 137 
 
 Separation of water in 149 
 
 Specifications for boiler plates 146 
 
 Superiority of 142 
 
 Tests of 43, 98 
 
 Helios 1 
 
 Hotel Majestic (Illustration) 100 
 
 Horse power of boilers 68, 72, 79 
 
 of engines 95 
 
 of pumping engines 91 
 
 Hoster Brewing Co. (Illustration). 169 
 
 Impurities in Heine Boilers. Precipitation and discharge of 150 
 
 in water 55 
 
 Inch in decimals. Fractions of. Table 75 156 
 
 in decimals of a foot. Table 76 157 
 
 in decimals of a square foot. Square, Table 77 158 
 
 Incrustation. Causes of 55, 58 
 
 Effects of 57, 59 
 
 Means of preventing 57, 58, 59 
 
 Independence Mine (Illustration) 27 
 
 Iron. Weight of round and square, Table 74 156 
 
 Kansas City Waterworks (Illustration) 80 
 
 Latent and sensible heat 7 
 
 Latent heat of expansion 7 
 
 Length. French and U. S. measures of. Table 70 160 
 
 Lignite and asphalt 25 
 
 Lignite. Composition of 26 
 
 Liquid fuels 31 
 
 Liquid. French and U. S. measures of, Table 82 161 
 
 Heating by steam 88 
 
 List of Heine Boiler plants 166 
 
 Longitudinal section of Heine Boiler (Illustration) 139 
 
 Loss of head in pipes due to bends 66 
 
 of pressure in feed pipes. Table 36 65 
 
 Mallinckrodt Building (Illustration) 83 
 
 Marquette Building (Illustration) 183 
 
 Mean effective pressure, diagram. Table 56 96 
 
 Measurement of water 64 
 
 Measures of heat 5 
 
 Mechanical unit of power 5 
 
 Melting points of metals and solids. Table 5 8 
 
 Metal plates. Weight of. Table 73 155 
 
 Minneapolis Exposition (Illustration) 97 
 
 Modes of firing 25 
 
 Motion of steam 74 
 
 Municipal and County Building, Toronto (Illustration) 33 
 
 Natural Gas 52, 53 
 
 Analysis of, Table 32 54 
 
 New Planters' House (Illustration) 63 
 
 Oil as a fuel 32 
 
 Advantages of 32 
 
 Oil in boilers. Effect of 61 
 
 Operation of Heine Boilers 138 
 
 —186— 
 
Page. 
 
 Orleans Traction Co. (Illustration) 21 
 
 Outflow of steam, Tables 42, 43 .'. 74 
 
 Peoria Water Works (Illustration 176 
 
 Petroleum. Composition of, Table 19 32 
 
 Petroleum oils. Composition of. Table 20 32 
 
 Philadelphia and Reading R. R. Station (Illustration) 46 
 
 Pipe coverings. Table 61 107 
 
 Pipes. Condensation of steam in 106 
 
 Condensation of steam in, uncovered, Table 60 106 
 
 Condensation of steam in, covered, Table 61 106 
 
 Loss of pressure in feed, Table 36 65 
 
 Loss of head due to bends in. Table 37 66 
 
 Rate of flow of water in, Table 35 65 
 
 Size of boiler feed 65 
 
 Standard sizes of gas and water. Table 84 162 
 
 Standard sizes of extra strong gas and water. Table 85 163 
 
 Standard sizes of double extra strong gas and water, Table 86 164 
 
 Plant. A modern boiler 124 
 
 Plants. List of Heine Boiler 166 
 
 Artificial ice and refrigerating companies 168 
 
 Breweries and distilleries 171 
 
 Cable and electric street railway companies 172 
 
 Electric light, power and gas companies 174 
 
 Flour mills 168 
 
 Hotels, offices and public buildings 166 
 
 Iron and steel manufacturers 167 
 
 Iron furnaces 177 
 
 Mining, coal and smelting companies 177 
 
 Miscellaneous 178 
 
 Packing houses 178 
 
 Rice and oil mills 172 
 
 Sugar plantations 171 
 
 Water works 176 
 
 Plates. Specification for boiler 146 
 
 Plugs. Fusible, Table 5 8 
 
 Power. Concentration and distribution of 121 
 
 Electrical units of 5 
 
 Mechanical units of 5 
 
 Relation of units of. Table 1 6 
 
 Relation of French and U. S. units of. Table 2 6 
 
 Relation of French and U. S. compound units of, Table 3 6 
 
 Water 5 
 
 Pressure. Mean effective 96 
 
 Mean effective, diagram, Table 56 96 
 
 Pulaski Iron Works (Illustration) 86 
 
 Pump. Example of pressure on plunger of 66 
 
 Pumping engines. Duty of 91, 92 
 
 Feed water required by. Table 55 92 
 
 Horse power and steam consumption of 91 
 
 Radiating surface. Heat transmitted by, Table 55 87 
 
 Rating of boilers 68, 72, 79 
 
 Relation of boiler to contents of building, Table 52 88 
 
 of boiler to radiating surface 88 
 
 of units of power. Tables 1, 2, 3 6 
 
 Relative values of fuel gases. Table 21 45 
 
 Safety at high pressures of Heine Boilers 146 
 
 Safety valves 89 
 
 Philadelphia rule for 91 
 
 b}' Philadelphia rule. Dimensions of, Table 54 91 
 
 United States rule for 89 
 
 Saturated steam. Properties of. Table 41 72 
 
 Scale (see Incrustation) . 
 
 Section of Heine Boiler (Illustration) 139 
 
 of water leg of Heine Boiler (Illustration) 137 
 
 Sectional boilers. Cast-iron end connections (Illustration) 148 
 
 Sensible and latent heats 7 
 
 Separation of water in Heine Boilers 149 
 
 Schichau engine (Illustration) ...., 161 
 
 Sizes of feed pipes 65 
 
 Sizes of chimneys, Table 68 118 
 
 —187— 
 
Page. 
 
 Solids. Expansion of, Table 6 10 
 
 Melting points of metals and, Table 5 8 
 
 Specific heat. Table 7 11 
 
 Specifications for boiler plates for Heine Boilers 146 
 
 Square feet in square inches. Decimals of. Table 78 159 
 
 Square inches in decimals of a square foot. Table 77 158 
 
 Stacks (see Chimneys). 
 
 Standard sizes of boiler tubes, Table 87 164 
 
 of gas and water pipes. Tables 84, 85, 86 162, 163, 164 
 
 Steam 71 
 
 Condensation in pipes. Tables 60, 61 106 
 
 Heating buildings by 83 
 
 Heating liquids by 88 
 
 Heating water by. Table 53 89 
 
 in Heine Boilers. Dryness of 149 
 
 Motion of 74 
 
 Outflow of, Tables 42, 43 74, 75 
 
 Properties of saturated. Table 41 72 
 
 Superheated 76 
 
 Value of dry 75 
 
 Straw 31 
 
 Composition of. Table 18 31 
 
 Heat of combustion of 31 
 
 Substances. Boiling point of. Table 4 8 
 
 Surface. French and United States measures of. Table 80 160 
 
 Relation of boiler to radiating 88 
 
 Transmission of heat by radiating, Table 51 87 
 
 Superheated steam 76 
 
 Superiority of Heine Boilers 142 
 
 Tan bark 31 
 
 Temperature of combustion. Table 10 16 
 
 Tests of Heine Boilers, Table 57 98 
 
 of steam boilers. Code of rules (see Boiler Tests) 99 
 
 Toronto Municipal and County Buildings (Illustration) 33 
 
 Transmission of heat by radiating surfaces. Table 51 87 
 
 Tubes. Standard sizes of boiler, Table 87 164 
 
 Unit. British thermal 5 
 
 Units of heat and power, Tables 1, 2, 3 6 
 
 of power. Mechanical 5 
 
 of power. Electrical 5 
 
 United States and French measures of length. Table 79 160 
 
 measures of liquids. Table 82 161 
 
 measures of surface. Table 80 160 
 
 measures of volume, Table 83 161 
 
 measures of weight. Table 81 160 
 
 Valves. Safety 89 
 
 Safety, Philadelphia rules for 91 
 
 Safety, dimensions of by Philadelphia rules, Table 54 91 
 
 Safety, United States rules for 88, 91 
 
 Velocity of chimney gases 114 
 
 Ventilation. Amount of air necessary for. Table 50 87 
 
 Volume of gaseous products of combustion 14 
 
 French and United States measures of, Table 83 161 
 
 Walling in of Heine Boilers 136 
 
 Washburn Flour Mill (Illustration) , 40 
 
 Water 55 
 
 Water. Analysis, Table 33 60 
 
 Commercial analysis of 57 
 
 Water Gas. Analysis, Table 29 49 
 
 Cost, Table 31 52 
 
 Water. Heating feed. Table 39 69, 70 
 
 Heating by steam, Table 53 89 
 
 Impurities in 55 
 
 Leg of Heine Boilers (Illustration) 149 
 
 Loss of pressure in pipes, Table 36 65 
 
 Measurement of 64 
 
 Power 5 
 
 Rate of flow in pipes, Table 35 65 
 
 required per horse power 55, 68, 69 
 
 required by condensers 95 
 
 —188— 
 
PaKC. 
 
 Water. Weight of 55, 64, 72 
 
 Weight required for engines, Tables 38, 39 68, 69 
 
 Weight. French and United States measures of, Table 81 160 
 
 and measures of coal 19 
 
 of metal plates, Table 73 155 
 
 of square and round Iron, Table 74 156 
 
 of water 56, 64, 72 
 
 of wood, Table 17 28 
 
 Wood 26 
 
 Composition of. Table 15 26 
 
 equivalent of coal 28 
 
 Gases from the combustion of one pound, Table 16 28 
 
 Weight of. Table 17 28 
 
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