FIVE YEARJ 
 QUESTIONS AND ANSWERS 
 
 NATIONAL ASSOCIATION OF 
 STATIONARY ENGINEERS 
 
 V - ; i :
 
 National Association of 
 Stationary Engineers 
 
 Five Years Questions 
 and Answers 
 
 As originally published in The 
 National Engineer 
 
 VOLUME TWO 
 
 First Edition 
 
 Chicago: 
 
 P. F. PETTIBONE & CO., Printers 
 1908
 
 Copyright 1908 
 
 by 
 FREDERICK. W. RAVEN, Nat'l Sec'y
 
 FOREWORD 
 
 This volume contains the Questions and Answers of the course 
 carried on by the National Educational Committees of the National 
 Association of Stationary Engineers during the years 1902 to 1906, 
 inclusive. 
 
 It is practically volume 2 of the work so widely and favorably 
 known as the "Five Years' Questions and Answers," published by 
 the National Association of Stationary Engineers in 1902. 
 
 The object of this volume is to present information for engi- 
 neers in such a manner as will convey the necessary information 
 clearly and yet concisely. 
 
 There has been added to the regular educational work, a series 
 of tables which of themselves form a modest work of reference. 
 
 This volume was compiled by the National Educational Com- 
 mittee for 1907-1908. Messrs. Chas. W. Naylor, Otto Luhr and 
 F. J. Roos, all of Chicago, and members of Illinois Nos. 28, 38 
 and 2, respectively.
 
 NATIONAL ASSOCIATION OF STATIONARY ENGINEERS. 
 
 QUESTIONS AND ANSWERS 
 
 1902-1906. 
 
 Engines. 
 
 Q. 1. Describe, in a general way, a simple slide-valve engine. 
 
 Ans. 1. A simple slide valve engine has three port openings, one for ex- 
 haust steam, and two for the admission of steam to each end of the cylin- 
 der. The slide valve is so fitted, then when at the center of its travel, it 
 covers both steam and exhaust ports; it is actuated by means of a valve 
 rod and an eccentric rod driven by an eccentric, the latter being mounted 
 upon the engine shaft. The motion of the eccentric communicated to the 
 valve moves the latter so that when steam is being admitted to one end 
 of the cylinder, the other end of the cylinder is open to the exhaust port; 
 this operation taking place twice in each revolution. 
 
 Q. 2. How early is it possible to cut off steam on this type of en- 
 gine, and what limits early cut-off! 
 
 Ans. 2. Steam cannot be cut off earlier than half stroke in this type 
 of engine. The reason for this is that the valve has to perform the double 
 function of admitting as well as exhausting the steam, and in order to do 
 this properly for both strokes of the engine the eccentric must be placed 
 at a 90 degree angle from the crank; the relative positions of eccentric 
 and crank preventing an earlier point of cut-off than one-half stroke. 
 
 Q. 3. How may cut-off and compression be changed in a simple slide- 
 valve engine? 
 
 Ans. 3. (a) Cut-off may be made earlier by increasing the outside 
 lap. 
 
 (b) Cut-off may be made later by decreasing outside lap. 
 
 (c) Compression may be made greater by increasing the inside lap. 
 
 (d) Compression may be lessened by decreasing the inside lap.
 
 Q. 4. Define clearance and explain its effect on the economy of the 
 engine. 
 
 Ans. 4. Clearance includes all space between the piston and cylin- 
 der head when piston is at the extreme point of travel, a ; so the space of 
 passages for the admission of steam between admission valve and cylin- 
 der, and between cylinder and exhaust valve. 
 
 These spaces must be filled with steam every stroke, and as the steam 
 used to fill the clearances does no appreciable amount of work it is con- 
 sidered as a loss. In other words, the greater the clearances the greater 
 the loss. 
 
 Q. 5. What is the object of having a valve riding on the back of a 
 slide-valve and in what way does it affect the valve-gear of the engine? 
 
 Ans. 5. The object of having one valve ride on the back of a slide 
 valve is to secure a point of cut-off earlier than half stroke. This is ac- 
 complished by having each valve driven by a separate eccentric; the rid- 
 ing valve determining the point of cut-off while the main valve controls 
 the admission and exhaust to and from the cylinder. 
 
 Q. 6. If a properly proportioned slide-valve is so set as to give too 
 much lead on one end and none on the other, what effect will it have on the 
 operations of the valve and what will remedy it? 
 
 Ans. 6. It will make the cut-off late and the compression early on 
 the end having excessive compression, and the cut-off early and compres- 
 sion late on the other end. 
 
 The remedy is to shorten or lengthen the valve stem as the case may 
 require. 
 
 Q. 7. What is understood by the term "a balanced slide-valve?" 
 
 Ans. 7. A balanced slide valve is one with surfaces so arranged that 
 the steam in the steam chest acts to balance the valve, preventing the 
 steam from pressing the valve on its seat, as is the case with a plain slide 
 valve. 
 
 Q. 8. State what advantage, if any, there is in using the forced system 
 of lubrication on engines, for both internal and external work. 
 
 Ans. 8. The advantage of forced feed of lubrication is the saving 
 in oil; positive feed and more uniform. 
 
 Q. 11. What is the difference between a piston valve and a flat slide 
 Talvef 
 
 Ans. 11. A piston valve consists of one or more pistons, without 
 packing, mounted upon a rod or spindle, and usually designed to cor- 
 respond with annular spaces in valve chests. In construction this type 
 of valve may be either single or multiported, it may or may not have 
 lead or lap, and is generally considered as being balanced.
 
 A flat or slide valve is made in one piece, and has one or more cham- 
 bers on the. inner face, and is commonly known as a D. or B. valve. Its 
 design is such that it controls the admission, cut-off, compression and re- 
 lease of the steam, and is not balanced. 
 
 Q. 12. What are the advantages of a four-valve engine, and a plain 
 slide valve engine! 
 
 Ans. 12. The advantages of a four-valve engine are as follows: 
 
 Good distribution of steam, resulting in better economy, due to the 
 independent action of each valve relative to opening and closing. 
 Cylinder drainage is well-nigh perfect owing to the position of the ex- 
 haust valves being at the bottom of the cylinder, as in the Corliss type 
 of engine. Full benefit of expansion of the steam, by admitting it at 
 approximately boiler pressure and maintaining same up to point of cut- 
 off, which is always automatic and proportionate to tbe load of the en- 
 gine. This type possesses the advantage of being easily started or 
 etopped and is easily manipulated. 
 
 The advantages of a plain slide valve consist of its low first cost, 
 ite mechanical simplicity, ease of putting it together, adaptability to 
 portable outfits, quiet running under light loads owing to the fixed point 
 of compression, and ease of maintenance. 
 
 Q. 13. (a) Describe a gridiron valve. 
 
 (b) Describe a poppet valve. 
 
 (c) Describe a Corliss valve. 
 
 Ans. 13. (a) A gridiron valve is a slide valve having one or more 
 parts, arranged to correspond with the ports leading to the cylinder, and 
 designed to give a short travel and rapid movement in opening. It is 
 classed as a multiported valve. 
 
 (b) A poppet valve consists of one or more discs mounted on a stem 
 or spindle, and in operation moves in a vertical plane, raising and drop- 
 ping over the corresponding valve seat or seats. 
 
 (c) A Corliss valve, as the name is now applied, consists of the seg- 
 mental parts of a cylindrical casting which is made to partly rotate in 
 a circular chamber; and is called a semi-rotative valve. The construction 
 may be either of single or multiported design, or may be arranged to ad- 
 mit steam through an opening in its center. 
 
 Q. 14. What range of cut-off is permissible on a four-valve engine, 
 where all valves are operated by one eccentric? 
 
 Ans. 14. In a four-valve engine of the Corliss type, for example, 
 where all the valves are operated by one eccentric, the range of cut-off 
 will be from zero to about one-half stroke. 
 
 Q. 15. With a single eccentric, as mentioned in the preceding ques- 
 tion, why cannot a long range of cut-off be obtained? 
 
 Ans. 15. Because the eccentric being set 90 degrees ahead of the 
 crank, reaches the extreme poir.t of its throw by the time the piston ha?
 
 reached the half-stroke, therefore cut-off must occur before that time. 
 Owing to the angularity of the connecting rod, however, it is possible to 
 have the cut-off occur later than half-stroke, particularly on the head 
 end of the engine. If the steam valves are set "late" it will also serves 
 to give a late cut-off. 
 
 Q. 16. How may a four-valve engine, with two eccentrics, be ad- 
 justed to obtain a late point in cut-off? 
 
 Ans. 16. A late point of cut-off may be obtained by taking the lap 
 off the steam valve and setting back the steam eccentric. 
 
 Q. 17. Describe a force feed method for lubricating steam engine, 
 pump or air compressor (steam end) cylinders. 
 
 Ans. 17. A force feed lubricator consists of a mechanically oper- 
 ated pump to force the oil into the feed pipes leading into the steam chest 
 and cylinders, the pump is operated by connecting to some moving part 
 of the engine and the pump can be adjusted to feed the required amount. 
 
 Q. 18. Enumerate some of the advantages to be derived from a point 
 of cut-off late in the stroke. 
 
 Ans. 18. It allows taking care of overloads under the control of the 
 governor. 
 
 Q. 19. Under what conditions would it be more economical to operate 
 a single cylinder, non-condensing engine, than a cross compound, 
 condensing engine, assuming the load to be 500 h. p., the run each day to 
 be nine hours? 
 
 Ans. 19. It would be more economical to run single cylinder and non- 
 condensing engine. When you have to buy water for your condenser and 
 where you can use the exhaust steam for heating purposes, dry kilns, etc. 
 
 Q. 20.' What closes the steam valves of a detachable valve gear en- 
 gine? 
 
 Ans. 20. Steam pressure on area of valve, steam vacuum dash pots, 
 springs, and weight dash pots. 
 
 Q. 21. Give five reasons, any one of which may cause a fly ball type 
 or steam engine governor to fail to regulate the speed of the engine. 
 
 Ans. 21. Five reasons for a fly ball governor not working would be: 
 
 1. Belt break or fly off. 
 
 2. Packing too tight on stem. 
 
 3. Pin in Governor too short. 
 
 4. Bevel gear loose on pulley shaft. 
 
 5. Dash pot out of order.
 
 Q. 22. Why are not detachable valve gears used on high speed en- 
 jfinesf 
 
 Ans. 22. They would not be able to engage when running faster 
 than 100 R. P. M. 
 
 Q. 23. If you were running a four valve engine non-condensing and 
 desired to have same run condensing, what change in the valve setting 
 would you make? 
 
 Ans. 23. Close the exhaust valves earlier in the stroke, giving almost 
 twice as much compression. 
 
 Q. 24. What effect would changing from non-condensing to con- 
 densing have on the engine, in relation to its developing power f What 
 would be the effect from an economy standpoint and whyf 
 
 Ana. 24. It would depend on what the cooling water cost. When 
 water can be obtained at little cost there is from 10% to 25% saved on 
 fuel. 
 
 Q. 25. Is the crosshead pressure greater on the guide of a vertical 
 engine than on a horizontal engine? Give reasons. 
 
 Ans. 25. It should have read, "No, except the weight of piston rod, 
 crosshead and connecting rod." 
 
 Q. 26. How does the length of the connecting rod as compared with 
 that of the crank affect the pressure of the crosshead upon the guide? 
 
 Ans. 26. A short connecting rod causes a greater strain on cross- 
 heads. The usual length of connecting rod is about five or six times the 
 length of crank. 
 
 Q. 27. How would you disconnect a crosshead from a piston rod where 
 the connection between both was by means of a key? 
 
 Ans. 27. Remove the key. Place the engine on crank end dead cen- 
 ter. Connect a pump with crank end of cylinder and force the rod out 
 of the crosshead with hydraulic pressure. 
 
 CORRECTIONS. 
 
 The following is a correction in the answer to question No. 27, as it 
 appeared in the March number of The National Engineer: 
 
 Remove the key; then by the use of a male and female gib, with taper 
 key between them, inserted in slot with male gib next to the crosshead. 
 A few sharp blows with a hammer will start the crosshead off the pin. 
 Another way is to remove the crosshead pin and insert a press as follows : 
 Take a piece of round iron as large as will go in pinhole with a hole 
 drilled and tapered as large as possible. Make a long thread screw so it 
 will reach from end of piston rod in crosshead out far enough to get a 
 wrench on, and then you can press off most any crosshead made.
 
 Q. 28. Is lead necessary iu a, steam engine! 
 
 Ans. 28. In a pump without a fly wheel or in a steam hammer lead 
 is desirable and in a very slow running engine it may be useful but in 
 the ordinary type of engines, lead is not necessary as the momentum of 
 the rotating parts will move the piston forward until the valve can open 
 and put steam into the cylinder. 
 
 Q. 29. Given two engines using, respectively, 15 and 30 pounds of 
 stoam per indicated horse power: All other conditions being the same, 
 which engine will show the greater increase in economy, when using steam 
 with 150 degrees superheat? 
 
 Ana. 29. The engine that uses the greatest weight of steam per in- 
 dicated horse power will be benefited the most when using steam with 
 150 F superheat, because the volume of steam required is the same in 
 any engine all other conditions being equal. 
 
 Q. 30. What pressure should there be in the receiver of a non-con- 
 densing, cross-compound engine, when the engine is running at one-half its 
 rated speed and without load? 
 
 Ans. 30. None that could be indicated by a steam gauge. 
 
 Q. 31. What examination of an engine should an engineer make, on 
 assuming charge of same, to assure himself that it is in condition to 
 operate properly? 
 
 Ans. 31. An engineer on taking charge of a strange plant should 
 make a sufficiently thorough examination to ascertain if the engine is in 
 fair working order. Such examination should include testing the piston 
 for leakages, examination of the cylinder for evidences of cutting or 
 scoring, testing valves for leakages and general condition as to wear, 
 etc., inspecting the adjustment and condition of all bearings, noting 
 valve adjustments and connections, turning engine over by hand to ascer- 
 tain clearance spaces of piston, carefully examining the oiling devices for 
 both internal and external lubrication, and inspecting the governor to see 
 if it is in proper working order. After thorough examination, with the 
 engine at rest, steam should be admitted to warm cylinder, after which 
 the engine can be started slowly and gradually brought up to speed. 
 
 Q. 32. How would you determine whether an engine connecting rod 
 was of the correct length to give an equal clearance at each end of the 
 engine cylinder? 
 
 Ans. 32. Disconnect the connecting rod from crosshead and place the 
 piston at the extreme end of cylinder. While piston is in this position 
 make a corresponding mark on the guide and crosshead for reference. 
 Then place piston at other extreme end of cylinder, and likewise place 
 a corresponding mark on guide and crosshead to designate point of ex- 
 treme travel. Now connect up the connecting rod, and place engine on 
 
 10
 
 one center. Then carefully note the difference in extreme travel of piston 
 as compared with the marks previously made on crosshead and guide. 
 Place engine on other center and repeat operation. In this way the 
 clearance at each end may be readily ascertained. If the amount is 
 greater on. one end than on the other, it may be equalized by one of two 
 methods. If the piston rod is screwed into the crosshead, and secured 
 by jam or lock nuts, the rod may be turned around a sufficient number 
 of times, either forward or back, to bring the piston to a position that 
 will equalize the clearances; it being understood, of course, that there 
 is a limit to the number of turns a rod should be moved in either direc- 
 tion. In turning the rod around care should be taken to see that the 
 piston does not have to assume a new position in relation to its wearing 
 places in the cylinder; in other words, the rod should "DC turned fully one 
 complete turn and not fractional parts of same. 
 
 Where the piston rod is attached to the crosshead by means of fixed 
 key or wedge, the equalization of clearance spaces may be brought about 
 by using shims at the stub ends of the connecting rod. 
 
 Q. 33. (a) What is a throttling governor? 
 
 (b) What is an inertia governor f 
 
 (c) What is meant by "governor range"! 
 
 Ans. 33. (a) In a governor of the fly-ball type so constructed that 
 when the engine attains more than a specified speed, the fly-balls are 
 forced outward, thereby forcing a spindle attached to a valve downward, 
 and by this action reducing the pressure of the steam admitted to the 
 cylinder, and partially shutting off the steam until the engine resumes 
 its normal speed, when the governor assumes a different plane, either 
 high or low, depending upon the amount of steam needed to keep engine 
 up to speed. 
 
 (b) An inertia governor is of the shaft or wheel type and is 
 usually placed within or adjacent to one of the driving or balance wheels 
 of the engine. When the shaft is turning at a constant speed, the only 
 forces tending to make the governor weights change their position rela- 
 tively are: First, centrifugal force; second, the pulling action of a springj 
 and third, resistances due to the connection of the governor weights with 
 the eccentric, and these latter must be in equilibrium. As soon, how- 
 ever, as the speed of the governor shaft and governor wheel changes, the 
 tendency of the governor weight or weights to continue at the same speed 
 in consequence of inertia, comes into play, and the accelerating forces 
 are thus developed which may aid or oppose the centrifugal action, de- 
 pending on the design of the governor. 
 
 (c) Long range governors control the point of cut-off from zero to 
 about 7/10 of the stroke, while short range governors control from zero 
 to about V> stroke. 
 
 Q. 34. Explain the difference between automatic cut-off, and throt- 
 tiing-governed engines, also the advantages of one method over the other. 
 
 Ans. 34. The difference between a throttling governor and an au- 
 tomatic governor is that the former reduces the steam pressure accord- 
 ing to the load, while the volume of steam admitted to the cylinder re- 
 mains constant, thus causing a wire-drawing action; whereas, with the 
 automatic type, steam at approximately boiler pressure is admitted to 
 the cylinder up to the point of cut-off, this point being determined by the 
 governor according to the engine load, and the remainder of the stroke 
 completed by expansion, making the latter method the more economical 
 in the use of steam. 
 
 11
 
 Q. 35. Regardless of design, into how many classes are steam en- 
 gines divided? 
 
 Ans. 35. Condensing and non-condensing. 
 
 Q. 36. What advantage is it to have two eccentrics on a condens- 
 ing engine f 
 
 Ans. 36. The use of two eccentrics permits of having the steam 
 and exhaust valves separately actuated, and in such a manner as to per- 
 mit of range of cut-off being independent of the opening and closure 
 of exhaust valves, thus allowing the latter to be set to secure any de- 
 sired amount of compression. 
 
 Q. 37. What is the difference between a surface condenser and a jet 
 condenser? 
 
 Ans. 37. A surface condenser is so constructed that the exhaust 
 steam does not come into direct contact with the cooling water, but ia 
 condensed by coming into contact with metal surfaces cooled by the cool- 
 ing water. This is generally accomplished by discharging the exhaust 
 steam in a receptacle having a number of small tubes through which the 
 cooling water circulates. Their installation is generally for the two-fold 
 purpose of saving the water of condensation and keeping the latter in 
 good condition for return to the boilers. 
 
 With a jet condenser, the exhaust steam and the cooling water mingle, 
 resulting in quick condensation. In many cases the injection water used 
 renders the combination unfit for boiler feed water. 
 
 , Q. 38. Why do we sometimes fail to realize the proper receiver pres- 
 sure, during the first half -hour's run, of a cross-compound condensing 
 engine? 
 
 Ans. 38. Leaks in L. P. valves which take up when all parts get hot. 
 
 Q. 39. What is a compound engine? 
 
 Ans. 39. A compound engine is one which expands steam in two or more 
 cylinders. If expanded in three cylinders it is called a triple expansion; 
 if in four cylinders it is called quadruple expansion. 
 
 Q. 40. Why are compound engines used? 
 
 Ans. 40. To obtain the advantage of high pressure steam, and at 
 the same time avoid the losses due to cylinder condensation as much as 
 possible. 
 
 If the steam be allowed to expand in two or more cylinders, the fall 
 in temperature is divided between the cylinders, consequently the loss 
 from condensation is considerably less. 
 
 12
 
 Q. 41. What types and designs of compound engines are in general 
 ef 
 
 Ans. 41. Horizontal, upright, tandem and cross-compound. 
 
 Q. 42. (a) Where no receiver is used in connection with a com- 
 pound engine, at what angle are the engine cranks set, one with the 
 other? 
 
 (b) Where a receiver is used, what will the relative angle of the 
 cranks be, and whyf 
 
 (c) Why are not receivers used in connection with tandem com- 
 pound engines f 
 
 Ans. 42. (a) At the same angle, or at 180. (b) Steam can be 
 taken from the receiver at any angle of the stroke, therefore the cranks 
 may be set at any angle, in relation to one another, (c) Because the 
 steam exhausts from the high pressure to the working side of the low 
 pressure piston. 
 
 Q. 43. What advantage is there in a compound engine over a single 
 engine, where the service conditions are such that the engine must ex- 
 haust against a gauge pressure of five pounds! 
 
 Ans. 43. Not any. 
 
 13
 
 Boilers. 
 
 Q. 1. Which is preferable -a diagonal or a through and through stay? 
 Why? 
 
 Ans. 1. Through and through stays are preferable in so far as 
 strength of the boiler is concerned, as they pull in the direction of the 
 stress, but their use is objected to on account of the inconvenience they 
 cause to any person entering the boiler; for this latter reason diagonal 
 stays are very often preferred. 
 
 Q. 2. Describe what you believe to be the most correct method for 
 conducting an inspection of a horizontal return tubular boiler. 
 
 Ans. 2. The hammer test is most correct but should be done by one 
 of experience so that he can readily detect by the sound whether the 
 braces have the proper tension or whether corroded or pitted or blistered 
 or the plates are sound and should ba tested inside and outside. The 
 hydraulic test may be used in connection if desired. 
 
 Q. 3. What causes a horizontal return tubular boiler to "pulsate" 
 in its setting; a kind of breathing action, as it weref And at what 
 time is such action apt to be discernible f 
 
 Ans. 3. Pulsation of a boiler is caused by weakness and want of 
 capacity in the boiler to supply the necessary quantity of steam, sometimes 
 caused by a boiler being poorly designed. It is discernible most when- 
 ever forcing the fire in order to keep steam at the required point. 
 
 Q. 4. Why are not rivets made larger and spaced farther apart, 
 in order to remove as small an amount of metal as possible. 
 
 Ans. 4. If rivets were spaced farther apart, the plate would spring 
 between rivets when caulking, making it impossible to make the joint 
 steam or water tight. 
 
 Q. 5. How are tubes fastened to boiler heads and made tight? 
 
 Ans. 5. Tubes are fastened to boiler heads by being rolled or ex- 
 panded, and the ends beaded over to form a slight flange, enabling the 
 tube to hold to the heads against the internal pressure in the boiler. 
 
 14
 
 Q. 6. What form of tool is used in caulking seams and why? State 
 effect of using improperly shaped tool. 
 
 Ans. 6. A flat thick chisel with rounded edges is used in caulking 
 seams. A tool of that shape upsets the edges of the plates without cut- 
 ting them. A sharp edged tool would cut the surface of the under plate, 
 and also leave a place liable to be attacked by corrosion. 
 
 Q. 7. How are manholes reinforced? 
 
 Ans. 7. Manholes are reinforced by having a ring of castiron or 
 Bteel of sufficient strength to take the stress off that part of the boiler, 
 riveted to the plate; or by having the plate itself flanged and thus form- 
 ing a strengthening rim around the manhole. 
 
 Q. 8. Why is the wide strap in a double butt strap seam placed on 
 the inside! 
 
 Ans. 8. Triple riveted double butt strap joints have the outside 
 rows of rivets spaced twice as far apart as the other rows, and with one 
 strap wide enough to take in this outside row of rivets. This wide strap is 
 placed on the inside in order that the caulking, which is done on the out- 
 side, may be done on the double sheet and on the straps having the rivets 
 closer together, thus avoiding any springing of the plate. Placing the 
 wide straps on the inside allows the boiler pressure to be exerted on th 
 larger area with less liability to leakage. 
 
 Q. 9. Under average service conditions which is the most economical 
 for boiler feeding, an exhaust injector or an ordinary duplex steam pump! 
 In these cases it is assumed that there is ample exhaust steam to operate 
 the injector, and that the pump delivers water to a feed water heater, 
 which raises the temperature of the water to 190 F. 
 
 Ans. 9. An exhaust injector would be more economical to use above 
 the Duplex feed pump, when you have no special use for the* exhaust 
 steam, of about 15%. 
 
 Q. 10. Why are rivets in double shear not twice as strong as rivets 
 in single shear! 
 
 Ans. 10. It is probable that if the stress could be equally divided be- 
 tween the two shearing sections of the rivets, that rivets in double shear 
 would be twice as strong as the same rivets in single shear, but, owing 
 to the uncertainty of having the stress equally divided, due to imperfect 
 alignment of holes in practical boiler work, it would not be safe to 
 allow for rivets in double shear, more than 185 per cent of the allowable 
 stress for the same rivets in single shear. 
 
 Q. 11. Why are some boiler and tank heads cupped out I 
 
 Ans. 11. Boiler and tank heads are sometimes cupped outward to 
 do away with the necessity of staying. With this form of head the 
 
 15
 
 strength is not wholly dependent on its stiffness, but part of the stresi 
 on the head is tensile strength, which makes this form of head much 
 stronger than a flat head. 
 
 Q. 12. Are straight tubes or curved tubes preferable in water tube 
 boilers? 
 
 Ans. 12. Straight tubes are preferable to curved tubes in water 
 tube boilers, because they are easier to clean and inspect, and give a more 
 direct passage for the circulation of water, as well as being easier to re- 
 place. 
 
 Q. 13. How are the nipples connecting tube headers and saddle piece 
 in a B. & W. boiler fastened? 
 
 Ans. 13. The nipples connecting tube headers and saddle piece in a 
 B. & W. boiler are expanded in the headers and saddle piece, and the endi 
 flared or bellied out to fasten them. 
 
 Q. 14. How are the tube caps put on a B. & W. boiler! 
 
 Ans. 14. (a) Tube caps on B. & W. boilers are put on the outside 
 and held in place by a bolt with a cap nut, the bolt passing through a 
 yoke or yoke plate inside the tube header. The joints between the cap 
 and header and between cap and nut are ground. Generally a little oil 
 and graphite to make the joint tight and occasionally a thin paper gasket 
 is used for this purpose. 
 
 (b) In the latest type of B. & W. boiler the caps are placed on the 
 inside similar to a hand-hole plate in a return tubular boiler. 
 
 Q. 15. What results may be noted when the mud drum of a B. & 
 W. boiler rests upon the brick work? 
 
 Ans. 15. Should the mud-drum of a B. & W. boiler rest upon the 
 brickwork it will sustain the weight of the boiler when heated, caused by 
 expansion of headers and nipples; these parts will then sustain the weight 
 of the rear of the boiler, generally causing the nipples to start in head- 
 ers and saddle piece, resulting in serious leaks. The mud-drum should 
 never rest on the brickwork. 
 
 Q. 16. When is a drift pin used in boiler construction? Why is its 
 use detrimental to good workmanship? 
 
 Ans. 16. In boiler construction a drift pin is sometimes used to 
 force carelessly spaced rivet holes into line so that the rivet may be driven 
 in. This distorts the rivet holes and causes strain in the metal near the 
 holes, which makes the use of a drift pin detrimental to good work- 
 manship. 
 
 Q. 17. Explain different methods of staying crown sheet of locomo- 
 tive type of boiler. 
 
 16
 
 Ans. 17. There are two methods generally followed in staying 
 crown sheets of locomotive type of boilers. The first is by means of 
 girder stays commonly called "fox roof stay." The ends of these 
 girder stays rest upon the edge of side sheet of fire box; a number of stay 
 bolts pass through crown sheet and girder stay secured at both ends with 
 nuts and washers, thereby staying the crown sheet. The ends of girder 
 stay are turned down, thereby causing a small water space between it and 
 the crown sheet. 
 
 A second method is by having stay bolts pass through crown sheet 
 and secured as in the first method; but the other end of bolt has a forked 
 end and pin fastened to angle irons which are riveted to shell of boiler. 
 
 Q. 18. In a longitudinal lap joint, why does the outside sheet point 
 upward, and the inside sheet downward! 
 
 Ans. 18. To prevent scale lodging on same inside of boiler. 
 
 Q. 19. What method is used to detect a defective stay bolt as used 
 on the side sheets of a locomotive type of boiler f 
 
 Ans. 19. Stay bolts staying flat surfaces very generally will, when 
 giving out, fracture near the outside shell. By drilling a small hole in 
 stay bolt, where protruding through outside shell, water and steam will 
 rush out of hole when fracture occurs, exposing the location of the de- 
 fective bolt. Stay bolts are now in the market having small holes drilled 
 into both ends. 
 
 Q. 20. What are the usual methods for inserting stay bolts for con- 
 necting flat surfaces? 
 
 Ans. 20. Stay bolts connecting flat surfaces of a boiler are usually 
 threaded the whole length and secured through both plates, and their 
 ends beaded over; sometimes that portion of the stay bolt between the 
 plates has the thread turned off smooth to prevent the lodgment of scale 
 on the thread. 
 
 Q. 21. Explain methods of connecting inner and outer sheets of water 
 leg of vertical tubular boiler. Which one method is the most preferable, 
 and why? 
 
 Ans. 21. The inner and outer sheets of water leg of a vertical boiler 
 are connected by a wrought iron ring which forms a distance piece separ- 
 ating the plates. Cast iron is sometimes substituted, but wrought iron 
 is preferable. Another method is by using a wrought iron double 
 flanged ring. This is not to be recommended, as it leaves a narrow ridge 
 on top of ring where sediment collects. This sediment is difficult to re- 
 move. 
 
 Q. 22. Which is preferable, short or long diagonal stays? Give rea- 
 sons. 
 
 Ans 22. A long diagonal stay is preferable to a short one as the 
 stress is more nearly in line with its length. 
 
 17
 
 Q. 23. How are through and through braces usually fasteued in a 
 boiler? 
 
 Ans. 23. Through and through stays are usually fastened with a nut 
 and washer on both inside and outside of head. The ends of rods where 
 threaded are enlarged so that the cross sectional area at bottom of thread 
 will be at least equal to cross sectional area of the rod. 
 
 Q. 24. When inspecting a boiler, how can one ascertain whether all 
 through and through braces are under uniform tension? 
 
 Ans. 24. The tension on through and through stays may be judged 
 by the sound given out when struck with a hammer. A. similar tone from 
 each indicates a uniform tension, while a dull tone indicates less tension. 
 
 Q. 25. Why is a reinforcing plate used where the blow-off pipe en- 
 ters a boiler? 
 
 Ans. 25. A reinforcing plate is used where the blow-off pipe enters 
 boiler to give greater thickness of metal to screw the blow-off pipe into. 
 If the hole into the shell is too large to fit the pipe, the main object of the 
 reinforcing plate is defeated, for, although the plate strengthens the 
 shell around hole, its main object is to better secure the blow-off pipe into 
 the shell by means of more threads. 
 
 Q. 26. Give reasons for and against the use of a submerged tube 
 sheet in a vertical tubular boiler. 
 
 Ans. 26. The submerged tube sheet in a vertical tubular boiler has 
 the advantage of protecting the upper end of tubes from the action of 
 the fire. Its disadvantages are a small steam space and a tendency to 
 prime when boiler is forced; they are then apt to carry water into the 
 steam mains. 
 
 Q. 27. Of what material are boiler lugs made? How are lugs 
 fastened to boiler? 
 
 Ans. 27. Boiler lugs on horizontal tubular boilers are made of cast 
 iron and riveted to the shell. 
 
 Q. 28. How many lugs should be attached to a boiler? Give rea- 
 sons. 
 
 Ans. 28. Not more than two lugs should be attached to each side of 
 the boiler, no matter what the length of the same may be. If more wer 
 used uneven settling of brick work might throw all the weight upon the 
 middle lug, causing a great strain upon boiler. 
 
 Q. 29. Explain the circulation of water in a B. & W. boiler. 
 
 Ans. 29. The circulation of water in a B. & W. boiler is from front 
 to rear of steam drum, down rear tubes and headers, thence through 
 inclined tubes to front headers, up through front headers and into steam 
 drum. 
 
 18
 
 Q. 30. Why are the mud drums of B. & W. boilers usually made of 
 cast iron! 
 
 Ans. 30. Cast iron is used as the impurities of the water do not so 
 readily attack cast iron as they do wrought iron or steel; and therefore, 
 cast iron better resists corrosion. In boilers built for high pressure steel 
 and wrought iron are sometimes used. 
 
 Q. 31. How should a fusible plug be constructed, and of what mate- 
 rial T 
 
 Ans. 31. The body or shell is made of brass, threaded, standard 
 pipe size, %", 1" or 1^4". The hole through the plug is made conical 
 to prevent the fusible metal being forced out by the pressure; the large 
 end of the cone being always on the pressure side. The small end of 
 the cone should not be less than l / 2 inch in diameter. Banca tin has 
 been found to be the most reliable metal to use for the cone. Its melt- 
 ing point is about 445 degrees F. 
 
 Q. 32. Where should a fusible plug be placed in the following types 
 of boilers? 
 
 a. Horizontal tubular. 
 
 b. Vertical tubular. 
 
 c. Locomotive. 
 
 d. Babcock & Wilcox. 
 
 Ans. 32. a. In a drop pipe from top of shell or in backhead above tubes. 
 
 b. In one of the tubes about 2 inches below the lower gauge 
 cock, a hand hole being cut through the shell for the purpose of 
 inserting the plug. 
 
 c. In crown sheet. 
 
 d. In a drop tube through top of shell. 
 
 Q. 33. What precautions should be observed in cutting a boiler in 
 on the steam main which is under pressure; also when a boiler in to be 
 cut out under the same conditions? 
 
 Ans. 33. The precautions observed should be to have steam brought 
 up equal to pressure in main, and all pipe connections should be well 
 drained and by pass (if any) opened to allow the pressure to equalize 
 before opening the main valve, and should be opened very cautiously at 
 all times, and to cut out the fire should be drawn or very low and valve 
 then closed. 
 
 Q. 35. When a steam boiler is equipped with two pop safety valves, 
 should the blowing point of each be the same? 
 
 Ans. 35. When two pop valves are used on one boiler one should be 
 slightly in advance of the other. 
 
 Q. 36. What precautions should be observed when laying up a re- 
 turn tubular boiler for an extended period of time? 
 
 19
 
 Ans. 36. Blow out boiler , while warm and clean out thoroughly and 
 if in a dry place leave off man hole and hand hole plates. If in a damp 
 place cover the inside of the boiler with black oil. Remove all ashes and 
 soot in direct contact with the shell of the boiler. 
 
 Q. 37. In steam boiler practice, neglecting the efficiency of the 
 butt-strap joint over the lap joint, name two other decided advantages 
 of the former over the latter type of joint. 
 
 Ans. 37. The strains are more directly in the line of the metal and 
 the plates are not injured to so great an extent in the rolling. 
 
 Q. 38. Does the normal steam pressure, or the expansion and con- 
 traction due to furnace operation, cause the greater strain in steam boil- 
 ers I 
 
 Ans. 38. Expansion and contraction cause the greater strain on a 
 steam boiler because of the enormous strain that must take place where 
 there is unequal heating; or the heating and cooling effect of ordinary 
 operation. 
 
 Q. 41. If a spring loaded safety valve is set at one hundred pounds, 
 what is the method of procedure to alter the blowing point to sixty 
 pounds! 
 
 Ans. 41. If a spring-loaded safety valve operates all right at 100 
 pounds' pressure it will be necessary to change the spring for a lighter 
 one, in order to operate successfully at 60 pounds' pressure, as these 
 springs should not be operated at a greater variation than 15 or 20 per 
 cent. 
 
 Q. 45. Where and how should a feed water pipe enter the follow- 
 ing types of boilers? 
 
 a. Horizontal tubular. 
 
 b. Vertical tubular. 
 
 c. Babcock & Wilcox. 
 
 Ans. 45. (a) The feed pipe may enter the boiler through top of 
 shell near front end, or through front tube sheet just above the top row 
 of tubes; in either case the pipe should be of brass and should extend 
 to near the back end of boiler and deliver the water below the water line. 
 
 (b) The feed pipe should enter the boiler through the shell near 
 the low water line, should extend across the boiler between the tubes, 
 should be of brass, the end should be capped and the pipe perforated to 
 distribute the water. 
 
 (c) The feed pipe should enter front of steam drum below the water 
 line and extend some distance back into the drum. 
 
 Q. 46. Describe, in from 75 to 125 words, the special features and 
 principles involved in the construction of the "Heine" water tube boiler. 
 
 Ans. 46. The Heine Safety Boiler has all flange steel construction, 
 without the use of expanded joints to hold any of the parts together, with 
 the exception of the tubes. There are no cast iron parts under tensile 
 
 20
 
 stress. The water legs, constructed somewhat similar to the side sheets 
 in a locomotive type, have a tendency, owing to their ample areas, to 
 give more rapid circulation. The trend of the combustion gases is hori- 
 zontal through the nest of tubes. The external side of tubes is cleaned 
 by means of a steam blower inserted through the hollow stay bolts in 
 front and rear water legs. Tube caps are on inside of water leg mak- 
 ing joint similar to an ordinary handhole. 
 
 Q. 47. Describe, in from 75 to 125 words, the special features and 
 principles involved in the construction of the "Cahall" water tube boil- 
 ers, both vertical and horizontal type. 
 
 Ans. 47. The Cahall Vertical Water Tube Boiler- consists of two 
 drums arranged one above the other and connected with a nest of tube*. 
 The upper, or steam drum, has an opening in the center through which 
 gases pass to chimney. The boiler rests upon four iron brackets riveted 
 to lower drum, supported upon four piers of the foundation. The boiler 
 is allowed freedom of expansion without interfering with external brick 
 work. The tubes are straight and placed in a vertical position, with, a 
 slight outward deflection from bottom to top, owing to the upper drum 
 oeing of slightly larger diameter than the lower drum. Owing to the 
 central hole in upper drum, there is a space in center of tubes, wide on 
 top and gradually narrowing down towards bottom. This boiler has an 
 external combustion chamber, and takes up very little floor space. It 
 is extensively used in places where waste furnace heat is available, such 
 as steel mills, etc. 
 
 The horizontal type of Cahall boilers is of the sectional header type, 
 such as the B. & W. The Cahall boilers are fitted with swinging manhole 
 covers. They swing on hinges, and the lifting in antl out of the covers 
 is thereby avoided. 
 
 Q. 48. Why will a fusible plug melt when covered with steam, and 
 the same plug not melt when covered with water, all other conditions being 
 the same? 
 
 Ans. 48. When a fusible plug is covered with water, the heat en- 
 tering the plug from the fire is absorbed by the water; but when plug is 
 covered with steam, the steam will not absorb the heat entering plug, 
 owing to the fact that steam is only able to absorb heat less than one- 
 third as rapidly as water. 
 
 Q. 49. What do you consider the best manner to temporarily stop 
 the leak of a split tube in a fire tube boiler in order to avoid a shut 
 down! 
 
 Ans. 49. A pine plug, the end of which should snugly fit the tube, 
 and the center turned to a smaller diameter. Drive the plug into tube 
 until the leak stops, then drive some little distance further, some two or 
 three inches until the leak will be opposite the turned part. 
 
 Q. 50. If the crab and nut of rear hand hole plate in a horizontal 
 tubular boiler should burn off would there be any danger of blowing 
 water out of boiler? 
 
 21
 
 Ans. 50. The burning off of a crab and nut would not allow water to 
 blow out of boiler as long as the handhole plate itself is intact, for, aa 
 these plates are put on from the inside, the pressure holds them firmly in 
 place. 
 
 Q. 51. How may crabs and nuts of rear hand hole plate be protected 
 from the fire? 
 
 Ans. 51. By covering nut and crab with asbestos or fire clay. 
 
 Q. 52. Why is good circulation of water in a boiler essential to 
 good steaming! 
 
 Ans. 52. Water is practically a nonconductor of heat. The heated 
 water therefore does not impart the heat it receives to its surround- 
 ing particles. However, when heated it expands, thereby becoming of a 
 lesser specific gravity than the cooler particles. This heated water will 
 endeavor to rise while the colder portions come to be heated in turn, thua 
 setting up currents in the water. The better the facilities in a boiler are 
 for setting up these currents or "circulation," the more efficient will be 
 its steaming qualities and its safety in operation. 
 
 Q. 53. Does the water level, as shown in gauge glass, always rep- 
 resent the true level in boiler, all connections being clear and openf 
 
 Ans. 53. If the water in the gauge glass and its connections could 
 be kept at the same temperature as the water in boiler, it would represent 
 the true level, but as the water in glass and connections cools off, it be- 
 comes of a greater density, and of course heavier than a corresponding 
 amount of warmer water would be. The water contained in glass, there- 
 fore, will be able to balance a column of greater height of warmer water. 
 When water gauge and connections are exposed in a cool place, and par- 
 ticularly so if the connections are long, the difference of the glass level 
 and boiler level become more pronounced. There are known instances 
 of the difference being some 1% to 2 inches. That is, the water in boiler 
 would be l l /2 to 2 inches higher than that shown in glass. Immediately 
 after thorough blowing down of glass, the true level will be shown until 
 water begins to cool off. 
 
 Q. 54. (a) If top of gauge glass is shut off what is the result? 
 (b)' If bottom of gauge glass is shut off what is the result? 
 
 Ans. 54. (a) By shutting off top valve of gauge glass the steam 
 is prevented from entering glass; the steam contained in glass will almost 
 immediately condense, allowing the water to take its place and rapidly, 
 in fact, almost instantly filling the glass. 
 
 (b) By shutting off bottom valve of gauge glass the water is pre- 
 vented from entering the glass; the steam in top of glass as it condenses 
 will slowly fill the glass. 
 
 Q. 57. Why do pop safety valves remain open some time after boiler 
 pressure has been reduced below the point at which they open?
 
 Ans. 57. Owing to the beveled edges of the valves and seat, the 
 steam after opening the valve is allowed to act upon a larger area than 
 when valve is closed, therefore the valve will blow until the steam has 
 fallen to a pressure too low to balance this larger area. 
 
 Q. 74. Describe in from 75 to 125 words the special features and 
 principles involved in the construction of the Iowa boiler. 
 
 Ans. 74 The Iowa boiler combines in its construction the return 
 
 tubular and the water tube type of boiler. The upper part consists of an 
 ordinary multi-tubular boiler. The low r er part, being of the water tube 
 type, is connected to the upper part by two water legs made in the form 
 of an arch, the tubes connecting the legs from the sides and top of fur- 
 nace and combustion chamber. Fire brick between tubes and fire clay 
 plastering keep furnace and combustion chamber tight on sides and top. 
 The tubes in lower part are inclined up towards rear, and circulation ia 
 through the tubes, up rear leg, through main shell and down through front 
 leg. Impurities in the water, precipitated in the upper shell, can do no 
 harm, as the shell is not in contact with the fire or combustion gases. The 
 rear of combustion chamber and rear of tubes in upper shell are con- 
 nected by means of a short flue for the passage of the combustion gases 
 from lower to upper part of boiler. 
 
 Q. 75. Describe in from 75 to 125 words the special features and 
 principles involved in the construction of a Stirling boiler. 
 
 Ans. 75. The Stirling boiler consists of three steam and water 
 drums at the top and one water or mud drum at the bottom. Each top 
 drum is connected to bottom drum by a bank of tubes slightly curved 
 at the ends. The steam spaces between the upper drums and the water 
 space between front and middle drums are also connected by means of 
 tubes. Suitable fire brick baffle plates between the banks of tubes direct 
 the course of the furnace gases. The feed water enters rear top drum, 
 the coolest part of the boiler, and its temperature is gradually raised 
 in its descent through the rear bank of tubes to mud drum below. The 
 lower drum is protected from the furnace heat by the bridge wall, and the 
 drum being large and the circulation therein very slight, it acts as a 
 settling chamber for the impurities precipitated there by the feed water as 
 it enters the drum, descending to the bottom of drum where they can be 
 blown off through the blow-off. The drums have manholes at each end, 
 The boiler is made of wrought material throughout. 
 
 Q. 77. What causes bagging in a boiler plate? 
 
 Ans. 77. Bagging of a boiler plate is caused by overheating, gen- 
 erally due to scale or other deposits accumulating to an extent that pre- 
 vents the water from coming in contact with the plate. The plate then 
 becomes soft and easily yields to the pressure acting upon it, thereby 
 forming a bag. A plate in such condition is materially weakened and 
 liable to be rent asunder, causing an explosion. 
 
 Q. 79. What is meant by the term, a ' ' blistered ' ' boiler plate, and 
 what is the cause thereof!
 
 Ans. 79. A blistered boiler plate is one having through imperfect 
 material, blisters on its surface. This is caused by the laminations or 
 layers of plate separating, the outer layer becoming burned and expanded 
 by heat, forming a blister. Sometimes these can be cut away. 
 
 Q. 81. A boiler is fitted with a safety valve set at 100 pounds, and 
 another safety valve also set at 100 pounds is fitted to outlet of the first one. 
 What will be the approximate pressure in boiler when blowing off through 
 both valves? 
 
 Ans. 81. By actual experiments it has been found that the pres- 
 sures required to lift each valve from the seat, must be added to obtain 
 the pressure in the boiler when blowing through both valves, hence, in this 
 case, the pressure in the boiler would be approximately 200 pounds. 
 
 Q. 84. What is a dead weight safety valve! What are its advan- 
 tages and disadvantages? 
 
 Ans. 84. A dead weight safety valve is a valve loaded with weights 
 acting directly on the valve. The weights corresponding with the total 
 pressure acting on the valve. For example, a four-inch valve intended to 
 blow at 100 pounds per square inch would require about 1,200 pounds of 
 weights. This type of valve has the advantage of being difficult to tam- 
 per with, as the adding of a few pounds weight woulfl not perceptibly 
 change the blowing point. On the other hand they are heavy and cumber- 
 some. 
 
 Q. 85. Explain the meaning of tensile strength, shearing strength, 
 and torsional strength. 
 
 Ans. 85. (a) Tensile strength is that strength in a substance which 
 resists its being pulled apart lengthwise. 
 
 (b) Shearing strength is the strength in a substance which resists its 
 being cut in two, as with a pair of shears. 
 
 (c) Torsional strength is the strength that resists twisting strains, 
 such as shafting is subjected to. 
 
 Q. 86. Why is a punched rivet hole more injurious to a boiler than a 
 drilled hole? 
 
 Ans. 86. Forcing a punch through boiler plates strains the metal 
 next to the hole so punched, and starts small radial cracks, in the metal. 
 If the hole is drilled there is no undue disturbance of the metal hence the 
 plate has full strength right up to the edge of the hole. 
 
 Q. 87. Is there any advantage in machine riveting over hand rivet- 
 ing if so, what does it consist of? 
 
 Ans. 87. Machine riveting is preferable to hand riveting because the 
 rivet has less time to cool before the head is fully formed, also because 
 pressure is exerted on the rivet while hot, enabling it to entirely fill the 
 hole and making a more solid joint than can be had by hand work. 
 
 21
 
 Pumps and Injectors. 
 
 Q. 1. If both are run under throttled steam, would a 8x6x10 steam 
 pump be as economical as a 10x6x10 pump of same type; the conditions 
 of oneration are to be identical. 
 
 of operation are to be identical 
 
 Ans. 1. If the work done were the same in both cases the smaller 
 pump would be the more economical. If the work done were proportional 
 to the pump dimensions then the larger would have the advantage. 
 
 Q. 2. Given a centrifugal pump elevating 300 gallons 25 ft. per min- 
 ute, what change in power used would occur if the discharge valve be 
 closed? 
 
 Ans. 2. There would be a large drop in power used owing to the 
 churning or whirling of the water. 
 
 Q. 3. What device should be placed in the suction pipe to a pump 
 which takes its supply from a place where the water holds sand and for- 
 eign matter in suspension? Describe the construction of such a device 
 and its location. 
 
 Ans. 3. A strainer should be used on a pump suction when the pump 
 draws its supply from rivers or ponds where foreign matter is held in 
 suspension. A strainer consists of a casting screwed on the end of the 
 suction pipe in the shape of a bowl. Woven wire or perforated metal is 
 fastened to the end of the strainer bowl. The fineness of the mesh is 
 made according to the material screened. The combined area of the open- 
 ings to be three or four times the area of the pipe. Where the end of the 
 pipe is not accessible for cleaning a strainer is placed near the pump on 
 the suction pipe. The strainer is cast iron casting in *^e shape of a plug 
 hat. The screen is fitted to the casting and placed so that the water has 
 to flow through it. There is a cap placed on the end of casting for clean- 
 ing. 
 
 Q. 58. How would you lengthen or shorten the stroke of a duplex 
 pump? 
 
 Ans. 58. The stroke of a duplex pump can be lengthened by increas- 
 ing the lost motion. To shorten the stroke the lost motion should be de- 
 creased. 
 
 Q. 59. What is the advantage and disadvantage of an outside 
 packed plunger pump as compared with a piston pump! 
 
 25
 
 Ans. 59. An outside packed plunger pump shows at a glance if the 
 packing is in good condition. The plungers can also be constructed to 
 better withstand heavy pressures than ordinary piston pumps. They have 
 the disadvantage of taking up larger floor space, and great friction of 
 packing around plungers. 
 
 Q. 60. Should a pump, pumping hot water and receiving it at atmos- 
 pheric pressure be placed above or below the source of supply f Whyf 
 
 Ans. 60. The pump should be placed below its source of supply, so 
 that the water may flow by gravity into the pump. The vapor arising 
 from the hot water would destroy the partial vacuum necessary to raise 
 the water, if the pump was placed above its source of supply. 
 
 Q. 61. How does a plunger or piston pump, setting above its source 
 of supply, draw the water and deliver it out of discharge pipe? 
 
 Ans. 61. When a pump raises water it is owing to the fact that a 
 vacuum has been created in the pump and suction pipe, the pump-piston 
 or plunger having expelled the air out of the same. The atmospheric 
 pressure acting upon the water supply has a tendency to destroy this 
 vacuum by equalizing {he pressures. It will, therefore, endeavor to do 
 this by entering the suction inlet, but the end of the suction being im- 
 mersed in the water, the water will be forced up into the suction pipe in- 
 stead until it reaches the pump, entering same through the suction valves, 
 being expelled through the discharge valves into the discharge pipe. 
 Should the partial vacuum maintained by the pump in the suction pipe 
 become equalized with the atmospheric pressure at a point below the pump, 
 the water will only rise to this point and the pump will not be able to get 
 water until this vacuum has been sufficiently increased. 
 
 Q. 62. What limits the height a pump can be placed above its source 
 of supply? 
 
 Ans. 62. The atmospheric pressure limits the height a pump can be 
 placed above its source of supply. Theoretically, this is about 34 feet, 
 but it requires the forming of a perfect vacuum in order to obtain this 
 result. To raise the water some 26 or 27 feet requires the pump to re- 
 duce the atmospheric pressure in the suction pipe about 12 pounds, or, in 
 other words, the pump has to maintain a vacuum in the suction pipe of 
 some 24 inches. Pumps doing this can be considered as giving good re- 
 sults. 
 
 Q. 63. Under what condition is an air-chamber on the suction pipe 
 most beneficial in obtaining good results? 
 
 Ans. 63. Air or vacuum chambers on the suction pipe are of most 
 benefit on pumps with a high or long lift. A vacuum chamber, owing to 
 the compression and expansion of the air contained therein, facilitates 
 changing a continuous into intermittent motion. The water in suction 
 coming to a standstill upon the end of stroke is brought to rest gradu- 
 ally by the compression of the air in vacuum chamber, when the next 
 stroke commences the air expands and helps the piston starting the water 
 in motion again. Pumps running at a high rate of speed should be fitted 
 with vacuum chambers, as it allows them to run with less noise and tends 
 to ease the strain on the moving parts of the pump. 
 
 26
 
 Q. 64. What is the object of an air-chamber on the discharge of a 
 pump? 
 
 Ans. 64. The air chamber, due to the compression and expansion of 
 the air contained therein, causes a steady discharge of water. During the 
 time the piston makes a stroke the air is compressed, expanding as the 
 piston comes to rest, acting as a cushion and gradually reducing the flow 
 of water until the beginning of the next stroke. It also allows the 
 valves to seat more easily. 
 
 Q. 65. What is the object of a foot valve on the suction pipe? 
 
 Ans. 65. It keeps the suction pipe full of water and greatly assists 
 the pump in case of high lifts or leaky valves. Suction pipes exposed to 
 freezing temperature should, if fitted with foot valves, have some means of 
 draining water out of suction pipe when shutting down any length of 
 time. 
 
 Q. 66. What is the best method of setting steam valves on a du- 
 plex pump? 
 
 Ans. 66. Place both pistons in center of travel; the rocker arms 
 will then be plumb. Kemove steam chest cover and set steam valves 
 in central position over steam ports, and adjust all lost motion equally 
 on each side of collars or nuts which move the valves. Before closing 
 steam chest one steam valve should be moved so as to open steam port; 
 this will facilitate starting up. 
 
 Q. 67. Why has the steam valve of a duplex pump no lap? 
 
 Ans. 67. The valves have no lap, as the pump must take steam the 
 full stroke. 
 
 Q. 68. Why is it necessary for a steam pump to have steam admis- 
 sion the full length of stroke? 
 
 Ans. 68. A steam pump having no balance wheel or other means of 
 momentum would stop if steam were cut off at partial stroke, due to the 
 steam pressure falling after cutting off steam supply, and the resist- 
 ance would soon equal and exceed the moving force. 
 
 Q. 69. What is the material best suited for the construction of 
 pump valves handling: 
 
 (a) Cold water. 
 
 (b) Hot water. 
 
 (c) Compressed air. 
 
 Ans. 69 (a) Pumps handling cold water should have pure rubber 
 valves. 
 
 (b) Pumps handling hot water should be fitted with either vulcan- 
 ized rubber valves or valves made of composition metal. 
 
 (c) Pumps compressing air give best results with steel valves. 
 
 27
 
 Q. 70. What is the object of lost motion in the steam valve gear of 
 a pump? 
 
 Ans. 70. The lost motion allows the valve to be motionless part 
 of the stroke, thereby permitting the piston to make the full stroke be- 
 fore the valve is reversed. 
 
 Q. 71. What is the object of a cushion valve on steam end of a 
 pumpf 
 
 Ans. 71. Cushion valves are used for the purpose of regulating the 
 degree of cushion at the end of stroke. It connects the steam and exhaust 
 ports. Closed, it gives the greatest amount of cushion. By opening the 
 cushion valve a little at a time, the amount of cushion required can be 
 easily determined. 
 
 Q. 72. How is a centrifugal pump constructed? 
 
 Ans. 72. The moving part of a centrifugal pump consists of a shaft, 
 having wings or arms radiating from the same, usually curved in a di- 
 rection opposite from the direction of rotation. The whole is enclosed in 
 a case, the case having openings in the center around the shaft and an 
 opening at a point farthest from the shaft. The center openings are 
 for the suction, the other opening is for the discharge. 
 
 Q. 73. How does a centrifugal pump work, and what work is it best 
 adapted for? 
 
 Ans. 73. The shaft and arms rotating in the pump case impart 
 motion to whatever substance is contained in the same, throwing it out- 
 ward from the center by centrifugal force, expelling it out of discharge 
 opening at the outer rim of the pump case. In this manner a vacuum is 
 formed in the pump and suction pipe, allowing the water, or other sub- 
 stance pumped, to enter the pump to be in turn expelled out of discharge. 
 These pumps must be primed when standing above their supply; this is 
 sometimes accomplished by shutting the discharge and having a pump 
 or ejector expel all air contained in suction pipe and pump case, start- 
 ing the pump and opening discharge valve when all air is expelled. These 
 pumps are extensively used for handling large volumes of water quickly, 
 such as in the case in tanneries, paper mills, dry docks, etc., as they are 
 valveless, sand, gravel and other impurities have no effect upon their 
 operation. 
 
 Q. 74. How is a rotary pump constructed, and what are the prin- 
 ciples governing its operation? 
 
 Ans. 74. A rotary pump is constructed of casing enclosing P piston 
 or pistons, sometimes called impellers. They are made several ways. 
 Some have the butments movable, while others have a movable wing on 
 the pistons which slides in and out when passing the butments. One 
 type is made with two gear-like impellers running together, others with 
 impellers that are larger top and bottom, and set so that the larger part 
 of one fits into the smaller part of the other; each impeiier is mounted 
 on separate shafts which are connected by gears. 
 
 28
 
 The principle governing the action is as follows: Running at a high 
 rate of speed the impellers create a partial vacuum, into which the atmos- 
 pheric pressure forces the water. The construction is such that the water 
 once caught by the impellers is prevented from returning to the suction 
 side and is forced into the discharge pipe. 
 
 Q. 76. Why is an auxiliary steam valve necessary on all single cylin- 
 der steam pumps? 
 
 Ans. 76. An auxiliary valve is necessary to operate the main valve 
 of the pump. If the main valve of the pump was mechanically con- 
 nected to piston rod of pump, the steamport would be covered slowly 
 toward the end of stroke and the stroke would not be completed, there- 
 fore the valve would not reverse. 
 
 Q. 82. Is a belt or motor driven boiler feed pump more economical than 
 a direct acting steam pump I If so, why? 
 
 Ans. 82. A belt or motor driven pump is more economical than a direct 
 acting steam pump, because the power to operate it is usually taken from an 
 engine using steam expansively. 
 
 Q. 83. About what efficiency should be obtained from an injector. 
 
 Ans. 83. The injector, taken as a pump, has a very low efficiency, much 
 below that of the ordinary direct acting steam pump. Considered as a pump 
 and feed water heater, it has an efficiency of nearly 100 per cent. 
 
 Q. 84. How is the steam used in an injector utilized? 
 
 Ans. 84. The steam condensed in the operation of the injector is used 
 in heating the feed water and forcing it into the boiler. The construction 
 of the injector is such that when steam from the boiler is admitted to it a 
 vacuum is created in the suction pipe, causing the water to flow through 
 the injector. The steam is condensed and its velocity imparted to the water, 
 thus giving the water sufficient velocity to force it into the boiler. 
 
 Q. 85. Why does an injector refuse to operate when the feed water is 
 too hot? 
 
 Ans. 85. As there is no means of exhausting the steam from an injector 
 except by condensing it and putting it into the boiler along with the feed 
 water, it follows that enough water must enter the injector to condense the 
 steam ; and if the water is too hot, enough of it cannot enter the injector to 
 condense the steam, hence the injector will not work. 
 
 Q. 86. How can a feed water heater be used in conjunction with an in- 
 jector? 
 
 Ans. 86. The water from an injector may be passed through a closed 
 feed water heater before entering the boiler. An open feed water heater can- 
 not be used in conjunction with an injector if the feed water is heated to a 
 perceptible degree.
 
 Q. 87. Explain fully, and in plain language, how an injector forces 
 water into the boiler from which it receives its steam supply. 
 
 Ans. 87. To feed water into a steam boiler by means of an injector is 
 mainly accomplished by the existing difference in velocity between the steam 
 and the water flowing from the boiler under the same pressure. The ratio 
 between the two velocities is quite large, leaving considerable energy for 
 forcing fresh water into the boiler. The mass of steam which meets the 
 comparatively cold feed water in the vacuum chamber of the injector acts 
 upon the latter by impact of the condensed water upon the feed water. 
 Usually the ratio between the two masses (steam and feed water) is 1 to 10 
 or 1 to 13 and the velocity with which the water is forced into the boiler is 
 at least as many times less than the steam velocity as the feed water mass 
 weighs more than the condensed steam mass, which forces the combined mass 
 into the boiler. For illustration, the following example may be given: 
 
 Assuming the boiler pressure to be 75 pounds gauge pressure, then the 
 velocity with which the water would flow out of the boiler would be 
 
 V2X 32.2X75X2.31 =105 feet per second. 
 
 The velocity with which the steam would flow from the boiler would de- 
 pend on the fall of temperature of the steam, which would be from 320 to 
 212 F and velocity would be (steam considered dry), 
 
 V778X2X32.2X(320 212)=2532 feet per second. 
 
 Assuming now that one pound of steam delivers 10 pounds of water into 
 the boiler, making a total of 11 pounds, then the steam velocity is thus re- 
 
 2532 
 
 duced from 2532 feet to =230 feet per second, and if 25% friction is 
 
 11 
 
 produced in the water passage then the water will still be forced into the 
 boiler with 
 
 230 X. 75 105=67 feet per second.
 
 Heaters and Condensers. 
 
 Q. 37. What is the difference in construction between the open and the 
 closed types of feed water heaters? Describe how the feed water is heated 
 in each type? 
 
 Ans. 37. In an open feed water heater the steam and water come in 
 actual contact with each other, the steam thereby heating the water. The 
 feed water sometimes enters this type of heater in the form of a spray, and 
 also quite often by filling a series of pans, overflowing them and tending to 
 purify the water thereby. In a closed heater the feed water does not come 
 in actual contact with the steam, but is heated by being passed through a 
 series of tubes or a coiled tube, the steam enveloping these tubes or tube, 
 heating the water. 
 
 Q. 38. What is a superheater? 
 
 Ans. 38. A superheater is an arrangement, usually of pipes, placed in 
 the combustion space of the furnace, or in the uptake. The steam on its way 
 from the boiler to the engine passes through this superheater and is super- 
 heated. 
 
 Q. 39. Describe the construction of a fuel economizer. 
 
 Ans. 39. A fuel economizer is an arrangement of tubes placed in the 
 uptake of a boiler or battery of boilers, through which the feed water passes 
 on its way to the boilers; the flue gases heating the feed water while pass- 
 ing through these tubes. 
 
 Q. 40. Describe constructional details of the most approved type of 
 condensers, of both jet and surface type, with reasons why each type is pe- 
 culiarly adaptable for some classes of service and not for others. 
 
 Ans. 40. The surface condenser consists of a number of brass tubes 
 within a box or case. Tubes should be well tinned, and should be small as 
 possible for good distribution of the condensing water. It should be pro- 
 vided with a good circulating pump to force the water rapidly around the 
 condensing surfaces, and also be provided with an air pump to remove air 
 and vapor. This form of a condenser is used where the water is salty or 
 very impure as the steam does not come in direct contact with condensing 
 water and condensed steam can be used for boiler feed water, and adapted 
 for marine purposes. 
 
 A jet condenser consists of a box or case in which the exhaust steam 
 comes in contact with condensing water in form of a spray falling on a 
 scattering plate. The pump should be placed below the condenser for re- 
 moving the air and water. This form of condenser takes less water and 
 costs less to install. 
 
 31
 
 Q. 41. How many square feet of Tooling surface should be required in a 
 surface condenser for an engine developing 250 I. H. P. and using 23 Ibs. of 
 steam per I. H. P. per hour? 
 
 Ans. 41. Several authorities give the constant .0944 multiplied by the 
 pounds of steam per horse power hour as the number of square feet of cool- 
 ing surface required. In this instance it will be 542 square feet. 
 
 Q. 42. How many gallons of water would be needed per hour to con- 
 dense the steam from an engine running under conditions as mentioned in 
 No. 41? Pressure of exhaust, 4 Ibs. absolute. Temperature of steam at 
 condenser is 170, cooling water entering at 60 and leaving at 112. 
 
 Ans. 42. 13,150 gallons. This answer is obtained by use of the follow- 
 ing rule : 
 
 1128.64170+32 
 
 =19.05X250X238.33 
 
 11260 
 
 Q. 43. About how much more cooling water is required in a surface con- 
 denser than a jet condenser? 
 
 Ans. 43. It takes about 25 to 35% more water for surface condensers 
 than for those of the jet type. This is due to the water not coming in direct 
 contact with the steam in the surface type of condenser. 
 
 Q. 44. In starting up a jet condensing engine, which would you start 
 first, the engine or condenser, assuming them to work independently; and 
 which would you shut down first? We will assume there are no pockets for 
 water between condenser and engine. 
 
 Ans. 44. Start the condenser before starting engine, and shut down the 
 engine before shutting down the condenser. 
 
 Q. 45. (a) What is a vacuum breaker and why are they used? (b) 
 Is vacuum a power? 
 
 Ans. 45. (a) A vacuum breaker is a valve attached to the condensing 
 chamber of a condenser, or to the exhaust pipe leadfng to the condenser. It 
 may be arranged to be automatic in action, or not, as may be desired. It 
 admits air to break or destroy the vacuum. 
 
 (b) Vacuum is not power, as all power in a steam engine is derived from 
 the pressure of steam on the piston ; if there is no resistance on one side of 
 the piston the entire pressure is available on the other side of the piston. 
 
 Q. 46. The temperature of water in hot well being more than 212 and 
 you lose your vacuum, what would be the cause? 
 
 Ans. 46. With a temperature of 212 in the hot well sufficient vapor will 
 be present to destroy all vacuum, and under such conditions a vacuum is not 
 possible.
 
 Q. 47. What are the necessary cocks and valves in an engine room of a 
 idensing engine? 
 
 condensing engine? 
 
 Ans. 47. Throttle valve of engine, valve in exhaust pipe between engine 
 and condenser, throttle valve for steam end of condenser pump, atmospheric 
 valve in exhaust pipe line, valve for priming condenser, suction valve on 
 suction pipe to condenser, and cocks on the steam pump cylinder of con- 
 denser. 
 
 Q. 48. What is the method used in cleaning the external surface of fuel 
 economizer tubes? 
 
 Ans. 48. The fuel economizer is provided with a set of scrapers en- 
 circling the tubes which are alternately raised and lowered the entire length 
 of the tube by mechanical means. 
 
 . Q. 49. Under what circumstances is the open type of feed water heater 
 preferable to a closed type of feed water heater? 
 
 Ans. 49. Where pumps are used instead of injector, when the feed water 
 is full of scale forming matter, and where there are a lot of drips to be taken 
 back into the feed water.
 
 Furnaces, Chimneys, Draft, Fuels, Com- 
 bustion, Etc. 
 
 Q. 1 What conditions must exist in the furnace of a steam boiler to in- 
 sure practically complete combustion? 
 
 Ans. 1. Must have a high temperature and the proper amount of air 
 brought into intimate contact with the fuel and distilled gases from same. 
 
 Q. 2. With coal at $2.25 per ton (of 2,000 Ibs.) and an actual evapora- 
 tion of 7.5 Ibs. show by a short metnod the cost of 1,000 Ibs. of steam ; also 
 how many Ibs. can be evaporated for one dollar? 
 
 Ans. 2. To find the cost per 1,000 Ibs. of water evaporated where the 
 cost per ton of coal and the evaporation are given : Divide the cost per ton 
 of coal by twice the evaporation gives cost per 1,000 Ibs. 6666.6 Ibs. of 
 water for $1.00, or 15 cts. per 1,000 Ibs. 
 
 Q. 3. In a combined steam boiler and coal burning furnace, why, in 
 practice, is it impossible to realize 90% efficiency? 
 
 Ans. 3. Assume a coal with 13,000 B. T. U. in it. Deduct 5% loss for 
 ashes and 5% loss for radiation there is lost in these two ways 10%. In 
 addition to these and some other small losses we have to heat 20 Ibs. of air 
 to each Ib. of fuel and if the specific heat of the gases is .25 there is lost five 
 heat units for each degree raise in temperature of the gases between enter- 
 ing and leaving the furnace. If this raise is 500 degrees we thus lose 500 
 times 5 or 2,500 heat units or 19% about on this account alone, makine a 
 total for these three causes almost 30%. Hence it is impossible in practice 
 to realize 90% efficiency in a boiler furnace. 
 
 Q. 4. In a typical mechanical draft plant, what percentage of the power 
 generated should, in good practice, be required to produce the draft? 
 
 Ans. 4. From 3% 
 
 Q. 43. How should chimney flues and feed water mains be arranged 
 when fuel economizers are used? 
 
 Ans. 43. Chimney flues and feed water mains should be arranged with 
 by-pass flues and mains so that the economizer can be cut out whenever it 
 becomes necessary to do so.
 
 Q. 44. How does the use of an economizer affect the chimney draft; 
 also the foreign matter contained in the feed water? 
 
 Ans. 44. Economizers reduce the temperature of the gases passing up 
 the chimney, hence it reduces the intensity of the draft. 
 
 Heating the feed water causes foreign matter held in suspension to de- 
 posit, and as the heating takes place in the economizer the deposit will be 
 there. 
 
 Q. 85. Describe in a general way the construction of an automatic 
 damper regulator, and the principles governing its operation. 
 
 Ans. 85. Describing damper regulators in a general way, it may be 
 said that two distinct types cover the field of general use. First, is the low 
 pressure regulator, where the steam pressure acts directly on a diaphragm, 
 which by a system of levers controls the damper or dampers. This type is 
 extensively used for low pressure heating plants. 
 
 Then comes the high pressure type of regulator, where the steam acts on 
 a diaphragm or piston counterbalanced by weights. This controls a valve 
 which in turn admits water under pressure to a piston which actuates the 
 damper. The water pressure may be taken from the boiler or other suitable 
 source. 
 
 Q. 89. Should there be a difference in the size of a fan supplying me- 
 chanical draft to a boiler under the following conditions: 
 
 (a) Forced draft. 
 
 (b) Induced draft. 
 
 Ans. 89. Owing to the fact that air after having passed through the fur- 
 nace has expanded in volume, a fan supplying cold air to the bottom of the 
 grates can be smaller than a fan placed in the uptake of a boiler, the duty 
 in both cases being alike in reference to work being done by the boiler. 
 
 The first Would supply a forced draft, while the second would induce a 
 
 draft by exhausting the air from the uptake. 
 As the larger fan 
 
 handles air which is of a lesser density, owing to its 
 
 volume being expanded, the power required to drive it would not materially 
 differ from that necessary to operate the fan handling the cold air.
 
 Air Compressors. 
 
 Q. 5. State what advantages there are in using an air lift for deep well 
 service, over those to be obtained by use of deep well pumps ; also conditions 
 under which the best results may be attained by use of the latter? 
 
 Ans. 5. The advantage of an air lift over a deep well pump for deep 
 well service, is its simplicity, being able to concentrate all the machinery 
 in one place which can be conveniently located, and its ability to handle 
 water containing grit without injury to the machinery, but where the wells 
 are not scattered and water is pure the deep well pump has a greater ef- 
 ficiency. 
 
 Q. 8. What is the difference between the real and apparent clearance 
 in an air compressor; how can the real clearance best be determined? 
 
 Ans. 8. The apparent clearance in an air compressor is the space left, 
 which is not swept through by the piston and is usually very small, i. e., sel- 
 dom more than % but frequently less than 1/16 of an inch between piston 
 and cylinder head. The real clearance is the amount of space the compressed 
 air, that is left in the compressor after completion of stroke, will occupy 
 after it is re-expanded to the original suction pressure. This clearance can 
 best be determined on the compressor indicator diagram and is that part of 
 the stroke where the expansion line meets the suction pressure line, or in 
 other words, where the prevailing pressure in the compressor during the re- 
 turn stroke reaches the suction pressure. 
 
 Q. 14. Given an air compressor with a cylinder 12 inches long, tak- 
 ing free air at atmospheric pressure (14.7 Ibs.), and discharging against 
 a pressure of 100 pounds gauge pressure; considered adiabatically, what 
 will be pressures at 3d, 6th and 9th inches of the stroke, and at what por- 
 tion of the stroke (considered in inches) will the discharge of air com- 
 mence? 
 
 Ans. 14. If P,=absolute final air pressure, 
 P ^absolute initial air pressure, 
 V t = final volume of air, 
 V =initial volume of air, 
 then 
 
 P, f V I 1.41 
 
 and 
 P V, 
 
 V P, I 0.71 
 
 V, I P 
 
 36
 
 hence the pressures at the 3d, 6th and 9th inches are 20.8, 55.3 and 98 
 pounds absolute, respectively, and the final volume at 100 pounds gauge 
 pressure would be 2.788 inches from the end or 76.8% of the entire stroke. 
 
 Q. 23. With a condensing, steam driven air compressor using 15 pounds 
 of steam per horse power, and compressing 5 cubic feet of free air for each 
 horse power exerted, how many degrees can the feed water be heated by the 
 compressed air, if the latter gives up 300 degrees of its temperature, 
 ignoring all losses? 
 
 Ans. 23. Assuming the temperature of the air when entering com- 
 pressor to be 60 F. then 5 cu. ft. would weigh .3805 of a pound. The 
 specific heat of air is .2375. hence the heat given off by 5 cu. ft. of air if 
 reduced 300 F. is . 3805 X. 2375X300=27 B. T. U., and since 15 pounds of 
 water must at least be fed to the boiler for every 5 cu. ft. of air compressed, 
 it follows that the temperature the feed water can be raised amounts to only 
 27 
 
 =1.8 F. 
 15
 
 Mechanics, Piping, Refrigeration, Test 
 Apparatus, Steam, Elevators, Gas Pro- 
 ducers, Etc., and Miscellaneous. 
 
 Q. 1. What features should be embodied in the design of gas engines of 
 100 h. p. for use in driving a mixed motor and lighting load? Peak load to 
 be of short duration at 10 per cent, overload, and normal load of about 
 75 h, p. 
 
 Ans. 1. The features that should be embodied in the design of gas en- 
 gine should be the ' ' Throttling Governor, ' ' very sensitive, heavy fly wheel, 
 (3 or 4) three or four cylinder, (4) four cycle. 
 
 Q. 2. Describe the construction and operation of some one type of suc- 
 tion gas producer. 
 
 Ans. 2. A suction gas producer has the following parts: A generator, 
 smoke pipe evaporator, scrubber, and gas receiver. The generator is an or- 
 dinary cylindrical stove lined with fire brick in which the coal burns. The 
 evaporator containing water is placed inside of the steel shell of the pro- 
 ducer or generator in contact with the fire and generates steam which is con- 
 ducted through a pipe and discharged beneath the grate mixing with the 
 air as it is drawn up into the fire. The heat of the fire decomposes this 
 steam into its constituent parts of oxygen and hydrogen. The hydrogen 
 increases the heating value of the fuel 20 to 25 heat units per foot. The 
 second large vessel is what is known as the scrubber. This is a boiler iron 
 cylinder filled with coke. The gas from the producer enters this scrubber 
 at the bottom, passing upward to the pipe leading to the gas receiver or en- 
 gine. At the top of this scrubber a water pipe enters and water is sprayed 
 on top of the coke and runs down through the coke to the trap at the bot- 
 tom. This cools the gas and washes out the dust and other impurities, which 
 are drawn through the producer by the suction of the engine. The gas re- 
 ceiver is a small storage tank for gas. To start the producer a fire is kindled 
 on the grate. The vent in the smoke pipe is opened to the outer air. The 
 blower is started, taking from 15 to 30 minutes the first time that the pro- 
 ducer is started. The fan must be operated until the test flame burns with 
 a bright blue flame. Then shut the damper in the smokestack. The blower 
 is stopped and the valve to the gas receiver is opened. The engine is then 
 started. 
 
 Q. 3. Given the famous Ferris wheel, 250 feet in diameter: A band or 
 tire of steel is made for same, and found to be 12 inches too long. How 
 much larger in diameter is the band than the diameter of the wheel; and
 
 how many degrees Fahr. drop in temperature will be needed to shrink the 
 band so that it will fit the wheel, if the coefficient of expansion is .00000686? 
 
 Ans. 3. 1 
 
 =185 Fab. 
 (250X3.1416+1) X.00000686 
 
 Q. 4. How wide should a double belt be to transmit 500 h. p. from a 
 drive wheel 22 ft. in diameter running 65 r. p. m.f 
 
 600X500 
 Ans. 4. 78 ins. wide, . Single belt, 7/10 of that trans- 
 
 22X3.1416X65 
 mitted bv a double belt. 
 
 Q. 5. If the power, as given in No. 4 was to be transmitted from shaft 
 .to shaft, which would require the heavier belt; in one case the driving and 
 receiving pulleys are both 48 inches in diameter, and in the other case the 
 diameters are 72 inches? 
 
 Ans. 5. The belt on the 48" pulleys would have to be 2/3 wider than the 
 one on the 72" pulleys as the speed in feet per minute is more. 
 
 Q. 6. What type of passenger elevator best meets the requirements of 
 office building service, it being assumed that the lift is not over 200 ft. nor 
 the car travel over 350 ft. per minute? Explain in detail. 
 
 Ans. 6. Electric type elevator when continued service can be had or ob- 
 tained. (Eeasons.) No expense when elevator not in use. Easy to operate 
 and when properly constructed cost of maintenance very light. 
 
 Q. 7. What is the smallest size elevator installation in which it would 
 be a paying investment to install a high duty pumping engine, one that 
 would develop a horse power on not more than 35 pounds of steam per hour? 
 
 Ans. 7. Two (2) two-ton elevators running continuously not less than 
 150 lift and speed not less than 150 feet per minute. 
 
 Q. 8. Assuming a high pressure, inverted hydraulic elevator; does it use 
 more power running light or loaded? 
 
 Ans. 8. The same amount is used under both conditions as the cylinder 
 must be filled in either case. 
 
 Q. 9. W T hat features of design and construction should be embodied in 
 valves, of either the globe or gate types, for use on high pressure steam 
 lines, where the service must be continuous? 
 
 Ans. 9. All high pressure valves should be constructed heavy enough to 
 withstand all strains, and those of 6" or over should have flange connections 
 and by-pass also be constructed so valve stem could be packed when valve is 
 open. 
 
 39
 
 Q. 10. In locating standpipes for fire protection purposes, in mills or 
 office buildings, which is preferable, the inside or outside pipes, and why? 
 
 Ans. 10. Standpipe should be placed on the outside for easy access. 
 
 Q. 11. What should the position of a globe valve be placed on pipes 
 lying in a horizontal position? 
 
 Ans. 11. A globe valve placed in a horizontal pipe line should have its 
 stem in a horizontal position. When so placed it prevents the trapping of 
 water in the pipe; the valve seat will be in a vertical position, and as it is 
 nearly the full size of the pipe it allows complete drainage. Should the stem 
 be in a vertical position, either upward or downward, water would be trapped 
 to a considerable extent. 
 
 Q. 12. What is a water hammer? Name some of the conditions under 
 which they occur. 
 
 Ans. 12. A water hammer is the snapping and pounding so frequently 
 heard in pipe systems. In its mild form it is simply annoying, but often 
 it occurs in a violent form and becomes highly dangerous. A water ham- 
 mer is produced under the following conditions: A pipe laying horizontal, 
 imperfectly drained and containing more or less water, has live steam turned 
 into it ; this live steam striking the water will almost instantly condense and 
 create a small area of vacuum into which the water rushes with great force, 
 and then coming to rest, resulting in a distinct shock. The strength of the 
 snapping or pounding depends upon the length of time it takes to condense 
 the steam admitted to the pipe. 
 
 Q. 13. What is the best method of preventing wasting or pitting in 
 underground steam lines, used for returning condensation? 
 
 Ans. 13. They should be of cast iron or brass and should be run in dry 
 boxes or trenches out of contact with the earth. 
 
 Q. 14. Describe the differences between the "compression" system of 
 refrigeration, and the one commonly termed the ' ' absorption ' ' system. 
 
 Ans. 14. A compression system of refrigeration is operated by means 
 of a gas pump or compressor. The operations are compression of the gas 
 by the compressor to about 150 Ibs. Next a withdrawal of the heat caused 
 by compression by means of cold water in contact with the pipes containing 
 the ammonia gas. Next the expansion of the liquid and absorption by it of 
 the heat of brine water or air to be cooled in their return to the compressor to 
 complete another cycle; It is an alternate compression and expansion of the 
 refrigerant. 
 
 In the absorption method in a still, aqua ammonia is used con- 
 taining 26% solution of ammonia in water which is put into a vessel 
 and a coil of steam pipe is run through the vessel. The heat of the steam 
 heats the ammonia and water, causing the ammonia to expand and evaporate 
 to a pressure of about 150 Ibs. The gas and some condensed water pass out 
 of the still to the dehydrating coil. The coil is enclosed in a tank which is 
 filled with water at a temperature of about 150 degrees where the water-vapor 
 condenses and the ammonia remains a gas. The gas and water flow to a 
 water separator w-here the water goes back to the still and the gas completes 
 the cycle as in a compression system. 
 
 40
 
 Q. 15.' How can transparent ice be made, by artificial means, from 
 clear water that has not been distilled or boiled? 
 
 Ans. 15. By gentle agitation of the water to be frozen. 
 
 Q. 16. Why should an indicator card be as long as possible? 
 
 Ans. 16. So as to magnify the different lines such as admission and 
 expansion and to separate the important points as cut off release and ex- 
 haust closure, making them all as distinct and prominent as possible. A long 
 card more readily adapts itself to graphical measurements and proofs. 
 
 Q. 17. Define the term "superheated steam." 
 
 Ans. 17. The term, superheated steam, means steam which has a higher 
 temperature than that normal to its pressure, or that contains more heat 
 than it is possible to contain while in contact with water. Steam cannot be 
 superheated when it is in direct contact with water. 
 
 Q. 18. (a). What are the advantages and disadvantages of using super- 
 heated steam ? 
 
 (b). What engine valve gears are best adapted for using superheated 
 steam? 
 
 Ans. 18. (a). The advantage of superheated steam is that, containing 
 a greater amount of heat than that normal to its pressure, it reduces the 
 amount of condensation in the cylinders to a minimum. 
 
 The disadvantage is the difficulty of lubricating the surfaces of valves 
 and cylinders, as the high temperature tends to burn the lubricating mate- 
 rial. The complex apparatus for superheating steam is somewhat of a dis- 
 advantage also. 
 
 (b). Poppet valves are best adapted for using superheated steam. 
 
 Q. 19. If steam enters an engine cylinder at 335 F. and leaves it at 
 225 F., what becomes of the temperature represented by the drop of 110; 
 no account need be taken of losses by radiation. 
 
 Ans. 19. The 110 F. did not disappear but simply became latent, i. e., 
 they are required to keep the steam in a more expanded form or rather at a 
 greater volume. If the steam was not released at 225 F. and no heat lost 
 by radiation the original temperature (335 F.) would be obtained again if 
 the piston would compress the steam back again to the original volume. 
 
 Q. 20. Describe a gravity heating system. 
 
 Ans. 20. A gravity heating system is a system where the steam, after 
 condensation in the radiating surfaces, will, in the form of condensation be 
 returned by gravity to the boiler, the boiler being the lowest part of the 
 system. The returns may also return to any suitable receptacle and enter 
 the boiler by means of a pump, in which case, the boiler may be located at 
 any point.
 
 Q. 21. Describe a vacuum heating system. 
 
 Ans. 21. A vacuum heating system has its returns exhausted by means 
 of a pump or ejector, creating a vacuum in the system. When exhaust steam 
 of low pressure is used this is very efficient, as the steam circulates thor- 
 oughly and rapidly. Steam at a pressure below the atmosphere can be used 
 if the pump or ejector handling the returns maintains a vacuum of suf- 
 ficient degree. In some cases a vacuum of 8 to 10 inches is maintained in 
 the exhaust pipe of the engine. In order to secure this result the system must 
 be free from all leaks, and a sufficient radiating surface must be available 
 to condense the exhaust steam. 
 
 Q. 22. Give several simple and easily applied tests whereby the hardness 
 of boiler feed water, or the presence of acid in same, may be detected. 
 
 Ans. 22. A few drops of a solution of good soap in alcohol if put in a 
 vessel of water will turn it quite milky if the water is hard, and if soft will 
 remain clear. The harder the water the less effect the soap has on it be- 
 cause the mineral matter neutralizes so much of it. Water which will turn 
 blue litmus paper red before boiling the water but not after boiling contains 
 carbonic acid. 
 
 Q. 23. In making a calorimeter test, what is the best method of se- 
 curing a fair sample of the steam passing through the pipe from which sam- 
 ple is to be taken ? 
 
 Ans. 23. A barrel calorimeter test is one of the best methods. It con- 
 sists of a barrel that will hold 400 or 500 pounds of water placed on plat- 
 form scales. A pipe or hose leading into it from the source of steam supply, 
 as near the throttle as possible. A valve to admit steam when needed. The 
 pipe or hose should be perforated and closed at end. A thermometer is also 
 used to show the difference in the temperature of the water before and after 
 the steam is admitted to the water. 
 
 Q. 24. What is a draft gauge, how is it constructed, and how is it used? 
 
 Ans. 24. A draft gauge is an instrument used to ascertain the amount 
 of draft in a chimney or uptake of a boiler. This instrument is made in 
 various forms, but all work on the same principle. In its simplest form it 
 consists of a U-shaped graduated glass tube partially filled with water, one 
 end of which is connected by means of a. suitable piece of flexible tubing or 
 pipe, to the chimney or uptake the draft of which is to be ascertained; the 
 other end of the glass tube should be open to the atmosphere. The differ- 
 ence in the height of the water in the two legs of the tube is the measure- 
 ment of the draft, and is stated in inches. 
 
 Q. 25. Describe the construction and operation of a steam pressure 
 gauge. Why is a loop used in connecting the gauge to the boiler? 
 
 Ans. 25. Steam gauges are constructed with a tube nearly elliptical in 
 cross section. This tube is bent nearly into a circle; as pressure is admitted 
 inside the tube it has a tendency to straighten out, which is resisted by its 
 own stiffness. The motion of the end of the tube is communicated to a 
 pointer by a rack and pinion. A loop or syphon is placed in the connection 
 between the boiler and steam gauge to trap water in the pipe so that the 
 steam cannot enter the tube and thereby affect its stiffness. 
 
 42
 
 Q. 26. Is there any difference in the construction and principle of opera- 
 tion between pressure and vacuum gauges? 
 
 Ans. 26. There is no difference in the construction and principle of 
 pressure gauges and vacuum gauges. Any pressure gauge will indicate a 
 vacuum by allowing the pointer to travel below the zero mark. However, 
 in order to correctly read the degree of vacuum, the gauge dial would have 
 to be properly graduated. In a vacuum gauge the pointer is, by suitable 
 connection to the elliptical tube, made to travel from left to right, the same 
 as the pointer in a steam gauge, and reads from to 30, representing inches 
 of vacuum. The reading from left to right is simply a matter of con- 
 venience. 
 
 Q. 27. What is a compound gauge, and where is it ordinarily used? 
 
 Ans. 27. The compound gauge has its dial graduated in such a manner 
 that both pressure above the atmosphere, as well as pressure below the at- 
 mosphere, can be read from it. Its dial has the zero mark somewhere near 
 the top, reading to the left, from to 30, representing inches of vacuum, and 
 to the right, reading pounds of pressure above atmosphere. Sometimes, in 
 compound gauges, the vacuum is also indicated in pounds, reading, of course, 
 from to 15. Compound gauges are necessary where the pressure ranges 
 below, as well as above, the atmosphere pressure. The receivers of com- 
 pound engines are usually fitted with compound gauges.
 
 Electricity. 
 
 Q. 1. Define, in a general way, the difference between direct current 
 and alternating current. 
 
 Ans. 1. Direct current is that which flows continuously in one direction. 
 
 Alternating current is that which changes its direction of flow; this 
 change of direction may vary from twenty-five to ten thousand times a 
 second. 
 
 Q. 2. What is a solenoid, and for what purposes is such a device best 
 adapted? 
 
 Ans. 2. A solenoid is an electric magnet made out of a hollow core 
 wound with insulated wire, and although not as strong as a magnet with a 
 solid core would be, owing to the fact that the armature of the magnet 
 can have a long range of action and without excessive variation in the pull 
 exerted upon it by the coil, a solenoid is preferable where long range of 
 armature action is desired. Arc lamps and various electrical instruments 
 are equipped with a solenoid. 
 
 Q. 3. What is meant by the term "booster set," and under what con- 
 ditions is it advantageous to use such apparatus in electric lighting or 
 power work? 
 
 Ans. 3. A " booster ' ' set consists, usually, of a motor and generator 
 mounted upon the same shaft, the motor using station voltage, and the gen- 
 erator also receiving station voltage at its negative terminals and raising, 
 or boosting, it up to a higher voltage. 
 
 In electric lighting and electric power work, this method is often used 
 lo send current to outlying districts where the long distance transmission 
 would cause a sufficient drop in voltage, from that at station, to give poor 
 service. 
 
 Q. 4. What is an electric step-up transformer? 
 
 Ans. 4. Step-up transformers consist of an iron core made of thin 
 sheets, on which are wound two sets of coils, called the primary and sec- 
 ondary windings; the primary windings, supplied by the lower potential, 
 creates lines of force in the core which may be considered to continuously 
 expand and contract, rapidly. 
 
 These lines of force are "cut" by the secondary windings and, conse- 
 quently, an electromotive is induced in the secondary winding, which fur- 
 nishes current to the high pressure mains. 
 
 It may be said that step-down transformers are constructed on similar 
 lines, the only difference being in the method of winding the primary and 
 secondary coils. 
 
 44
 
 Q. 5. Why is direct current required to excite the fields of an alter- 
 nating current generator? 
 
 Ans. 5. It requires current flowing continuously in the same direction 
 to excite the fields of any magnet; if alternating current were used, the field 
 would lose its magnetism at each alternation of the current, at the zero 
 point. Alternating current dynamos derive the direct current necessary for 
 their fields from a direct current dynamo, known as the exciter. 
 
 Q. 6. Describe the material used in the construction of an electro-mag- 
 net, also the method of constructing the magnet, and state what limits the 
 magnetic force of an electro-magnet. 
 
 Ans. 6. Iron is used for commercial electro-magnets, as it remains a 
 magnet only so long as current flows around it, whereas steel would for a 
 long while retain the magnetic qualities after once being induced. The 
 magnetic force is limited by the quantity of current flowing around the mag- 
 netic core and the amount of iron and its permeability contained in the core 
 of the magnet. 
 
 Q. 7. What voltage is most economical for use on a combination light- 
 ing and motor load, and why? 
 
 Ans. 7. The most economical would be 220 volt direct current (3) three 
 wire system on account of cheapness to install. 
 
 Q. 8. Explain the meaning of volt, ampere and ohm. 
 
 Ans. 8. (a). The volt is the unit of electromotive force, and can best 
 be compared with the pound as used in connection with steam, water or air 
 pressures ; it represents the difference in potential which tends to force a 
 flow of current through a conductor. 
 
 (b). The ampere is a term used for the quantity of current flowing in 
 a circuit, and is the accepted unit of quantity. 
 
 (c). The ohm is the unit whereby the resistance in an electric circuit is 
 measured. 
 
 The three foregoing terms bear a close relationship one with the other. 
 
 Q. 9. In what way do ohms affect amperes? 
 
 Ans. 9. The increase or diminishing of the number of ohms will di- 
 rectly affect the number of amperes; in other words, the current varies in- 
 versely with the resistance. 
 
 Q. 10 W T hat is meant by the terms of (a) natural magnet and (b) an 
 electro or induced magnet? 
 
 Ans. 10. (a). A natural magnet is a magnet that exists in a natural 
 state, such as magnetic ore, generally called the lodestone. 
 
 (b). An electro or induced magnet is a magnet only while an electric 
 current is passed around it by means of windings of electric wire, or if a 
 substance lays in a field of magnetic force and thereby becomes magnetized. 
 
 45
 
 Q. 11. What class of apparatus is generally found in sub-stations for 
 the transmission of electricity, and what are the separate functions of each 
 piece of apparatus? 
 
 Ans. 11. Sub-stations apparatus differs according to conditions, but one 
 or more of the following will be found: 
 
 Step-down transformers, to reduce voltage. 
 
 Eotary converters to change the current from A. C. to D. C. current. 
 
 Frequency changer to change to lower frequency where motor load only 
 is used. 
 
 Boosters to raise voltage on line. 
 
 Storage batteries to relieve generator during heavy loads, also to steady 
 the load where variation is great. 
 
 Lightning arresters. And switch-board with controlling apparatus for 
 whatever kind installed. 
 
 Q. 12. Explain what is meant by electric lamps placed in series, and 
 how it affects the voltage and candle-power. 
 
 Ans. 12. Lamps placed in series means that they are placed one after 
 another on the same circuit, the current in the circuit passing through each 
 lamp. For illustration, five 110 volt 16 candle power lamps, each using one- 
 half ampere, are to be put on a circuit where the voltage is 550; each lamp 
 is then in series and uses current at a potential of 110 volts, thus dividing 
 the potential of 550 equally among the five lamps. The power used in such 
 a case would be 5 X. 5X110=275 watts. 
 
 Q. 13. Given a compound D. C. generator, running in multiple, wired 
 up in the usual way; if the circuit breaker opens and the main switch is 
 pulled, while machine is still running, what causes the pilot lamp to ex- 
 plode; and what is the remedy? 
 
 Ans. 13. In the wiring up of the generator only one shunt field wire 
 is run from switchboard to generator, this wire is connected to the machine 
 lead next to machine under the fuse. If circuit breaker is placed on the 
 generator and it opens, the shunt field will still be fed from the bus bar, if 
 the main switch is pulled it opens the shunt field. The pilot light is wired 
 from the two machine leads; when main switch is pulled the discharge or 
 kick from the fields explodes the lamp. To remedy the trouble either change 
 the circuit breaker to where it will not cut the field away from the arma- 
 ture when it opens or cut the field wire off of the machine lead and run two 
 wires to the generator; tap one at the top of circuit breaker, or next to the 
 generator, connect this wire to rheostat, tap the other wire to the shunt 
 field so as to allow the armature to absorb the kick; the opening of the 
 breaker will have no effect on the pilot-light. 
 
 Q. 14. What is meant by the term "compound wound electric genera- 
 tort" What feature of construction would determine in your opinion that 
 a generator was compound wound? 
 
 Ans. 14. It is meant that this generator has its field magnets wound 
 with two sets of coils, one of which is connected in series, and the other one 
 in parallel, with the armature and the external circuit. 
 
 By noting how the wiring from the field magnets and the armature wires 
 or cables are connected up. 
 
 46
 
 Q. 15. What is meant by the term "constant current generators!" 
 
 Ans. 15. A constant current generator is one which does not vary; al- 
 though the voltage may vary the amount of current is constant. 
 
 Q.' 16. Explain the term of neutral point in connection with electric 
 generators. 
 
 Ans. 16. The neutral points of a generator are the positions on the 
 commutator between which the difference in potential is greatest, and where 
 there is the least difference in potential between adjacent bars. These points 
 are diametrically opposite. 
 
 Q. 17. Explain the term lead in connection with electric generators. 
 
 Ans. 17. Lead is the term applied to the slight forward movement, 
 which it is necessary to give the brushes in order to avoid sparking with the 
 increase of load, due to the fact of a magnetic reaction of the armature due 
 to the heavier load. Increase the lead in the direction of rotation ; decrease 
 in the opposite direction. 
 
 Q. 18. What are the conditions when an electric generator is given: 
 (a) More lead! (b) Less lead? 
 
 Ans. 18. (a). An increase of load, 
 (b). A decrease of load. 
 
 Q. 19. With a generating unit consisting of a cross-compound engine 
 of the Corliss type, and an alternator, describe method of starting same, 
 bringing it up to speed and cutting it in on the load. This unit is supposed 
 to operate in conjunction with others. 
 
 Ans. 19. Start up the condenser and turn on steam to the high pressure 
 cylinder and use the bypass to the low pressure cylinder. Let the engine 
 warm up for ten minutes or so, and while engine is warming, oil up. Then- 
 start engine, running slowly for about 15 minutes, then bring engine up to 
 speed, throw in field switch, build up voltage and when in step with other 
 generator throw in main switch. 
 
 Q. 20. Can a D. C. compound wound motor of large size be started 
 under full load, without a starting box? 
 
 Ans. 20. Yes; by disconnecting the shunt and starting as a series mo- 
 tor after it is up to speed or nearly so put in the shunt field. 
 
 Q. 21. Explain the method of winding electric motors of the following 
 types: 
 
 (a). Shunt wound, 
 (b). Series wound, 
 (c). Compound wound. 
 
 Ans. 21. (a). In a shunt-wound motor the current for exciting the 
 fields is taken from the main circuit, but only in sufficient amount for ex- 
 citation purposes, and forms a by-path in parallel with the main circuit. 
 
 47
 
 (b) In a series-wound motor the whole of the main circuit passes 
 through the wires conveying the current to excite the fields. 
 
 (c) In a compound-wound motor there are two circuits, one containing 
 many turns of small wire, through which part of the main current passes, 
 and another consisting of a lesser number of turns of large wire, through 
 which the whole of the main circuit passes, with the exception of the amount 
 passing through the circuit formed by the smaller wires. This type is a 
 combination of the shunt and series types, as described in (a) and (b). 
 
 Q. 22. What effect does the strength of the fields have upon the speed 
 of a direct current motor? 
 
 Ans. 22. Decreasing the strength of the fields increases the speed of 
 the motor, and increasing the strength of the fields decreases the speed. 
 
 Q. 23. What is the difference between a synchronous motor, and an in- 
 duction motor? 
 
 Ans. 23. A synchronous motor has its field excited from some direct 
 current source, while its armature takes current oflf the alternating current 
 line; whereas the fields of an induction motor are supplied with alternating 
 current, and the armature is not connected to any source of current, the cur- 
 rent being induced by the field.
 
 The National Association of Stationary Engineers. 
 
 ORGANIZED OCTOBER, 1882. INCORPORATED OCTOBER, 1892. 
 
 Four Hundred and Fifty Subordinate Associations with Twenty Thousand Members in Forty- 
 Eight States and Territories. 
 
 PEEAMBLE. 
 
 This Association shall at no time be used for the furtherance of strikes, 
 or for the purpose of interfering in any way between its members and their 
 employers in regard to wages; recognizing the identity of interests between 
 employer and employe, and not countenancing any project or enterprise that 
 will interfere with perfect harmony between them. 
 
 Neither shall it be used for political or religious purposes. Its meetings 
 shall be devoted to the business of the Association, and at all times prefer- 
 ence shall be given to the education of engineers, and to securing of the 
 enactment of engineers' license laws in order to prevent the destruction of 
 life and property in the generation and transmission of steam as a motive 
 power. 
 
 FORMER PRESIDENTS AND YEARS OF SERVICE. 
 
 1882-3. H. D. Cozens Providence, R. I. 
 
 1883-4. James G. Beckerleg Chicago, 111. 
 
 1884-5. R. J. Kilpatrick St. Louis, Mo. 
 
 1885-6. James G. Beckerleg Chicago, III. 
 
 1886-7. F. A. Foster Bridgeport, Conn. 
 
 1887. G. M. Barker Boston, Mass. 
 
 1888. R. O. Smith New York City 
 
 1889. John Fehrenbatch Cincinnati, O. 
 
 1890. J. J. Illingworth Utica, N. T. 
 
 1891. William Powell Cleveland, O. 
 
 1892. C. W. Naylor Chicago, 111. 
 
 1893. James D. Lynch Philadelphia, Pa. 
 
 1894. M. D. Nagle New York City 
 
 1895. Charles H. Garlick Pittsburg, Pa. 
 
 1896. J. W. Lane Providence, R. I. 
 
 1897. C. A. Collett St. Louis, Mo. 
 
 1898. W. T. Wheeler New York City 
 
 1899. Herbert E. Stone Cambridge, Mass. 
 
 1900. P. E. Leahy New York City 
 
 1901. E. G. Jacques Detroit, Mich. 
 
 1902. R. G. Ingleson Cleveland, O. 
 
 1903. P. F. Hogan, Boston, Mass. 
 
 1904. C. F. Wilson Milwaukee, Wis. 
 
 1905. R. D. Tomlinson New York City 
 
 1906. T. N. Kelsey Lowell, Mass. 
 
 1907. J. F. Carney New York City 
 
 49
 
 RULES FOB CONDUCTING BOILER TRIALS, FORMULATED BY 
 
 THE AMERICAN SOCIETY OF MECHANICAL ENGINEERS. 
 
 KNOWN AS THE CODE OF 1899. 
 
 I. DETERMINE AT THE OUTSET the specific object of the proposed trial, 
 whether it be to ascertain the capacity of the boiler, its efficiency a3 a 
 steam generator, its efficiency and its defects under usual working con- 
 ditions, the economy of some particular kind of fuel, or the effect of 
 changes of design, proportion, or operation; and prepare for the trial 
 accordingly. 
 
 II. EXAMINE THE BOILER, both outside and inside; ascertain the 
 dimensions- of grates, heating surfaces, and all important parts; and 
 make a full record describing the same, and illustrating special features 
 by sketches. The area of heating surface is to be computed from the 
 surfaces of shells, tubes, furnaces, and fire-boxes in contact with the 
 fire or hot gases. The outside diameter of water-tubes and the inside 
 diameter of fire-tubes are to be used in the computation. All surfaces 
 below the mean water level which have water on on side and products 
 of combustion on the other are to be considered as water heating sur- 
 face, and all surfaces above the mean water level which have steam on 
 one side and products of combustion on the other are to be considered 
 as superheating surface. 
 
 III. NOTICE THE GENERAL CONDITION of the boiler and its equipment, 
 and record such facts in relation thereto as bear upon the objects in 
 view. 
 
 If the object of the trial is to ascertain the maximum economy or 
 capacity of the boiler as a steam generator, the boiler and all its appur- 
 tenances should be put in first class condition. Clean the heating sur- 
 face inside and outside, remove clinkers from the grates and from the 
 sides of the furnace. Remove all dust, soot, and ashes from the cham- 
 bers, smoke connections and flues. Close air leaks in the masonry and 
 poorly fitted cleaning doors. See that the damper will open wide and 
 close tight. Test for air leaks by firing a few shovels of smoky fuel 
 and immediately closing the damper, observing the escape of smoke 
 through the crevices, or by passing the flame of a candle over cracks 
 in the brickwork. 
 
 IV. DETERMINE THE CHARACTER OF THE COAL to be used. For tests 
 of the efficiency or capacity of the boiler for comparison with other boil- 
 ers, the coal should, if possible, be of some kind which is commercially 
 regarded as a standard. For New England and that portion of the 
 country east of the Allegheny Mountains, good anthracite egg coal, 
 containing not over ten per cent, of the ash, and the semi-bituminous Clear- 
 field, (Pa.), Cumberland (Md.), and Pocahontas (Va.), are thus regarded. 
 West of the Allegheny Mountains, Pocahontas, (Va.), and New River, 
 (W. Va.), semi-bituminous, and Youghiogheny or Pittsburg bituminous 
 coals are recognized as standards. There is no special grade of coal 
 mined in the Western States which is widely recognized as of superior 
 quality or considered as a standard coal for boiler testing. Big Muddy 
 lump, an Illinois coal mined in Jackson County, 111., is suggested as being 
 of sufficiently high grade to answer these requirements in districts where 
 
 50
 
 it is more conveniently obtainable than the other coals mentioned above. 
 For tests made to determine the performance of a boiler with a par- 
 ticular kind of coal, such as may be specified in a contract for the sale 
 of a boiler, the coal used should not be higher in ash and in moisture 
 than that specified, since increase in ash and moisture above a stated 
 amount is apt to cause a falling off of both capacity and economy in 
 greater proportion than the proportion of such increase. 
 
 V. ESTABLISH THE CORRECTNESS OF ALL APPARATUS used in the test 
 for weighing and measuring. These are: 
 
 1. Scales for weighing coal, ashes, and water. 
 
 2. Tanks, or water-meters, for measuring water. Water-meters, as 
 a rule should be used only as a check on other measurements. For 
 accurate work, the water should be weighed or measured in a tank. 
 
 3. Thermometers and pyrometers for taking temperatures of air, 
 steam, feed-water, waste gases, etc. 
 
 4. Pressure gauges, draught gauges, etc. 
 
 The kind and location of the various pieces of testing apparatus 
 must be left to the judgment of the person conducting the test; always 
 keeping in mind the main object, that is, to obtain authentic data. 
 
 VT. SEE THAT THE BOILER IS THOROUGHLY HEATED to its USUal working 
 
 temperature before the trial. If the boiler is new and of a form provided 
 with a brick setting, it should be in regular use at least a week before 
 the trial, so as to dry and heat the walls. If it has been laid off and 
 become cold, it should be worked before the trial until the walls are 
 well heated. 
 
 VII. THE BOILER AND CONNECTIONS should be proved to be free from 
 leaks before beginning a test, and all water connections, including below 
 and extra feed pipes, should be disconnected, stopped with blank flanges, 
 or bled through special openings beyond the valves, except the particular 
 pipe through which water is fed to the boiler during the trial. During 
 the test the blow-off and feed pipes should remain exposed to view. 
 
 If an injector is used, it should receive steam directly through a felted 
 pipe from the boiler being tested.* 
 
 If the water is metered after it passes the injector, its temperature 
 should be taken at the point where it leaves the injector. If the quantity 
 is determined before it goes to the injector the temperature should be 
 determined on the suction side of the injector, and if no change of tem- 
 perature occurs other than that due to the injector, the temperature thus 
 determined is properly that of the feed water. When the temperature 
 changes between the injector and the boiler, as by the use of a heater 
 or by radiation, the temperature at which the water enters and leaves 
 the injector and that at which it enters the boiler should all be taken. 
 In that case the weight to be used is that of the water leaving the 
 injector, computed from the heat units if not directly measured, and the 
 temperature, that of the water entering the boiler. 
 
 Let w=weight of water entering the injector. 
 a;=weight of steam entering the injector. 
 
 ^j=heat units per pound of water entering the injector. 
 
 7ij=heat units per pound of steam entering the injector. 
 
 A 3 =heat units per pound of water leaving injector. 
 Then w+x weight of water leaving injector. 
 
 * In feeding a boiler undergoing test with an injector taking steam from another 
 boiler, or from the main steam pipe from several boilers, the evaporative results may 
 be modified by a difference in the quality of the steam from such source compared with 
 that supplied by the boiler being tested, and in some cases the connection to the 
 injector may act as a drip for the main steam pipe. If it is known that the steam 
 from the main pipe is of the same pressure and quality as that furnished by the boiler 
 undergoing the test, the steam may be taken from such main pipe. 
 
 51
 
 A.-A. 
 
 See that the steam main is so arranged that water of condensation 
 cannot run back into the boiler. 
 
 VIII. DURATION OF THE TEST For tests made to ascertain either the 
 maximum economy or the maximum capacity of a boiler, irrespective of 
 the particular class of service for which it is regularly used, the duration 
 should be at least ten hours of continuous running. If the rate of com- 
 bustion exceeds 25 pounds of coal per square foot of grate surface per 
 hour, it may be stopped when a total of 250 pounds of coal has been 
 burned per square foot of grate. 
 
 In cases where the service requires continuous running for the whole 
 24 hours of the day, with shifts of firemen a number of times during that 
 period, it is well to continue the test for at least 24 hours. 
 
 When it is desired to ascertain the performance under the working 
 conditions of practical running, whether the boiler be regularly in use 
 24 hours a day or only a certain number of hours out of each 24, the fires 
 being banked the balance of the time, the duration should not be less 
 than 24 hours. 
 
 IX. STARTING AND STOPPING A TEST 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. Two methods of obtaining the desired equality of 
 conditions of the fire may be used, viz.; those which were called in the 
 Code of 1885 "the standard method" and "the alternate method," the 
 latter being employed where it is inconvenient to make use of the standard 
 method, t 
 
 X. STANDARD METHOD OF STARTING AND STOPPING A TEST 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 and 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, which has been burned 
 low, clean the grates and ash-pit, and note the water level when the water 
 is in a quiescent state, and record the time of hauling the fire. 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 the pump after the test is completed. 
 
 XI. ALTERNATE METHOD OF STARTING AND STOPPING A TEST. The boiler 
 being thoroughly heated by a preliminary run, the fires are to be burned 
 low and well cleaned. Note the amount of coal left on the grate as nearly 
 as it can be estimated; note the pressure of steam and the water level. 
 Note the time and record it as the starting time. 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 fire's 
 should be burned low, just as before the start, and the fires cleaned in 
 
 t The Committee concludes that It is best to retain the designations "standard" 
 and "alternate," since they have become widely known and established in the minds 
 of engineers and in the reprints of the Code of 18R5. Many engineers prefer the 
 "alternate" to the "standard" method on account of Its being less liable to error 
 due to cooling of the boiler at the beginning and end of a test. 
 
 * The gauge-glass should not be blown out within an hour before the water levpl 
 Is taken at the beginning and end of test, otherwise an error in the reading of tho 
 water level may be caused by a change in the temperature and density of the water in 
 the pipe leading from the bottom of the glass into the boiler. 
 
 52
 
 such a manner as to leave a bed of coal on the grates of the same depth, 
 and in the same condition, as at the start. When this stage is reached, 
 note the time and record it as the stopping time. The water level and 
 steam pressures should previously be brought as nearly as possible to 
 the same point as at the start. If the water level is not the same as at 
 the start, a correction should be made by computation, and not by opera- 
 ting the pump after the test is completed. 
 
 XII. UNIFORMITY op CONDITIONS In all trials made to ascertain 
 maximum economy or capacity, the conditions should be maintained uni- 
 formly constant. Arrangements should be made to dispose of the steam 
 so that the rate of evaporation may be kept the same from beginning 
 to end. This may be accomplished in a single boiler by carrying the steam 
 through a waste-steam pipe, the discharge from which can be regulated 
 as desired. In a battery of boilers, in which only one is tested, the 
 draft may be regulated on the remaining boilers, leaving the test boiler 
 to work under a constant rate of production. 
 
 Uniformity of conditions should prevail as to the pressure of steam, 
 the height of water, the rate of evaporation, the thickness of fire, the 
 times of firing and the quantity of coal fired at one time, and as to the 
 intervals between the times of cleaning the fires. 
 
 The method of firing to be carried on in such tests should be dictated 
 by the expert or person in responsible charge of the test, and the method 
 adopted should be adhered to by the fireman throughout the test. 
 
 XIII. KEEPING THE RECORDS Take note of every event connected with 
 the progress of the trial, however unimportant it may appear. Kecord the 
 time of every occurrence and the time of taking every weight and every 
 observation. 
 
 The coal should be weighed and delivered to the fireman in equal 
 proportions, each sufficient for not more than 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 last of each 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 evap- 
 orated by successive portions of coal, the test may be divided into several 
 periods if desired, and the degree of uniformity of combustion, evapora- 
 tion, and economy analyzed for each period. In addition to these records 
 of the coal and the feed water, half hourly observations should be made 
 of the temperature of the feed water, of the flue-gases, of the external 
 air in the boiler room, of the temperature of the furnace when a furnace 
 pyrometer is used, also of the pressure of steam, and of the readings of 
 the instruments for determining the moisture of the steam. A log shouM 
 be kept on properly prepared blanks containing columns for record of 
 the various observations. 
 
 When the "standard method" of starting and stopping the test is 
 used, the hourly rate of combustion and evaporation and the horse- 
 power should be computed from the records taken during the time when 
 the fires are in active condition. This time is somewhat less than the 
 actual time which elapses between the beginning and end of the run. The 
 loss of time due to kindling the fire at the beginning and burning it out 
 at the end makes this course necessary. 
 
 XIV. QUALITY OF STEAM The percentage of moisture in steam should 
 be determined by the use of either a throttling or a separating steam 
 calorimeter. The sampling nozzle should be placed in the vertical steam 
 pipe rising from the boiler. It should be made of lA-inch pipe, and should 
 extend across the diameter of the steam pipe to within half an inch 
 of the opposite side, being closed at the end and perforated with not less 
 
 53
 
 than twenty %-inch holes equally distributed along and around its cylin- 
 drical surface, but none of these holes should be nearer than i^-inch 
 to the inner side of the steam pipe. The calorimeter and the pipe lead- 
 ing to it should be well covered with felting. Whenever the indications of 
 the throttling or separating calorimeter show that the percentage of 
 moisture is irregular, or occasionally in excess of three per cent., the 
 results should be checked by a steam separator pNced in the steam pipe 
 as close to the boiler as convenient, with a calorimeter in the steam pipe 
 just beyond the outlet from the separator. The drip from the separator 
 should be caught and weighed, and the percentage of moisture computed 
 therefrom added to that shown by the calorimeter. 
 
 Superheating should be determined by means of a thermometer placed 
 in a mercury-well inserted in the steam pipe. The degree of superheating 
 should be taken as the difference between the reading of the thermometer 
 for superheated steam and the readings of the same thermometer of sat- 
 urated steam at the same pressure as determined by a special experiment, 
 and not by reference to steam tables. 
 
 XV. SAMPLING THE COAL AND DETERMINING ITS MOISTURE As each 
 barrow load or fresh portion of coal is taken from the coal pile, a repre- 
 sentative shovelful is selected from it and placed in a barrel or box in 
 a cool place and kept until the end of the trial. The samples are then 
 mixed and broken into pieces not exceeding one inch in diameter, and 
 reduced by the processes of repeated quartering and crushing until a final 
 sample weighing about five pounds is Obtained, and the size of the larger 
 pieces is such that they will pass through a sieve with %-inch meshes. 
 From this sample two one-quart, air-tight glass preserving jars, or other 
 air-tight vessels which will prevent the escape of moisture from the 
 sample, are to be promptly filled, and these samples are to be kept for sub- 
 sequent determinations of moisture and of heating value and for chemi- 
 cal analyses. During the process of quartering, when the sample has been 
 reduced to about 100 pounds, a quarter to a half of it may be taken 
 for an approximate determination of moisture. This may be made by 
 placing it in a shallow iron pan, not over three inches deep, carefully 
 weighing 'it and setting the pan in the hottest place that can be found 
 on the brickwork of the boiler setting or flues keeping it there for at least 
 12 hours, and then weighing it. The determination of moisture thus 
 made is believed to be approximately accurate for anthracite and semi- 
 bituminous coals, and also for Pittsburg or Youghiogheny coal; but it can- 
 not be relied upon for coals mined west of Pittsburg, or for other coals 
 containing inherent moisture. For these latter coals it is important that 
 a more accurate method be adopted. The method recommended by the 
 Committee for all accurate tests, whatever the character of the coal, 
 is described as follows: 
 
 Take one of the samples contained in the glass jars, and subject it to 
 a thorough air drying, by spreading it in a thin layer and exposing it for 
 several hours to the atmosphere of a warm room, weighing it before and 
 after, thereby determining the quantity of the surface moisture it con- 
 tains. Then crush the whole of it by running through an ordinary coffee 
 mill adjusted so as to produce somewhat coarse grains (less than 1-16 
 inch), thoroughly mix the crushed sample, select from it a portion of from 
 10 to 50 grams, weigh it in a balance which will easily show a variation 
 as small as 1 part in 1,000, and dry it in an air or sand bath at a temper- 
 ature between 240 and 280 degrees Fahr. for one hour. Weigh it and 
 record the loss, then heat and weigh it again repeatedly, at intervals of 
 an hour or less, until the minimum weight has been reached and the weight 
 begins to increase by oxidation of a portion of the coal. The difference 
 between the original and the minimum weight is taken as the moisture 
 in the air-dried coal. This moisture test should preferably be made 
 on duplicate samples, and the results should agree within 0.3 to 0.4 of 
 one per cent., the mean of the two determinations being taken as the 
 
 54
 
 correct result. The sum of the percentage of moisture thus found and the 
 percentage of surface moisture previously determined is the total moist- 
 ure. 
 
 XVI. TREATMENT OP ASHES AND REFUSE The ashes and refuse are to 
 be weighed in a dry state. If it is found desirable to show the principal 
 characteristics of the ash, a sample should be subjected to a proximate 
 analysis and the actual amount of incombustible material determined. 
 For elaborate trials a complete analysis of the ash and refuse should be 
 made. 
 
 XVII. CALORIC TESTS AND ANALYSIS OF COAL. The quantity of the fuel 
 should be determined either by heat test or by analysis, or by both. 
 
 The rational method of determining the total heat of combustion is 
 to burn the sample of coal in an atmosphere of oxygen gas, the coal to be 
 sampled as directed in Article XV of this code. 
 
 The chemical analysis of the coal should be made only by an expert 
 chemist. The total heat of combustion computed from the results of the 
 ultimate analysis may be obtained by the use of Dulong's formula, pages 
 106 and 131. 
 
 It is desirable that a proximate analysis should be made, thereby 
 determining the relative proportions of volatile matter and fixed carbon. 
 These proportions furnish an indication of the leading characteristics of 
 the fuel, and serve to fix the class to which it belongs. As an additional 
 indication of the characteristics of the fuel, the specific gravity should 
 be determined. 
 
 XVIII. ANALYSIS OF FLUE GASES The analysis of the flue gases is 
 an especially valuable method of determining the relative value of differ- 
 ent 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. The com- 
 position is also apt to vary from minute to minute, and for this reason the 
 drawings of gas should last a considerable period of time. Where com- 
 plete determinations are desired, the analyses should be intrusted to an 
 expert chemist. For approximate determinations the Orsat or the Hem- 
 pel apparatus may be used by the engineer. 
 
 For a continuous indication of the amount of carbonic acid (CO 2 ) pres- 
 ent in the flue-gases, an instrument may be employed which shows the 
 weight of the sample of gas passing through it. 
 
 XIX. SMOKE OBSERVATIONS It is desirable to have a uniform sys- 
 tem of determining and recording the quantity of smoke produced where 
 bituminous coal is used. The system commonly employed is to express 
 the degree of smokiness by means of percentages dependent upon the 
 judgment of the observer. The Committee does not place much value 
 upon a percentage method, because it depends so largely upon the personal 
 element, but if this method is used, it is desirable, that so far as possible, 
 a definition be given in explicit terms as to the basis and method employed 
 in arriving at the percentage. The actual measurement of a sample of 
 soot and smoke by some form of meter is to be preferred. 
 
 XX. MISCELLANEOUS In tests for purposes of scientific research, in 
 which the determination of all the valuables entering into the test is 
 desired, certain observations should be made which are in general 
 unnecessary for ordinary tests. These are the measurements of the air 
 supply, the determination of its contained moisture, the determination 
 of the amount of heat lost by radiation, of the amount of infiltration 
 of air through the setting, and (by condensation of all the steam made 
 by the boiler) of the total heat imparted to the water. 
 
 As these determinations are rarely undertaken, it is not deemed 
 advisable to give directions for making them. 
 
 55
 
 XXI. CALCULATIONS OF EFFICIENCY Two methods of defining and cal- 
 culating the efficiency of a boiler are recommended. They are: 
 
 1. Efficiency of the boiler 
 
 _Heat absorbed per Ib. combustible 
 "Caloric value of 1 Ib. combustible. 
 
 2. Efficiency of the boiler and grate 
 
 _Heat absorbed per Ib. coal 
 ""Caloric value of 1 Ib. coal. 
 
 The first of these is sometimes called the efficiency based on combus- 
 tible, and the second efficiency based on coal. The first is recommended 
 as a standard of comparison for all tests, and this is the one which is 
 understood to be referred to when the word "efficiency" alone is used 
 without qualification. The second, however, should be included in a report 
 cf a test, together with the first, whenever the object of the test is to deter- 
 mine the efficiency of the boiler and the furnace together with the grate (or 
 mechanical stoker), or to compare different furnaces, grates, fuels or methods 
 of firing. 
 
 The heat absorbed per pound of combustible (or per pound of coal) 
 is to be calculated by multiplying the equivalent evaporation from and 
 at 212 degrees per pound combustible (or coal) by 965.7. 
 
 XXII. THE HEAT BALANCE An approximate "heat balance," or state 
 ment of the distribution of the heating value of the coal among the 
 several items of heat utilized and heat lost may be included in the report 
 of a test when analyses of the fuel and of the chimney-gases have been 
 made. The methods of computing the heat balance and the form in which 
 it should be reported, are given in chapter on Steam Boiler Efficiency. 
 
 XXIII. REPORT OF THE TRIAL The data and results should be reported 
 in the manner given in either one of the two following tables, omitting 
 lines where the tests have not been made as elaborately as provided for in 
 such tables. Additional lines may be added for data relating to the 
 specific object of the test. The extra lines should be classified under the 
 headings provided in the tables, and numbered as per preceding line, 
 with sub-letters a, ~b, etc. The Short Form of Eeports is recommended 
 for commercial tests and as a convenient form of abridging the longer 
 form of publication when saving space is desirable. For elaborate trials, 
 it is recommended that the full log of the trial be shown graphically, by 
 means of a chart. 
 
 DATA AND RESULTS OF EVAPORATIVE TEST. 
 
 Made by of boiler at to 
 
 determine 
 
 Principal conditions governing the trial 
 
 Kind of fuel. 
 
 Kind of furnace 
 
 State of the weather 
 
 Method of starting and stopping the test ("standard" or "alternate," 
 Art. X and XI, Code) 
 
 1. Date of trial 
 
 2. Duration of trial hours. 
 
 Dimensions and Proportions. 
 
 (A complete description of the boiler, and drawings of the same if of 
 unusual type, should be given on an annexed sheet.) 
 
 3. Grate surface width length area sq. ft. 
 
 4. Height of furnace ins 
 
 5. Approximate width of air spaces in grate in. 
 
 56
 
 6. Proportion of air space to whole grate surface per cent. 
 
 7. Water-heating surface sq. ft. 
 
 8. Superheating surface sq. ft. 
 
 9. Ratio of water-heating surface to grate surface to 1. 
 
 10. Ratio of minimum draft area to grate surface 1 to . 
 
 Average Pressures. 
 
 11. Steam pressure by gauge Ibs. per sq. in. 
 
 12. Draft between damper and boiler ins. of water 
 
 13. Force of draft in furnace ins. of water 
 
 14. Force of draft or blast in ash-pit ins. of water 
 
 Average Temperatures. 
 
 1 5. Of external air deg. 
 
 16. Of fireroom deg. 
 
 17. Of steam deg. 
 
 18. Of feed water entering heater deg. 
 
 19. Of feed water entering economizer deg. 
 
 20. Of feed water entering "boiler deg. 
 
 21. Of escaping gases from boiler deg. 
 
 22. Of escaping gases from economizer deg. 
 
 Fuel. 
 
 23. Size and condition 
 
 24. Weight of wood used in lighting fire Ibs. 
 
 25. Weight of coal as fired Ibs. 
 
 26. Percentage of moisture in coal per cent. 
 
 27. Total weight of dry coal consumed Ibs. 
 
 28. Total ash and refuse 
 
 29. Quality of ash and refuse 
 
 30. Total combustible consumed lb. 
 
 31. Percentage of ash and refuse in dry coal per cent. 
 
 Proximate Analysis of Coal. 
 
 Coal. Combustible. 
 
 32. Fixed carbon per cent. per cent. 
 
 33. Volatile matter ' ' ' ' 
 
 34. Moisture " 
 
 35. Ash . " 
 
 100 % 100 % 
 
 36. Sulphur, separately determined " " 
 
 Ultimate Analysis of Dry Coal. 
 
 (Art. XVII., Code.) 
 
 Coal. Combustible. 
 
 37. Carbon (C) per cent per cent. 
 
 38. Hydrogen (H) 
 
 39. Oxygen (0) 
 
 40. Nitrogen (N) 
 
 41. Sulphur (S) 
 
 42. Ash . 
 
 100 % 100 % 
 
 43. Moisture in sample of coal as received " " 
 
 57
 
 Analysis of Ash and Refuse. 
 
 44. Carbon per cent. 
 
 45. Earthy matter per cent. 
 
 Fuel per Hour. 
 
 46. Dry coal consumed per hour Ibs. 
 
 47. Combustible consumed per hour Ibs. 
 
 48. Dry coal per sq. .'. of grate surface per hour Ibs. 
 
 49. Combustible per square foot of water heating surface per hour Ibs. 
 
 Calorific Value of Fuel. 
 (Art. XVII., Code.) 
 
 50. Calorific value by oxygen calorimeter, per Ib. of dry coal B. T. U. 
 
 51. Calorific value by oxygen calorimeter, per Ib. of combustible. . .B. T. U. 
 
 52. Calorific value by analysis, per Ib. of dry coal B. T. U. 
 
 53. Calorific value by analysis, per Ib. of combustible B. T. U. 
 
 Quality of Steam. 
 
 54. Percentage of moisture in steam per cent. 
 
 55. Number of degrees of superheating deg. 
 
 56. Quality of steam (dry steam=unity) 
 
 Water. 
 
 57. Total weight of water fed to boiler Ibs. 
 
 58. Equivalent water fed to boiler from and at 212 degrees Ibs. 
 
 59. Water actually evaporated, corrected for quality of steam Ibs. 
 
 60. Factor of evaporation Ibs. 
 
 61. Equivalent water evaporated into dry steam from and at 212 de- 
 
 grees. (Item 59Xltem 60.) Ibs. 
 
 Water per Hour. 
 
 62. Water evaporated per hour, corrected for quality of steam Ibs. 
 
 63. Equivalent evaporation per hour from and at 212 degrees Ibs. 
 
 64. Equivalent evaporation per hour from and at 212 degrees per square 
 
 foot of water heating surface Ibs. 
 
 Rorsc-Poiver. 
 
 65. Horse-Power developed (34% Ibs. of water evaporated per hour 
 
 into dry steam from and at 212 degrees, equals one horse-power)!^.. P. 
 
 66. Builders ' rated horse-power H. P. 
 
 67. Percentage of builders' rated horse-power developed per cent. 
 
 Economic Results. 
 
 68. Water apparently evaporated under actual conditions per pound of 
 
 coal as fired. (Item 57^-Item 25.) Ibs. 
 
 69. Equivalent evaporation from and at 212 degrees per pound of coal 
 
 as fixed. (Item 61+Item 25) .Ibs. 
 
 70. Equivalent evaporation from and at 212 degrees per pound of dry 
 
 coal. (Item 61+Item 27.) Ibs. 
 
 71. Equivalent evaporation from and at 212 degrees per pound of 
 
 combustible. (Item 61+Item 30.) Ibs. 
 
 (If the equivalent evaporation, Items 69, 70 and 71, is not 
 corrected for the quality of steam, the fact should be stated.) 
 
 58
 
 Efficiency. 
 (Art. XXI., Code.) 
 
 72. Efficiency of boiler; heat absorbed by the boiler per Ib. of com- 
 
 bustible divided by the heat value of one Ib. of combustible, .per cent. 
 
 73. Efficiency of boiler, including the grate; heat absorbed by the 
 
 boiler, per Ib. of dry coal, divided by the heat value of one Ib. 
 
 of dry coal per cent. 
 
 Cost of Evaporation. 
 
 74. Cost of coal per ton of Ibs. delivered in boiler room $. . . . 
 
 75. Cost of fuel for evaporating 1,000 Ibs. of water under observed 
 
 conditions $ .... 
 
 76. Cost of fuel used for evaporating 1,000 Ibs. water from and at 
 
 212 degrees $. . . . 
 
 Smolce Observations. 
 
 77. Percentage of smoke as observed per cent. 
 
 78. Weight of soot per hour obtained from smoke meter ounces. 
 
 79. Volume of soot per hour obtained from smoke meter cub. in. 
 
 Methods of Firing. 
 
 80. Kind of firing (spreading, alternate or coking) 
 
 81. Average thickness of fire 
 
 82. Average intervals between firing for each furnace during time 
 
 when fires are in normal condition 
 
 83. Average interval between times of leveling or breaking up 
 
 Analysis of the Dry Gases. 
 
 84. Carbon dioxide (CO 2 ) per cent. 
 
 85. Oxygen (O) " 
 
 86. Carbon monoxide (CO) " 
 
 87. Hydrogen and hydrocarbons " 
 
 .88. Nitrogen (by difference) (N) " 
 
 100 per cent. 
 
 59
 
 
 82 
 
 0= 
 
 
 = ^ 
 
 _o = o 
 
 
 =S Ills 
 
 
 
 !! 
 
 ^l 
 
 |*g| I! 
 
 O 000 
 
 33S5.g SSggS S = g ggSSS ??5S|S 
 
 ...MiNlMr-. ,< ,*_,* ^^^o OOCOO OOOOSV 
 
 <O OOP 
 
 iii ggssi gii 
 
 ,?z 
 
 
 assis 2^=28 mi 
 
 ss^ls 2S1S SSSII lilll ill 
 
 ^^ N 0-1 N ^nOOOO CiOSoCOOl^. t^CO^Q W^^COC<I 
 
 sl^S S^SSS S=2SS o83 S3sS 
 ^.^,; ^^^^^ JJ^^^ ^^^^^ "-^gS 
 
 
 - 
 III 
 
 iiss 
 
 - r = r - p c 
 
 iiiii iliss ii||i iisls 
 
 
 is 5 i 
 
 i! ! 
 
 H 5 
 
 2& 
 
 S3 ? 
 
 ^ 
 
 &i d 
 
 <c| a 
 
 SS? S -a 
 
 60
 
 o SSS88SS88S8258S5ia 
 
 |SSS=! 
 
 IK* 9.IIU 
 pea.! 
 
 sis. 
 
 
 =1 * 
 
 ifii 
 111! 
 
 61
 
 APPROXIMATE HEATING VALUE OP GENERAL GRADES OP 
 COAL PER POUND OP COMBUSTIBLE B. T. U. 
 
 KIND OF COAL. 
 
 PER CENT. OF COMBUSTIBLE. 
 
 HEATING VALUE 
 PER POUND OF 
 COMBUSTIBLE. 
 
 FIXBD CARBON. 
 
 VOLATILE 
 MATTER. 
 
 Anthracite . 
 
 97.0 to 92. 5 
 92. 5 to 87. 5 
 87. 5 to 75. 
 75. to 60. 
 65. to 50. 
 Under 50. 
 
 3.0to 7.5 
 7. 5 to 12. 5 
 12. 5 to 25. 
 25. to 40. 
 35. to 50. 
 Over 50. 
 
 14,600 to 14,800 
 14,700 to 15,500 
 15,500 to 16,000 
 14,800 to 16,200 
 18,500 to 14,800 
 11,000 to 1.8 500 
 
 Semi-anthracite 
 Semi-bituminous 
 
 Bituminous, Eastern 
 
 Bituminous, Western 
 Lignite 
 
 
 STEAM DISCHARGES. 
 
 Absolute Ini- 
 tial Pressure 
 per Square 
 Inch. Pounds. 
 
 Velocity of 
 Outflow at 
 Constant Den- 
 sity, Feet per 
 Second.* 
 
 Actual Veloc- 
 ity of Outflow, 
 Expanded. 
 Feet per 
 Second. 
 
 Discharge per 
 Square Inch 
 of Orifice per 
 Minute. 
 Pounds. 
 
 Horse-Power 
 per Square Inch 
 of Orifice if H. 
 P. = 80 Ibs. 
 per hour. 
 
 25.37 
 
 863 
 
 1,401 
 
 22.81 
 
 45.6 
 
 30. 
 
 867 
 
 1,408 
 
 26.84 
 
 53.7 
 
 40. 
 
 874 
 
 1,419 
 
 35.18 
 
 70.4 
 
 50. 
 
 880 
 
 1,429 
 
 44.06 
 
 88.1 
 
 60. 
 
 885 
 
 1,437 
 
 52.59 
 
 105.2 
 
 70. 
 
 889 
 
 1,444 
 
 61.07 
 
 122.1 
 
 75. ' 
 
 891 
 
 1,447 
 
 65.30 
 
 130.6 
 
 90. 
 
 895 
 
 1,454 
 
 77.94 
 
 155.9 
 
 100. 
 
 898 
 
 1,459 
 
 86.34 
 
 172.7 
 
 115. 
 
 902 
 
 1,466 
 
 98.76 
 
 197.5 
 
 135. 
 
 906 
 
 1,472 
 
 115.61 
 
 231.2 
 
 155. 
 
 910 
 
 1,478 
 
 132.21 
 
 264.4 
 
 165. 
 
 912 
 
 1,481 
 
 140.46 
 
 280.9 
 
 215. 
 
 919 
 
 1,493 
 
 181.58 
 
 .363.2 
 
 COMPARISON OF OIL AND COAL. 
 
 B. T. U. Per Pound 
 of Coal. 
 
 Pounds of Coal Equal 
 to One Barrel 
 of Oil. 
 
 Barrels of Oil Equal 
 to One Short Ton 
 of Coal. 
 
 10,000 
 11,000 
 12,000 
 13,000 
 14,000 
 15,000 
 
 620 
 564 
 517 
 477 
 443 
 413 
 
 8.23 
 3.55 
 
 3.87 
 4.19 
 4.52 
 
 4.84 
 
 62
 
 3 9 
 
 9.renbs jo i 
 
 sss 
 
 3 S 
 
 ill 
 
 S 1C 
 
 3 7. Z 
 
 3$ 
 
 - 5 gig 
 
 iliiil tlilili 
 
 11 
 
 2 S 
 
 I 8 S S 
 3 cl gla 5 
 
 I Mil 
 
 i illlii 
 
 
 i lililili I Hill 
 
 l 
 
 "' 
 
 s ilili 
 
 i i. IP 
 
 IPP 
 
 inns 
 
 IPPP 
 
 SB SI 
 
 HI 
 
 5< i - 
 i- >. 
 
 III! 
 
 ?,*, 
 
 ' = 
 
 s s 
 
 I 
 
 3 S 
 
 5? -
 
 M9JOS JO ipni J9(I 
 
 
 
 
 1C CO 
 
 CO t- * <?* rH 
 
 H OF PIPE PBB 
 ABB FOOT OF 
 
 Internal 
 Surface. 
 
 iO C- t- t- *< -H 
 
 < C- t- T-( CO t- 1O 
 
 r as -o eo t Tt< 
 
 g ^^SSwifflQOI-Tj"! 
 
 iOOOOQDOOaOiOW 
 
 ^ ^ ^ (N CO ^ 10 SO t- OS ~ M OS * O 00 H 
 
 8S8SSS 
 
 CQ w cj cii co co ec 
 
 
 ctual 
 ternal 
 meter. 
 
 r,4
 
 ~ ~ ~ ./'. . ~ ^ Z: Z^ Z-/.ZI . Z- . 
 
 t- <M *-f eo -^< c- so t- oo o 10 t- -^ -^ ic t- TJ< 10 o * o m 10 o c -i o to o 
 
 OOC^ CCOOOrHiOt^TCOOCOQOOT-trrOOOtr-^L^iOC^^^OO^CDt^iC 
 
 -i< -<f c>< oo o -^ <M CM -^ o TO co o 03 oo o so eo ic TJ< o c- c c- c- oo o; 
 
 C5 O O 
 
 t-coi-iooot-oaoooooooo-<}<ooo>o*coooc 
 
 io eoi-ieoecot-oO'^<o--co!CoO'*ioooaTHOoeoo-iioeoco 
 '<o t~ t- o t- o to co t- t- oo o oo ?o co t- so ;o t- so c- c- t- t- oo c- c- t- 
 
 ^cf wco^cleo^^co co ^ ^ cl co cl co c ^i co 3 ^ % eo S 
 
 o ca oo o o ** o o* t- * ex o to oo o o> o c* c- o -^ o o o cs 10 >c 
 
 os x oo co eo * o i-( i T-I o w o o I-KH ^- 
 
 c- eo CM ^- as co o as t- c- 
 
 :h 
 
 700 < 00 00 00 <N -^ ff 00 <N (? (N 7? O 00 <M * "* 00 <M 00 00 
 
 
 2= - - : : : 
 
 t 1 '2" 

 
 TABLE OF PROPERTIES OF SATURATED STEAM. 
 
 Total 
 Pres- 
 sure 
 perSq 
 Inch. 
 
 Tempera- 
 ture in 
 Fahrenh't 
 Degrees. 
 
 Total Heat 
 in Heat 
 Units from 
 Water at 
 32 Fahr. 
 
 Latent 
 Heat 
 in 
 Heat 
 Units 
 
 Density 
 Weight of 
 Cubic Foot 
 
 Volume ol 
 One 
 Pound of 
 Steam. 
 
 Relative 
 Volume, 
 or Cub. Ft. 
 from One 
 of Water. 
 
 Factor of 
 Equiva- 
 lent Evap- 
 oration, at 
 812. 
 
 1 
 
 102 
 
 1113.05 
 
 1042.964 
 
 .0030 
 
 330.36 
 
 0620 
 
 0.965 
 
 2 
 
 126.266 
 
 1120.45 
 
 1026.010 
 
 .0058 
 
 172.08 
 
 107*0 
 
 0.972 
 
 3 
 
 141.622 
 
 1125.131 
 
 1015.254 
 
 .0085 
 
 117.52 
 
 7326 
 
 0.977 
 
 4 
 
 158.070 
 
 1128.625 
 
 1007.229 
 
 .0112 
 
 89.62 
 
 5600 
 
 0.981 
 
 5 
 
 162.830 
 
 1131.449 
 
 1000.727 
 
 .0137 
 
 72.66 
 
 4535 
 
 0.984 
 
 6 
 
 170.123 
 
 1133.826 
 
 995.219 
 
 .0163 
 
 61.21 
 
 3814 
 
 0.986 
 
 7 
 
 176.910 
 
 1135.896 
 
 990.471 
 
 .0189 
 
 52.94 
 
 3300 
 
 0.988 
 
 8 
 
 182.910 
 
 1137.726 
 
 986.245 
 
 .0214 
 
 46.69 
 
 2910 
 
 0.990 
 
 9 
 
 188.316 
 
 1139.375 
 
 982.434 
 
 .0239 
 
 41.79 
 
 2607 
 
 0.992 
 
 10 
 
 193.240 
 
 1140.877 
 
 978.958 
 
 .0264 
 
 37.84 
 
 2360 
 
 0.994 
 
 15 
 
 213.025 
 
 1146.912 
 
 964.973 
 
 .0387 
 
 25.85 
 
 1612 
 
 1.000 
 
 20 
 
 227.917 
 
 1151.454 
 
 954.415 
 
 .0511 
 
 19.72 
 
 1220.3 
 
 1.005 
 
 25 
 
 240.000 
 
 1155.139 
 
 945.825 
 
 .0634 
 
 15.99 
 
 984.8 
 
 1.008 
 
 30 
 
 250.245 
 
 1158.263 
 
 938.925 
 
 .0755 
 
 13.46 
 
 826.8 
 
 1.012 
 
 35 
 
 259.176 
 
 1160.987 
 
 932.152 
 
 .0875 
 
 11.85 
 
 713.4 
 
 1.015 
 
 40 
 
 267.120 
 
 1163.410 
 
 926.472 
 
 .0994 
 
 10.27 
 
 628.2 
 
 1.017 
 
 45 
 
 274.296 
 
 1165.600 
 
 921.334 
 
 .1111 
 
 9.18 
 
 561.8 
 
 1.019 
 
 50 
 
 280.854 
 
 1167.600 
 
 916.631 
 
 .1227 
 
 8.31 
 
 508.5 
 
 1.021 
 
 55 
 
 286.897 
 
 1169.442 
 
 912.290 
 
 .1343 
 
 7.61 
 
 464.7 
 
 1.023 
 
 60 
 
 292.520 
 
 1171.158 
 
 908.247 
 
 .1457 
 
 7.01 
 
 428.5 
 
 1.025 
 
 65 
 
 297.777 
 
 1172.762 
 
 904.462 
 
 .1569 
 
 6.49 
 
 397.7 
 
 1.027 
 
 70 
 
 302.718 
 
 1174.269 
 
 900.899 
 
 .1681 
 
 6.07 
 
 871.2 
 
 1.028 
 
 75 
 
 307.388 
 
 1175.692 
 
 897.526 
 
 .1792 
 
 5.68 
 
 348.3 
 
 1.030 
 
 80 
 
 311.812 
 
 1177.042 
 
 894.830 
 
 .1901 
 
 5.35 
 
 328.3 
 
 1.031 
 
 85 
 
 316.021 
 
 1178.326 
 
 891.286 
 
 .2010 
 
 5.05 
 
 810.5 
 
 1.033 
 
 90 
 
 320.039 
 
 1179.551 
 
 8S8.375 
 
 .2118 
 
 4.79 
 
 294.7 
 
 1.034 
 
 95 
 
 323.884 
 
 1180.724 
 
 885.588 
 
 .2234 
 
 4.55 
 
 280.6 
 
 1.035 
 
 100 
 
 327.571 
 
 1181.849 
 
 883.914 
 
 .2330 
 
 4.33 
 
 267.9 
 
 1.036 
 
 105 
 
 331.113 
 
 1182.929 880.342 
 
 .2434 
 
 4.14 
 
 265.5 
 
 1.037 
 
 110 
 
 334.523 
 
 1183.970 877.865 
 
 .2537 
 
 3.97 
 
 246.0 
 
 1.038 
 
 115 
 
 337.814 
 
 1184.974 875.472 
 
 .2640 
 
 3.80 
 
 236.3 
 
 1.039 
 
 120 
 
 340.995 
 
 1185.944 
 
 873.155 
 
 .2742 
 
 3.65 
 
 227.6 
 
 1.040 
 
 125 
 
 344.074 
 
 1186.883 
 
 870.911 
 
 .2842 
 
 3.51 
 
 219.7 
 
 1.041 
 
 130 
 
 347.059 
 
 1187.794 
 
 868.735 
 
 .2942 
 
 3.38 
 
 212.3 
 
 1.042 
 
 140 
 
 352.757 
 
 1189.535 
 
 864.566 
 
 .3138 
 
 3.16 
 
 199.0 
 
 1.044 
 
 150 
 
 358.161 
 
 1191.180 
 
 860.621 
 
 .3340 
 
 2.96 
 
 187.5 
 
 1.046 
 
 160 
 
 868.277 
 
 1192.741 
 
 856.874 
 
 .3520 
 
 2.79 
 
 177.3 
 
 1.047 
 
 170 
 
 368.158 
 
 1194.228 
 
 853.294 
 
 .3709 
 
 2.fi3 
 
 168.4 
 
 1.049 
 
 180 
 
 872.822 
 
 1195.650 
 
 849.869 
 
 .3889 
 
 2.49 
 
 160.4 
 
 1.051 
 
 190 
 
 377.291 
 
 1197.013 
 
 846.584 
 
 .4072 
 
 2.37 
 
 153.4 
 
 1.052 
 
 200 
 
 381.573 
 
 1198.310 
 
 843.432 
 
 .4249 
 
 2.26 
 
 147.1 
 
 1.053 
 
 250 
 
 401.072 
 
 1203.735 
 
 831.222 
 
 .5464 
 
 1.83 
 
 114 
 
 1.059 
 
 300 
 
 418.225 
 
 1208.737 
 
 819.610 
 
 .6486 
 
 1.54 
 
 96 
 
 1.064 
 
 350 
 
 431.956 
 
 1212.580 
 
 810.690 
 
 .7498 
 
 1.33 
 
 83 
 
 1.068 
 
 400 
 
 444.919 
 
 1217.094 
 
 800.198 
 
 .8502 
 
 1.18 
 
 73 
 
 1.073 
 
 
 
 
 
 
 I 

 
 PROPERTIES OF SATURATED STEAM. 
 
 Pressure 
 above 
 Vacuum. 
 Lbs. per 
 Sq. Inch. 
 
 Temperature 
 Degrees 
 Fahrenheit. 
 
 Heat of Liquid 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Latent Heat 
 above 32 
 Fahrenheit 
 B. T. U. 
 
 Total Heat 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Density, or 
 Weight per 
 Cubic Foot. 
 Pounds. 
 
 2 
 
 126.3 
 
 94.4 
 
 1026.1 
 
 1120.5 
 
 0.00576 
 
 4 
 
 153.1 
 
 121.4 
 
 1007.2 
 
 1128.6 
 
 0.01107 
 
 6 
 
 170.1 
 
 138.6 
 
 995.2 
 
 1133.8 
 
 0.01622 
 
 8 
 
 182.9 
 
 151.5 
 
 986.2 
 
 1137.7 
 
 0.02125 
 
 10 
 
 193.3 
 
 161.9 
 
 979.0 
 
 1140.9 
 
 0.02621 
 
 12 
 
 202.0 
 
 170.7 
 
 972.9 
 
 1143.6 
 
 0.03111 
 
 14 
 
 209.6 
 
 178.3 
 
 967.5 
 
 1145.8 
 
 0.03600 
 
 14.7 
 
 212.0 
 
 180.8 
 
 965.8 
 
 1146.6 
 
 0.03760 
 
 16 
 
 216.3 
 
 185.1 
 
 962.8 
 
 1147.9 
 
 0.04067 
 
 18 
 
 222.4 
 
 191.3 
 
 958.5 
 
 1149.8 
 
 0.04547 
 
 20 
 
 228.0 
 
 196.9 
 
 954.6 
 
 1151.5 
 
 0.05023 
 
 22 
 
 233.1 
 
 202.0 
 
 951.0 
 
 1153.0 
 
 0.05495 
 
 24 
 
 237.8 
 
 206.8 
 
 947.6 
 
 1154.4 
 
 0.05966 
 
 26 
 
 242.2 
 
 211.2 
 
 944.6 
 
 1155.8 
 
 0.06432 
 
 28 
 
 246.4 
 
 215.4 
 
 941.7 
 
 1157.1 
 
 ,0.06899 
 
 30 
 
 250.3 
 
 219.4 
 
 938.9 
 
 1158.3 
 
 0.07360 
 
 32 
 
 254.0 
 
 223.1 
 
 936.3 
 
 1159.4 
 
 0.07821 
 
 34 
 
 857.5 
 
 226.7 
 
 933.7 
 
 1160.4 
 
 0.08280 
 
 36 
 
 260.9 
 
 230.0 
 
 931.5 
 
 1161.5 
 
 0.08736 
 
 38 
 
 264.1 
 
 233.3 
 
 929.2 
 
 1162.5 
 
 0.09191 
 
 40 
 
 267.1 
 
 236.4 
 
 927.0 
 
 1163.4 
 
 0.09644 
 
 42 
 
 270.1 
 
 239.3 
 
 925.0 
 
 1164.3 
 
 0.1009 
 
 44 
 
 272.9 
 
 242.2 
 
 923.0 
 
 1165.2 
 
 0.1054 
 
 46 
 
 275.7 
 
 245.0 
 
 921.0 
 
 1166.0 
 
 0.1099 
 
 48 
 
 278.3 
 
 247.6 
 
 919.2 
 
 1166.8 
 
 0.1144 
 
 60 
 
 280.9 
 
 250.2 
 
 917.4 
 
 1167.6 
 
 0.1188 
 
 52 
 
 283.3 
 
 252.7 
 
 915.7 
 
 1168.4 
 
 0.1233 
 
 54 
 
 285.7 
 
 255.1 
 
 914.0 
 
 1169.1 
 
 0.1277 
 
 56 
 
 288.1 
 
 257.5 
 
 912.3 
 
 1169.8 
 
 0.1321 
 
 58 
 
 290.3 
 
 259.7 
 
 910.8 
 
 1170.5 
 
 0.1366 
 
 60 
 
 292.5 
 
 261.9 
 
 909.3 
 
 1171.2 
 
 0.1409 
 
 62 
 
 294.7 
 
 264.1 
 
 907.7 
 
 1171.8 
 
 0.1453 
 
 64 
 
 296.7 
 
 266.2 
 
 906.2 
 
 1172.4 
 
 0.1497 
 
 66 
 
 298.8 
 
 268.3 
 
 904.7 
 
 1173.0 
 
 0.1541 
 
 68 
 
 300.8 
 
 270.3 
 
 903.3 
 
 1173.6 
 
 0.1584 
 
 70 
 
 302.7 
 
 272.2 
 
 902.1 
 
 1174.8 
 
 0.1628 
 
 72 
 
 304.6 
 
 274.1 
 
 900.8 
 
 1174.9 
 
 0.1671 
 
 74 
 
 306.5 
 
 276.0 
 
 899.4 
 
 1175.4 
 
 0.1714 
 
 76 
 
 308.3 
 
 277.8 
 
 898.2 
 
 1176.0 
 
 0.1757 
 
 78 
 
 310.1 
 
 279.6 
 
 896.9 
 
 1176.5 
 
 0.1801 
 
 80 
 
 311.8 
 
 281.4 
 
 895.6 
 
 1177.0 
 
 0.1843 
 
 82 
 
 313.5 
 
 283.2 
 
 894.4 
 
 1177.6 
 
 0.1886 
 
 84 
 
 315.2 
 
 285.0 
 
 893.1 
 
 1178.1 
 
 0.1930 
 
 86 
 
 316.8 
 
 286.7 
 
 891.9 
 
 1178.6 
 
 0.1978 
 
 88 
 
 318.5 
 
 288.4 
 
 890.7 
 
 1179.1 
 
 0.2016 
 
 90 
 
 320.0 
 
 290.0 
 
 889.6 
 
 1179.6 
 
 O.S058 
 
 92 
 
 321.6 
 
 291.6 
 
 888.4 
 
 1180.0 
 
 0.2101 
 
 94 
 
 323.1 
 
 293.2 
 
 887.3 
 
 1180.5 
 
 0.2144 
 
 96 
 
 324.6 
 
 294.8 
 
 886.2 
 
 1181.0 
 
 0.2186 
 
 98 
 
 326.1 
 
 296.4 
 
 885.0 
 
 1181.4 
 
 0.2229 
 
 100 
 
 827.6 
 
 297.9 
 
 884.0 
 
 1181.9 
 
 0.2271 
 
 102 
 
 329.0 
 
 299.4 
 
 882.9 
 
 1182.8 
 
 0.2314 
 
 104 
 
 330.4 
 
 300.9 
 
 881.8 
 
 1182.7 
 
 0.2356 
 
 67
 
 PROPERTIES OP SATURATED STEAM (Continued). 
 
 Pressure 
 above 
 Vacuum 
 Lbs. per 
 Sq. Inch. 
 
 Temperature, 
 Degrees 
 Fahrenheit. 
 
 Heat of Liquid 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Latent Heat 
 above 32 
 Fahrenheit 
 B. T. U. 
 
 Total Heat 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Density, or 
 Weight per 
 Cubic Foot. 
 Pounds. 
 
 106 
 
 831.8 
 
 302.3 
 
 880.8 
 
 1183.1 
 
 0.2399 
 
 108 
 
 333.2 
 
 303.8 
 
 879.8 
 
 1183.6 
 
 0.2441 
 
 110 
 
 334.6 
 
 805.2 
 
 878.8 
 
 1184.0 
 
 0.2484 
 
 112 
 
 335.9 
 
 306.6 
 
 877.8 
 
 1184.4 
 
 0.2526 
 
 114 
 
 337.2 
 
 308.0 
 
 876.8 
 
 1184.8 
 
 0.2568 
 
 116 
 
 338.5 
 
 309.4 
 
 875.8 
 
 1185.2 
 
 0.2610 
 
 118 
 
 339.8 
 
 810.7 
 
 874.9 
 
 1185.6 
 
 0.2653 
 
 120 
 
 841.1 
 
 312.0 
 
 874.0 
 
 1186.0 
 
 0.^695 
 
 122 
 
 342.3 
 
 813.3 
 
 873.0 
 
 1186.3 
 
 0.2786 
 
 124 
 
 343.5 
 
 314.6 
 
 872.1 
 
 1186.7 
 
 0.2779 
 
 126 
 
 344.7 
 
 815.9 
 
 871.2 
 
 1187.1 
 
 0.2820 
 
 128 
 
 345.9 
 
 317.1 
 
 870.3 
 
 1187.4 
 
 0.2862 
 
 130 
 
 347.1 
 
 818.4 
 
 869.4 
 
 1187.8 
 
 0.2904 
 
 132 
 
 348.3 
 
 319.6 
 
 868.6 
 
 1188.2 
 
 0.2946 
 
 134 
 
 349.5 
 
 320.8 
 
 867.7 
 
 1188.5 
 
 0.2988 
 
 136 
 
 350.6 
 
 322.0 
 
 866.9 
 
 1188.9 
 
 0.3030 
 
 138 
 
 351.7 
 
 223.2 
 
 866.0 
 
 1189.2 
 
 0.8072 
 
 140 
 
 352.9 
 
 324.4 
 
 865.1 
 
 1189.5 
 
 0.3113 
 
 142 
 
 354.0 
 
 325.6 
 
 864.3 
 
 1189.9 
 
 0.3155 
 
 144 
 
 355.1 
 
 326.7 
 
 863.5 
 
 1190.2 
 
 0.3197 
 
 146 
 
 356.1 
 
 327.8 
 
 862.8 
 
 1190.6 
 
 0.3239 
 
 148 
 
 357.2 
 
 328.9 
 
 862.0 
 
 1190.9 
 
 0.3280 
 
 150 
 
 358.3 
 
 330.0 
 
 861.2 
 
 1191.2 
 
 0.3321 
 
 152 
 
 359.3 
 
 331.1 
 
 860.4 
 
 1191.5 
 
 0.3363 
 
 154 
 
 360.3 
 
 332.2 
 
 859.6 
 
 1191.8 
 
 0.3405 
 
 156 
 
 361.4 
 
 333.3 
 
 858.9 
 
 1192.2 
 
 0.3447 
 
 158 
 
 362.4 
 
 334.3 
 
 858.2 
 
 1102.5 
 
 0.3488 
 
 160 
 
 363.4 
 
 835.4 
 
 857.4 
 
 1192.8 
 
 0.3530 
 
 162 
 
 364.4 
 
 336.4 
 
 856.7 
 
 1193.1 
 
 0.3572 
 
 164 
 
 365.4 
 
 337.5 
 
 855.9 
 
 1193.4 
 
 0.8614 
 
 166 
 
 366.4 
 
 338.5 
 
 855.2 
 
 1143.7 
 
 0.3655 
 
 168 
 
 367.3 
 
 339.5 
 
 854.5 
 
 1194.0 
 
 0.3695 
 
 170 
 
 368.3 
 
 340.5 
 
 853.8 
 
 1194.3 
 
 0.3737 
 
 172 
 
 369.2 
 
 841.5 
 
 853.1 
 
 1194.6 
 
 0.3778 
 
 174 
 
 370.2 
 
 842.5 
 
 852.3 
 
 1194.8 
 
 0.3820 
 
 176 
 
 371.1 
 
 343.5 
 
 851.6 
 
 1195.1 
 
 0.8862 
 
 178 
 
 372.1 
 
 344.4 
 
 851.0 
 
 1195.4 
 
 0.3904 
 
 180 
 
 373.0 
 
 345.4 
 
 850.3 
 
 1195.7 
 
 0.3945 
 
 183 
 
 373.9 
 
 346.4 
 
 849.6 
 
 1196.0 
 
 0.3987 
 
 184 
 
 374.8 
 
 347.3 
 
 848.9 
 
 1196.2 
 
 0.4029 
 
 186 
 
 875.7 
 
 348.2 
 
 848.3 
 
 1196.5 
 
 0.4070 
 
 188 
 
 376.6 
 
 349.2 
 
 847.6 
 
 1196.8 
 
 0.4111 
 
 190 
 
 377.4 
 
 350.1 
 
 847.0 
 
 1197.1 
 
 0.4158 
 
 192 
 
 378.3 
 
 851.0 
 
 846.3 
 
 1197.3 
 
 0.4194 
 
 194 
 
 379.9 
 
 351.9 
 
 845.7 
 
 1197.6 
 
 0.4236 
 
 196 
 
 380.0 
 
 352.8 
 
 845.0 
 
 1197.8 
 
 0.4278 
 
 198 
 
 380.9 
 
 353.7 
 
 844.4 
 
 1198.1 
 
 0.4318 
 
 200 
 
 381.7 
 
 854.6 
 
 843.8 
 
 1198.4 
 
 0.4359 
 
 202 
 
 382.6 
 
 855.4 
 
 843.2 
 
 1198.6 
 
 0.4399 
 
 204 
 
 383.4 
 
 356.3 
 
 842.6 
 
 1198.9 
 
 0.4441 
 
 206 
 
 884.2 
 
 857.2 
 
 841.9 
 
 1199.1 
 
 0.4482 
 
 208 
 
 385.1 
 
 358.0 
 
 841.4 
 
 1199.4 
 
 0.4524 
 
 210 
 
 385.9 
 
 858.9 840.7 
 
 1199.6 
 
 0.4565
 
 PROPERTIES OP SATURATED STEAM (Continued). 
 
 Pressure 
 above 
 Vacuum 
 Lbs. per 
 Sq. Inch. 
 
 Temperature, 
 Degrees 
 Fahrenheit. 
 
 Heat of Liquid 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Latent Heat 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Total Heat 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Density, or 
 Weight per 
 Cubic Foot. 
 Pounds. 
 
 212 
 
 386.7 
 
 359.7 
 
 840.2 
 
 1199.9 
 
 0.4607 
 
 214 
 
 387.5 
 
 360.6 
 
 839.5 
 
 1200.1 
 
 0.4648 
 
 216 
 
 888.3 
 
 361.4 
 
 839.0 
 
 1200.4 
 
 0.4690 
 
 218 
 
 389.1 
 
 362.2 
 
 838.4 
 
 1200.6 
 
 0.4781 
 
 220 
 
 389.8 
 
 363.0 
 
 837.8 
 
 1200.8 
 
 0.4772 
 
 222 
 
 390.6 
 
 863.9 
 
 837.2 
 
 1201.1 
 
 0.4813 
 
 224 
 
 391.4 
 
 864.7 
 
 836.6 
 
 1201.3 
 
 0.4855 
 
 226 
 
 392.2 
 
 365.5 
 
 836.1 
 
 1201.6 
 
 0.4896 
 
 228 
 
 392.9 
 
 366.3 
 
 835.5 
 
 1201.8 
 
 0.4989 
 
 230 
 
 393.7 
 
 367.1 
 
 834.9 
 
 1202.0 
 
 0.4979 
 
 232 
 
 394.5 
 
 367.9 
 
 834.3 
 
 1202.2 
 
 0.5021 
 
 234 
 
 395.2 
 
 368.6 
 
 833.9 
 
 1202.5 
 
 0.5062 
 
 236 
 
 395.9 
 
 369.4 
 
 833.3 
 
 1202.7 
 
 0.5103 
 
 238 
 
 396.7 
 
 870.2 
 
 832.7 
 
 1202.9 
 
 0.5144 
 
 240 
 
 397.4 
 
 371.0 
 
 832.2 
 
 1203.2 
 
 0.5186 
 
 242 
 
 398.1 
 
 371.7 
 
 831.7 
 
 1203.4 
 
 0.5226 
 
 244 
 
 898.9 
 
 872.5 
 
 831.1 
 
 1203.6 
 
 0.5268 
 
 246 
 
 899.6 
 
 873.2 
 
 830.6 
 
 1203.8 
 
 0.5311 
 
 248 
 
 400.3 
 
 374.0 
 
 830.0 
 
 1204.0 
 
 0.5353 
 
 250 
 
 401.0 
 
 374.7 
 
 829.5 
 
 1204.2 
 
 0.5393 
 
 252 
 
 401.7 
 
 375.4 
 
 829.1 
 
 1204.5 
 
 0.5483 
 
 254 
 
 402.4 
 
 876.2 
 
 828.5 
 
 1204.7 
 
 0.5475 
 
 256 
 
 403.1 
 
 876.9 
 
 828.0 
 
 1204.9 
 
 0.5517 
 
 258 
 
 403.8 
 
 377.6 
 
 827.5 
 
 1205.1 
 
 0.5559 
 
 260 
 
 404.5 
 
 378.4 
 
 826.9 
 
 1205.3 
 
 0.5601 
 
 262 
 
 405.2 
 
 379.1 
 
 826.4 
 
 1205.5 
 
 0.5642 
 
 264 
 
 405.8 
 
 379.8 
 
 825.9 
 
 1205.7 
 
 0.5684 
 
 266 
 
 406.5 
 
 380.5 
 
 825.4 
 
 1205.9 
 
 0.5726 
 
 268 
 
 407.2 
 
 381.2 
 
 824.9 
 
 1206.1 
 
 0.5767 
 
 270 
 
 407.9 
 
 381.9 
 
 824.4 
 
 1206.3 
 
 0.5809 
 
 272 
 
 408.6 
 
 882.6 
 
 823.9 
 
 1206.5 
 
 0.5850 
 
 274 
 
 409.2 
 
 383.3 
 
 823.4 
 
 1206.7 
 
 0.5892 
 
 276 
 
 409.8 
 
 384.0 
 
 822.9 
 
 1206.9 
 
 0.5934 
 
 278 
 
 410.5 
 
 384.6 
 
 822.5 
 
 1207.1 
 
 0.5976 
 
 280 
 
 411.1 
 
 385.3 
 
 822.0 
 
 1207.3 
 
 0.602 
 
 282 
 
 411.8 
 
 886.0 
 
 821.5 
 
 1207.6 
 
 0.606 
 
 284 
 
 412.4 
 
 b86.6 
 
 821.1 
 
 1207.7 
 
 0.610 
 
 286 
 
 413.0 
 
 887.3 
 
 820.6 
 
 1207.9 
 
 0.614 
 
 288 
 
 413.7 
 
 388.0 
 
 820.1 
 
 1208.1 
 
 0.618 
 
 290 
 
 414.3 
 
 888.6 
 
 819.7 
 
 1208.3 
 
 0.622 
 
 292 
 
 414.9 
 
 389.3 
 
 819.2 
 
 1208.6 
 
 0.627 
 
 294 
 
 415.6 
 
 390.0 
 
 818.7 
 
 1208.7 
 
 0.631 
 
 296 
 
 416.2 
 
 390.6 
 
 818.3 
 
 1208.9 
 
 0.635 
 
 298 
 
 416.8 
 
 391.3 
 
 817.8 
 
 1209.1 
 
 0.639 
 
 300 
 
 417.4 
 
 891.9 
 
 817.4 
 
 1209.3 
 
 0.644 
 
 302 
 
 418.0 
 
 392.5 
 
 816.9 
 
 1209.4 
 
 0.648 
 
 304 
 
 418.6 
 
 393.2 
 
 816.4 
 
 1209.6 
 
 0.65J 
 
 306 
 
 419.2 
 
 393.8 
 
 816.0 
 
 1209.8 
 
 0.656 
 
 308 
 
 419.8 
 
 394.4 
 
 815.6 
 
 1210.0 
 
 0.660 
 
 310 
 
 420.4 
 
 395.0 
 
 815.2 
 
 1210.2 
 
 0.664 
 
 312 
 
 421.0 
 
 895.7 
 
 814.7 
 
 1210.4 
 
 0.668 
 
 314 
 
 421.6 
 
 396.3 
 
 814.2 
 
 1210.5 
 
 0.673 
 
 316 
 
 422.2 
 
 396.9 
 
 813.8 
 
 1210.7 
 
 0.677
 
 PROPERTIES OP SATURATED STEAM (Continued). 
 
 Pressure 
 above 
 Vacuum 
 Lbs. per 
 Sq. Inch. 
 
 Temperature, 
 Degrees 
 Fahrenheit. 
 
 Heat of Liquid 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Latent Heat 
 above 32 
 Fahrenheit, 
 B. T. U. 
 
 Total Heat 
 above 32 
 Fahrenheit. 
 B. T. U. 
 
 Density, or 
 Weight per 
 Cubic Foot. 
 Pounds. 
 
 318 
 
 422.8 
 
 397.5 
 
 813.4 
 
 1210.9 
 
 0.681 
 
 320 
 
 423.4 
 
 398.1 
 
 813.0 
 
 1211.1 
 
 0.685 
 
 322 
 
 424.0 
 
 398.7 
 
 812.5 
 
 1211.2 
 
 0.690 
 
 324 
 
 424.5 
 
 399.3 
 
 812.1 
 
 1211.4 
 
 0.694 
 
 326 
 
 425.1 
 
 899.9 
 
 811.7 
 
 1211.6 
 
 0.698 
 
 328 
 
 425.7 
 
 400.5 
 
 811.3 
 
 1211.8 
 
 0.702 
 
 330 
 
 4-26.2 
 
 401.1 
 
 810.8 
 
 1211.9 
 
 0.707 
 
 335 
 
 427.6 
 
 402.6 
 
 809.8 
 
 1212.4 
 
 0.717 
 
 350 
 
 431.9 
 
 406.9 
 
 806.8 
 
 1213.7 
 
 0.748 
 
 375 
 
 438.4 
 
 414.2 
 
 801.5 
 
 1215.7 
 
 0.800 
 
 400 
 
 445.2 
 
 421.4 
 
 796.3 
 
 1217.7 
 
 0.853 
 
 450 
 
 456. ^ 
 
 433.4 
 
 787.7 
 
 1221.1 
 
 0.959 
 
 500 
 
 466.6 
 
 444.3 
 
 779.9 
 
 1224.2 
 
 1.065 
 
 AIR REQUIRED FOR VENTILATION. 
 
 Standard Parts of Carbonic Acid 
 
 Cubic Feet of Air Required, per Person. 
 
 
 Per Minute. 
 
 Per Hour, 
 
 5 
 
 133 
 
 8,000 
 
 6 
 
 67 
 
 4,000 
 
 7 
 
 44 
 
 2,667 
 
 8 
 
 33 
 
 2,020 
 
 9 
 
 27 
 
 1,600 
 
 10 
 
 22 
 
 1,333 
 
 11 
 
 19 
 
 ],151 
 
 12 
 
 17 
 
 1,000 
 
 VENTILATION FOR DIFFERENT TYPES OF BUILDINGS. 
 
 Air Supply per Occupant for 
 
 Cubic Feet per 
 Minute. 
 
 Cubic Feet per 
 Hour. 
 
 Hospitals .... 
 
 50 to 80 
 
 3,000 to 4,000 
 
 High Schools 
 
 50 
 
 3,000 
 
 Grammar Schools 
 Theatres and Assembly Halls 
 Churches 
 
 40 
 25 
 20 
 
 2,400 
 1,500 
 1 200 
 
 
 
 
 HORSE POWER FOR VENTILATION. 
 
 Our B. T. U. will raise the temperature of one cubic foot of air 55 
 degrees. In other words, the B. T. U. required to raise any given volume 
 of air any number of degrees is equal to : 
 
 Volume of Air in Cubic Feet x Degrees T?aised 
 55 
 
 7U
 
 VELOCITIES OBTAINED THROUGH FLUES OP HEIGHTS FOR 
 
 VARYING DIFFERENCES IN TEMPERATURE BETWEEN 
 
 OUTSIDE AIR AND THAT IN FLUE. 
 
 
 Excess of Temperature of Air in Flue Above that of External Air. 
 
 Height of Flue 
 in Feet. 
 
 5 
 
 10 
 
 15 
 
 20 
 
 30 
 
 50 
 
 5 
 
 55 
 
 70 
 
 94 109 
 
 134 
 
 167 
 
 10 
 
 77 
 
 108 
 
 133 
 
 153 
 
 188 
 
 242 
 
 15 
 
 94 
 
 133 
 
 162 
 
 18 
 
 230 
 
 297 
 
 20 
 
 108 
 
 153 
 
 188 
 
 217 
 
 225 
 
 342 
 
 25 
 
 121 
 
 171 
 
 210 
 
 242 
 
 297 
 
 383 
 
 30 
 
 133 
 
 188 
 
 230 
 
 265 
 
 325 
 
 419 
 
 35 
 
 1-13 
 
 203 
 
 248 
 
 286 
 
 351 
 
 458 
 
 40 
 
 153 
 
 217 
 
 265 
 
 306 
 
 375 
 
 484 
 
 45 
 
 162 
 
 230 
 
 282 
 
 325 
 
 398 
 
 514 
 
 50 
 
 171 
 
 242 
 
 297 
 
 342 
 
 419 
 
 541 
 
 GO 
 
 188 
 
 264 
 
 325 
 
 378 
 
 461 
 
 594 
 
 NUMBER OF SQUARE FEET OF DIRECT STEAM RADIATION 
 
 DIFFERENT SIZES OF PIPES WILL SUPPLY FOR 
 
 VARYING LENGTHS OF RIM. 
 
 Square Feet of Radiating Surface. 
 
 Size of Pipe. 
 
 100 ft. 
 Rim. 
 
 200ft. 
 Riui. 
 
 300ft. 
 Rim. 
 
 400ft. 
 Rim. 
 
 500ft. 
 Rim. 
 
 600ft. 
 Rim. 
 
 700ft. 
 Rim. 
 
 800ft. 
 Rim. 
 
 900ft. 
 R m. 
 
 1 
 
 30 
 
 
 
 
 
 
 
 
 
 \\A 
 
 60 
 
 50 
 
 
 
 
 
 
 
 
 Ii2 
 
 100 
 
 75 
 
 50 
 
 
 
 
 
 
 
 2 
 
 200 
 
 150 
 
 125 
 
 100 
 
 7.1 
 
 
 
 
 
 2V 
 
 850 
 
 250 
 
 200 
 
 175 
 
 150 
 
 125 
 
 
 
 
 8 
 
 3^ 
 
 5 
 6 
 
 7 
 
 550 
 850 
 1200 
 
 400 
 600 
 850 
 1400 
 
 300 
 450 
 700 
 1150 
 
 275 
 400 
 600 
 1000 
 1600 
 
 250 
 350 
 525 
 700 
 1400 
 
 225 
 325 
 475 
 850 
 1300 
 
 200 
 300 
 450 
 775 
 1-200 
 1700 
 
 175 
 250 
 400 
 725 
 1150 
 1606 
 
 150 
 22--) 
 350 
 050 
 1000 
 1500 
 
 SIZES FOR VERTICAL RISERS AND DROPS FOR 
 STEAM HEATING. 
 
 Square Feet of Radiating Surface. 
 
 
 1st Story. 
 
 2.1 Story. 
 
 3d Story. 
 
 4th Story. 
 
 5th Story. 
 
 6th Story. 
 
 1 
 
 Ifcl 
 
 
 
 2M 
 
 30 
 60 
 100 
 200 
 350 
 
 55 
 90 
 140 
 275 
 475 
 
 65 
 110 
 165 
 375 
 
 75 
 125 
 185 
 4-J5 
 
 85 
 140 
 210 
 500 
 
 95 
 160 
 240 
 
 3 
 
 550 
 
 
 
 
 
 
 3^ 
 
 850 
 
 
 
 
 
 
 
 
 
 
 

 
 TONNAGE BASIS IN REFRIGERATING WORK. 
 
 One ton of refrigeration is the amount of heat absorbed by the melting 
 of 2,000 pounds of ice at 32 F. into 2,000 pounds of water at 32 F., or the 
 amount of heat that must be extracted from 2,000 pounds of water at 32 F. 
 to reduce it to 2,000 pounds of ice at 32 F., which is 2,000X142=284.000 
 B. T. U. The reason the multiplier 142 is used, is that the latent heat of 
 one pound of ice is 142 B. T. U. 
 
 COMPRESSION PLANT IN REFRIGERATION 
 
 is one where the gas is drawn from the expansion side of the plant by the 
 suction of the compressor, compressed to a liquifying pressure and dis- 
 charged into the condenser. 
 
 WITH THE ABSORPTION PLANT 
 
 the gas from the expansion side is absorbed into water and a rich liquor so 
 made is heated in a still, and the ammonia gas driven out of the water and 
 forced into the condenser. 
 
 POWER REQUIRED FOR REFRIGERATING PLANT 
 
 is, broadly speaking, about 1.5 horse power per ton of refrigeration, for 
 plants above 10 tons; for less tonnage about 2 horse power per ton is allowed. 
 
 TESTING AND CHARGING OF REFRIGERATING MACHINERY 
 
 as given by a prominent firm of builders, is as follows: 
 
 In testing a refrigerating plant, it is advisable to pump up an air pres- 
 sure of 300 pounds per square inch. A soap suds solution should then be 
 applied to all joints to detect any leakage. If leaks are discovered, the air 
 must be allowed to escape and such new gaskets inserted or such new joints 
 made, as circumstances demand. 
 
 After the entire plant has been carefully examined and found absolutely 
 tight, a pressure of 300 pounds should be maintained and the compressor 
 permitted to remain idle for a period of about twelve hours. Unless there 
 is further leakage or a severe fluctuation in atmospheric temperature, this 
 pressure will remain constant. When such a condition is assured, it is ad- 
 visable to admit a small quantity of ammonia into the system. For instance, 
 a 10-ton plant would require about 15 pounds, a 25-ton plant, about 30 
 pounds, a 50-ton plant, about 60 pounds by weight and for a 100-ton plant, 
 about one cylinder of ammonia should be used. 
 
 A pressure of about 300 pounds per square inch should then be pumped 
 up, and in the event of further leakage in any part of the plant, it will 
 readily be detected because of the obnoxious odor of ammonia gas. 
 
 Several methods of detecting ammonia leaks are employed, among which 
 are the use of litmus paper, usually supplied by manufacturers of ammonia, 
 and also by the use of sulphur sticks. White litmus paper slightly moistened 
 
 72
 
 will turn red in the presence of ammonia fumes. Lighted sulphur sticks, 
 when brought into contact with the ammonia fumes will create a very black 
 smoke. This is one of the most positive methods known. After the plant 
 has been tested in this manner, all compressed air should be allowed to es- 
 cape down to the atmospheric pressure, after which the machine should be 
 started and the coils evacuated of any remaining air, until there exists a 
 vacuum of from 28 to 29 inches. 
 
 The machine should again be permitted to stand inactive for a period of 
 from six to eight hours for the purpose of determining whether the piping 
 and joints are absolutely tight against the external pressure of the atmos- 
 phere. If the system is tight, the vacuum will remain constant. Should the 
 vacuum be broken, it will indicate the presence of a leak, which should be 
 definitely located. 
 
 After the plant has been finally tested with both air pressure and vacuum, 
 the system should be pumped down to about 28 or 29 inches and the ammonia 
 drums connected. The ammonia should be permitted to run into the low pres- 
 sure side until a pressure of 10 or 15 pounds is secured. The condensing water 
 must then be supplied to ammonia condenser and the machine operated for the 
 purpose of confining the ammonia to the condenser and liquid receiver. When 
 pumping the ammonia into the system, we advise that the pressure on the low 
 pressure side of the machine never be decreased to the extent of less than 5 
 pounds, as the small quantity of ammonia then remaining in the ammonia 
 drum would not justify the expense of pumping down to a 10 or 15-inch vac- 
 uum as is frequently done for the purpose of securing a complete evacua- 
 tion of the drum. This is also a doubtful method of charging the machine, ow- 
 ing to the liability of admitting considerable air through the stuffing box 
 packing on the piston rod, when working the machine under a vacuum. This 
 of course, would create a false condensing pressure, which would necessitate 
 the interruption of the machine for the purpose of purging the system. 
 
 73
 
 PROPERTIES OP SATURATED AMMONIA GAS. 
 
 Gauge Pressure 
 Pounds 
 per Square Inch. 
 
 Absolute Pres- 
 sure, Pounds per 
 Square Inch. 
 
 Temperature 
 Degrees F. 
 
 Absolute Tem- 
 perature Degrees 
 Fahrenheit. 
 
 Latent Heat of 
 Evaporation In 
 Thermal Units. 
 
 Volume of One 
 Pound Vapor In 
 Cubic Feet. 
 
 Weight of One II 
 Cubic Foot of 
 Vapor in pounds, n 
 
 Volume of One 
 Pound of Liquid 
 in Cubic Feet. 
 
 Weight of One 
 Cubic Foot of 
 Liquid in pounds. 
 
 4.01 
 
 10.69 
 
 -40 
 
 420.66 
 
 579.67 
 
 24.38 
 
 .0410 
 
 .0234 
 
 42.589 
 
 2.39 
 
 12.31 
 
 -35 
 
 425.66 
 
 576.68 
 
 21.32 
 
 .0469 
 
 .0236 
 
 42.337 
 
 -0.57 
 
 14.13 
 
 -30 
 
 430.66 
 
 573.69 
 
 18.69 
 
 .0535 
 
 .0237 
 
 42.123 
 
 +1.47 
 
 16.17 
 
 -25 
 
 435.66 
 
 570.68 
 
 16.44 
 
 .0608 
 
 .0238 
 
 41.858 
 
 3.75 
 
 18.45 
 
 20 
 
 440.66 
 
 567.67 
 
 14.51 
 
 .0690 
 
 .0240 
 
 41.615 
 
 6.29 
 
 20.99 
 
 -15 
 
 445.66 
 
 564.64 
 
 12.83 
 
 .0779 
 
 .0241 
 
 41.374 
 
 9.1<> 
 
 23.80 
 
 10 
 
 450.66 
 
 661.61 
 
 11.38 
 
 .0878 
 
 .0243 
 
 41 . 135 
 
 12.22 
 
 'Z6.92 
 
 5 
 
 455.66 
 
 558.56 
 
 10.12 
 
 .0988 
 
 .0244 
 
 40.900 
 
 15.67 
 
 30.37 
 
 
 
 460.66 
 
 555.50 
 
 9.03 
 
 .1107 
 
 .0246 
 
 40.650 
 
 19.46 
 
 34.16 
 
 + 5 
 
 465.66 
 
 552.43 
 
 8.07 
 
 .1240 
 
 .0247 
 
 40.404 
 
 23.64 
 
 38.34 
 
 10 
 
 470.66 
 
 549.35 
 
 7.23 
 
 .1383 
 
 .0249 
 
 40.160 
 
 28.24 
 
 42.94 
 
 15 
 
 475.66. 
 
 546.26 
 
 6.49 
 
 .1541 
 
 .0250 
 
 39.920 
 
 33.25 
 
 47.95 
 
 20 
 
 480.66 
 
 543.15 
 
 5.84 
 
 .1711 
 
 .0252 
 
 39.682 
 
 38.73 
 
 53.43 
 
 25 
 
 485.66 
 
 540.03 
 
 5.27 
 
 .1897 
 
 .0253 
 
 39.432 
 
 44.72 
 
 59.42 
 
 30 
 
 490.66 
 
 536.91 
 
 4.76 
 
 .2099 
 
 .0255 
 
 39.200 
 
 51.22 
 
 65.92 
 
 35 
 
 495.66 
 
 533.78 
 
 4.31 
 
 .2318 
 
 .0256 
 
 38.940 
 
 58.29 
 
 72.99 
 
 40 
 
 500.66 
 
 530.63 
 
 3.91 
 
 .2554 
 
 .0258 
 
 38.684 
 
 65.96 
 
 80.66 
 
 45 
 
 505.66 
 
 527.47 
 
 3.56 
 
 .2809 
 
 .0260 
 
 38.461 
 
 74.26 
 
 88.96 
 
 50 
 
 510.66 
 
 524.30 
 
 3.24 
 
 .3084 
 
 .0261 
 
 38.226 
 
 83.22 
 
 97.92 
 
 55 
 
 5J5.66 
 
 521.12 
 
 2.96 
 
 .3380 
 
 .0263 
 
 37.994 
 
 92.89 
 
 107.59 
 
 60 
 
 520.66 
 
 517.93 
 
 2.70 
 
 .3697 
 
 .0265 
 
 37.736 
 
 103.33 
 
 118.03 
 
 65 
 
 525.66 
 
 514.73 
 
 2.48 
 
 .4039 
 
 .0266 
 
 37.481 
 
 114.49 
 
 129.19 
 
 70 
 
 530.66 
 
 511.52 
 
 2.27 
 
 .4401 
 
 .0260 
 
 37.230 
 
 126.52 
 
 141.22 
 
 75 
 
 535.66 
 
 508.29 
 
 2.09 
 
 .4791 
 
 .0270 
 
 36.995 
 
 139.40 
 
 154.10 
 
 80 
 
 540.66 
 
 505.05 
 
 .92 
 
 .5205 
 
 .0272 
 
 36.751 
 
 153.18 
 
 167.88 
 
 85 
 
 545.66 
 
 501.81 
 
 .77 
 
 .5649 
 
 .0273 
 
 36.509 
 
 167.92 
 
 182.62 
 
 90 
 
 550.66 
 
 498.55 
 
 .64 
 
 .6120 
 
 .0275 
 
 36.258 
 
 183.65 
 
 198.35 
 
 95 
 
 555.66 
 
 495.29 
 
 .51 
 
 .6622 
 
 .0277 
 
 36.023 
 
 200.42 
 
 215.12 
 
 100 
 
 560.66 
 
 492.01 
 
 .39 
 
 .7153 
 
 .0279 
 
 35.778 
 
 218.28 
 
 232.98 
 
 105 
 
 565.66 
 
 4*8 . 72 
 
 1.289 
 
 .7757 
 
 .0281 
 
 
 237.27 
 
 251.97 
 
 110 
 
 570.66 
 
 485.42 
 
 1.203 
 
 .8312 
 
 .0283 
 
 
 258.7 
 
 272.14 
 
 115 
 
 575.66 
 
 482.41 
 
 1.121 
 
 .8912 
 
 .0285 
 
 
 275.79 
 
 293.49 
 
 120 
 
 58J.66 
 
 478.79 
 
 1 041 
 
 .9608 
 
 .0287 
 
 
 301.46 
 
 316.16 
 
 125 
 
 585.66 
 
 475.45 
 
 .9699 
 
 1.0310 
 
 .0289 
 
 
 325.72 
 
 340.42 
 
 130 
 
 590.66 
 
 472.11 
 
 .9051 
 
 1.1048 
 
 .0291 
 
 
 
 350.46 
 
 365.16 
 
 135 
 
 595.66 
 
 468.75 
 
 .8457 
 
 1 . 1824 
 
 .0293 
 
 
 377.52 
 
 392.22 
 
 140 
 
 600.66 
 
 465.39 
 
 .7910 
 
 1.26421.0295 
 
 
 405.79 
 
 420.49 
 
 145 
 
 605.66 
 
 462.01 
 
 .7408 1.34971. 0297 
 
 
 435.5 
 
 450.20 
 
 150 
 
 610.66 
 
 458.62 
 
 .69461.4396 .0299 
 
 
 466.84 
 
 481.54 
 
 155 
 
 615.66 
 
 455.22 
 
 .65111.5358 .0302 
 
 
 499.70 
 
 514.50 
 
 160 
 
 620.66 
 
 451.81 
 
 .61 28 1.6318!. 0304 
 
 
 534.34 
 
 549.04 
 
 165 
 
 625.66 
 
 448.39 
 
 .576511.7344.0306 
 
 
 One atmosphere in this table is equal to a pressure of a column of mercury. 
 
 29.9 inches high. 
 Specific heat of ammonia gas and vapor at constant pressure = 0.508 
 
 The same at constant volume = 0.3913 
 
 Weight of 1 cubic foot liquid ammonia at 32 degrees Fahr. =39.108 Lbs. 
 
 Volume of 1 pound liquid ammonia at 32 degrees Fahr = 0.04557 cu.ft. 
 
 Specific heat of liquid ammonia = 1.01233 + 0.008378 t.
 
 TABLE OF BRINE SOLUTION. 
 
 (CHLORIDE OP SODIUM COMMON SALTS.) 
 
 Percentage 
 of Salt 
 by Weight. 
 
 Degrees on 
 Salometer 
 at 60 
 Degrees F. 
 
 o cs * 
 
 ?*&i 
 
 ijf 
 
 Specific 
 Heat. 
 
 Weight of 
 1 Gallon. 
 
 Pounds of 
 Salt in 
 1 Gallon. 
 
 Pounds of 
 Water in 
 l Gallon. 
 
 +3 r- 
 A W 
 
 sl 
 Z 
 
 Pounds of 
 Salt in 1 
 Cubic Foot. 
 
 Pounds of 
 Water in 1 
 Cubic Foot. 
 
 Freezing 
 Point, De- 
 grees Fah. 
 
 
 
 
 
 i. 
 
 1. 
 
 8.35 
 
 0. 
 
 8.35 
 
 62.4 
 
 0. 
 
 62.4 
 
 32. 
 
 1 
 
 4 
 
 1.C07 
 
 0.992 
 
 8.4 
 
 0.084 
 
 8.316 
 
 62.8 
 
 0.628 
 
 62.172 
 
 31.8 
 
 5 
 
 20 
 
 1.037 
 
 0.96 
 
 8.65 
 
 0.432 
 
 8.218 
 
 64.7 
 
 3.237 
 
 61.465 
 
 25.4 
 
 10 
 
 40 
 
 1.073 
 
 0.892 
 
 8.95 
 
 0.895 
 
 8.055 
 
 66.95 
 
 6.695 
 
 60.253 
 
 18.6 
 
 15 
 
 60 
 
 1.115 
 
 0.855 
 
 9.3 
 
 1.395 
 
 7.905 
 
 69.57 
 
 10.435 
 
 59.134 
 
 12.2 
 
 20 
 
 80 
 
 1.150 
 
 0.829 
 
 9.6 
 
 1.92 
 
 7.68 
 
 71.76 
 
 14.352 
 
 57.408 
 
 6.86 
 
 25 
 
 100 
 
 1.191 
 
 0.783 
 
 9.94 
 
 2.485 
 
 7.455 
 
 74.26 
 
 18.565 
 
 55.695 
 
 1.00 
 
 TABLE OP CHLORIDE OF CALCIUM SOLUTION. 
 
 Specific 
 Gravity at 64 
 Degrees Fah. 
 
 Degree 
 Beaume at 64 
 Degrees Fah. 
 
 Degree 
 Salometer at 
 64 Degrees 
 Fahrenheit. 
 
 Per Cent of 
 CaCl a . 
 
 Freezing 
 Point in 
 Degrees Fah. 
 
 * 2 11 
 
 Ills 
 
 **g. 
 
 1.007 
 
 1 
 
 4 
 
 0.943 
 
 +31.20 
 
 46 
 
 1.014 
 
 2 
 
 8 
 
 1.886 
 
 +30.40 
 
 45 
 
 1.021 
 
 3 
 
 12 
 
 2.829 
 
 +29.60 
 
 44 
 
 1.028 
 
 4 
 
 16 
 
 3.772 
 
 +28.80 
 
 43 
 
 1.035 
 
 5 
 
 20 
 
 4.715 
 
 +28.00 
 
 42 
 
 1.043 
 
 7 
 
 24 
 
 5.658 
 
 +26.89 
 
 41 
 
 1.050 
 
 7 
 
 28 
 
 6.601 
 
 425.78 
 
 40 
 
 1.058 
 
 8 
 
 32 
 
 7.544 
 
 + 24.67 
 
 38 
 
 1.065 
 
 9 
 
 36 
 
 8.487 
 
 + 23.56 
 
 37 
 
 1.073 
 
 10 
 
 40 
 
 9.430 
 
 +22.09 
 
 35.5 
 
 1.081 
 
 11 
 
 44 
 
 10.373 
 
 +20.62 
 
 34 
 
 1.089 
 
 12 
 
 48 
 
 11.316 
 
 +19.14 
 
 32.5 
 
 1.097 
 
 13 
 
 52 
 
 12.259 
 
 +17.67 
 
 30.5 
 
 1.105 
 
 14 
 
 56 
 
 13.202 
 
 +15.75 
 
 29 
 
 1.114 
 
 15 
 
 60 
 
 14.145 
 
 +13.82 
 
 27 
 
 1.122 
 
 16 
 
 64 
 
 15.088 
 
 +11.89 
 
 25 
 
 1.131 
 
 17 
 
 68 
 
 16.031 
 
 + 9.96 
 
 23.5 
 
 1.140 
 
 18 
 
 72 
 
 16.974 
 
 + 7.68 
 
 21.5 
 
 1.149 
 
 19 
 
 76 
 
 17.917 
 
 + 5.40 
 
 20 
 
 1.158 
 
 20 
 
 80 
 
 18.860 
 
 + 3.12 
 
 18 
 
 1.167 
 
 21 
 
 84 
 
 19.803 
 
 0.84 
 
 15 
 
 1.176 
 
 22 
 
 88 
 
 20.746 
 
 4.44 
 
 12.5 
 
 1.186 
 
 23 
 
 92 
 
 21.689 
 
 8.03 
 
 10.5 
 
 1.196 
 
 24 
 
 96 
 
 22.632 
 
 11.63 
 
 8 
 
 1.205 
 
 25 
 
 100 
 
 23.575 
 
 15.23 
 
 6 
 
 1.215 
 
 26 
 
 104 
 
 24.518 
 
 -19.56 
 
 4 
 
 1.225 
 
 27 
 
 108 
 
 25.461 
 
 -24.43 
 
 1.5 . 
 
 1.236 
 
 28 
 
 112 
 
 26.404 
 
 -29.29 
 
 1' ' vacuum 
 
 1.246 
 
 29 
 
 116 
 
 27.347 
 
 35.30 
 
 5 ' ' vacuum 
 
 1.257 
 
 30 
 
 120 
 
 28.290 
 
 -41.32 
 
 8.5' ' vacuum 
 
 1.268 
 
 31 
 
 
 
 29.233 
 
 -47.66 
 
 12' ' vacuum 
 
 1.279 
 
 32 
 
 
 30.176 
 
 -54.00 
 
 15' ' vacuum 
 
 1.290 
 
 33 
 
 
 31.119 
 
 -44.32 
 
 10'' vacuum 
 
 1.302 
 
 34 
 
 
 32.062 
 
 -34. 6 
 
 4 ' ' vacuum 
 
 1.313 
 
 35 
 
 
 33. 
 
 -25.00 
 
 1.5 pounds
 
 REFRIGERATING EFFECT OF QNE CUBIC FOOT OF AMMONIA 
 
 GAS AT DIFFERENT CONDENSER AND SUCTION 
 
 (BACK) PRESSURES IN B. T. U. 
 
 L 
 
 IJ 
 
 Temperature of the Liquid in Degrees Fahrenheit. 
 
 * 
 
 IS* 
 
 65. 70, 75 80 85 99 95 100 105 
 
 ii 
 
 11 
 
 
 
 la- 
 
 III 
 
 Corresponding Condenser Pressure (gauge), Pounds per Square Inch. 
 
 Is 
 
 n 
 
 103 115 127 139 153 168 184 200 218 
 
 -27 
 
 G.Prs 
 
 27.30 
 
 27 01 
 
 26.73 
 
 26.44 
 
 26.16 
 
 25.87 
 
 25.59 
 
 25.30 
 
 25.02 
 
 -20 
 
 4 
 
 33.74 
 
 33.40 
 
 33.04 
 
 32.70 
 
 32.34 
 
 31.99 
 
 31.64 
 
 31.30 
 
 30.94 
 
 15 
 
 6 
 
 36.36 
 
 36.48 
 
 36.10 
 
 35.72 
 
 35.34 
 
 34.96 
 
 34.58 
 
 34.20 
 
 33.82 
 
 10 
 
 9 
 
 42.28 
 
 41.84 
 
 41.41 
 
 40.97 
 
 40.54 
 
 40.10 
 
 39.67 
 
 39.23 
 
 38.80 
 
 5 
 
 13 
 
 48.31 
 
 47.81 
 
 47.32 
 
 46.82 
 
 46.33 
 
 45.83 
 
 45.34 
 
 44.84 
 
 44.35 
 
 
 
 16 
 
 54.88 
 
 54 . 32 
 
 53.76 
 
 53.20 
 
 52.64 
 
 52.08 
 
 51.52 
 
 50.96 
 
 50.40 
 
 5 
 
 20 
 
 61.50 
 
 60.87 
 
 60.25 
 
 59.62 
 
 59.00 
 
 58.37 
 
 57.75 
 
 57.12 
 
 66.50 
 
 10 
 
 24 
 
 68.66 
 
 67.97 
 
 67.27 
 
 66.58 
 
 65.88 
 
 65.19 
 
 64.49 
 
 63.80 
 
 63.16 
 
 15 
 
 28 
 
 75.88 
 
 75.12 
 
 74.35 
 
 73.59 
 
 72.82 
 
 72.06 
 
 71.29 
 
 70.53 
 
 69.70 
 
 20 
 
 33 
 
 85.15 
 
 84.30 
 
 83.44 
 
 82.59 
 
 81.73 
 
 80.88 
 
 80.02 
 
 79.17 
 
 78.31 
 
 25 
 
 39 
 
 95.50 
 
 94.54 
 
 93.59 
 
 92.63 
 
 91.68 
 
 90.72 
 
 89.97 
 
 88.81 
 
 87.86 
 
 30 
 
 45 
 
 106.21 
 
 105.15 
 
 104.09 
 
 103.03 
 
 101.97 
 
 100.91 
 
 99.85 
 
 98.79 
 
 97.73 
 
 35 
 
 51 
 
 115.69 
 
 114.54| 123. 39 
 
 112.24 
 
 111.09 
 
 109.94 
 
 108.79 
 
 107.64 
 
 106.49 
 
 NUMBER OP CUBIC FEET OF GAS THAT MUST BE PUMPED 
 PER MINUTE AT DIFFERENT CONDENSER AND SUCTION 
 PRESSURES TO PRODUCE ONE TON OF REFRIG- 
 ERATION IN TWENTY-FOUR HOURS. 
 
 1 ' 
 
 iJ 
 
 Temperature of the Gas in Degrees Fahrenheit. 
 
 o 
 
 IS? 
 
 65 70 75 80 85 90 93 100 105 
 
 Hi 1 
 
 Iflf 
 
 Corresponding Condenser Pressure (gauge), Pounds per Square Inch. 
 
 f-9 
 
 ll 
 
 103 115 127 139 153 168 184 200 218 
 
 
 G. Pres 
 
 
 
 
 
 
 
 
 
 
 27 
 
 1 
 
 7.22 
 
 7.3 
 
 7.37 
 
 7.46 
 
 7.54 
 
 7.62 
 
 7.70 
 
 7.79 
 
 7.88 
 
 -20 
 
 4 
 
 5.84 
 
 5.9 
 
 5.96 
 
 6.03 
 
 6.09 
 
 6.16 
 
 6.23 
 
 6.30 
 
 6.43 
 
 15 
 
 6 
 
 5.35 
 
 5.4 
 
 5.46 
 
 5.52 
 
 5.58 
 
 5.64 
 
 5.70 
 
 5.77 
 
 5.83 
 
 10 
 
 9 
 
 4.66 
 
 4.73 
 
 4.76 
 
 4.81 
 
 4.86 
 
 4.91 
 
 4.97 
 
 5.05 
 
 5.08 
 
 5 
 
 13 
 
 4.09 
 
 4.12 
 
 4.17 
 
 4.21 
 
 4.25 
 
 4.30 
 
 4.35 
 
 4.40 
 
 4.44 
 
 
 
 16 
 
 3.59 
 
 3.63 
 
 3.66 
 
 3.70 
 
 3.74 
 
 3.78 
 
 3.83 
 
 3.87 
 
 3.91 
 
 5 
 
 20 
 
 3.20 
 
 3.24 
 
 3.27 
 
 3.30 
 
 3.34 
 
 3.38 
 
 3.41 
 
 3.45 
 
 3.49 
 
 .10 
 
 24 
 
 2.87 
 
 2.9 
 
 2.93 
 
 2.96 
 
 2.99 
 
 3.02 
 
 3.06 
 
 3.09 
 
 3.12 
 
 15 
 
 28 
 
 2.59 
 
 2.61 
 
 2.65 
 
 2.68 
 
 2.71 
 
 2.73 
 
 2.76 
 
 2.80 
 
 2.82 
 
 20 
 
 33 
 
 2.31 
 
 2.34 
 
 20C 
 .OD 
 
 2.38 
 
 2.41 
 
 2.44 
 
 2.46 
 
 2.49 
 
 2.51 
 
 25 
 
 39 
 
 2.06 
 
 2.08 
 
 2.10 
 
 2.12 
 
 2.15 
 
 2.17 
 
 2.20 
 
 2.22 
 
 2.24 
 
 30 
 
 45 
 
 1.85 
 
 1.87 
 
 1.89 
 
 1.91 
 
 1.93 
 
 1.95 
 
 1.97 
 
 2.00 
 
 2.01 
 
 35 
 
 51 
 
 1.70 
 
 1.72 
 
 1.74 
 
 1.76 
 
 1.77 
 
 1.79 
 
 1.81 
 
 1.83 
 
 1.85 
 
 76
 
 DAILY ELEVATOR REPORT* 
 
 Dat.p Monroe Street 
 
 Hack. 
 No. 
 
 In 
 Sirvioe 
 
 Out of 
 Strvica 
 
 Thai Repair 
 
 Time OIT 
 
 REMARKS 
 
 1 
 
 
 
 
 
 
 
 
 
 
 
 2 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 3 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 4 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 5 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 6 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 7 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 & 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 ft 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 it 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 SUPPLIES WANTED 
 
 
 
 
 
 
 
 
 SIGNED.... 
 
 Working size of this sheet 8x14. 
 77
 
 ENGINE No. 1.* Month of... ...190... 
 
 Hours Cj'l 
 Run Oil 
 
 . Boars Klee. P. Hoars 
 
 Itmarks and Repairs 
 
 Working size of this sheet 12x16 
 78
 
 SWITCHBOARD READINGS 
 
 Date 
 
 DYNAMO 
 NO. 1 
 
 DYNAMO 
 NO. 2 
 
 DYNAMO 
 NO. 3 
 
 DYNAMO 
 NO. 4 
 
 DYNAMO 
 NO. 5 
 
 AM. Voltl 
 
 1A.M 
 
 2 
 
 3 
 
 TOTAL'AM AVERAGE AM. HRS 
 
 TOTAL K. W READING TOTAL WATT METER. 
 
 AVERAGE VOLTAGE 
 
 *Working size of this sheet 9x13. 
 
 79
 
 DAILY BOILER ROOM REPORT* 
 
 Date_ 
 
 EQUIPMENT 
 
 ON 
 
 OFF 
 
 DAYS RUN 
 
 VEEN 
 WASHED 
 
 CONDITION 
 
 DRAFT IX. REMAMS AND REPAIRS 
 
 In*. 
 
 lit. 
 
 Boiler No. 1... 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Boiler Ho. 2... 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Boiler Ho. 3... 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Boiler No. 4... 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Boiler No. 5... 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 STOKERS 
 
 
 
 
 
 
 REMARKS AND REPAIRS 
 
 No. 1 
 
 
 
 
 
 
 
 No. 2 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 No. 3 
 
 
 
 
 
 
 
 
 
 
 
 
 No. 4 
 
 
 
 
 
 
 
 
 
 
 
 Ho.5 
 
 
 
 
 
 
 STOKER FANS 
 
 ON 
 
 OFF 
 
 HOURS 
 RUN 
 
 CON- 
 DITION 
 
 GIL. OIL 
 PTS. 
 
 MACE. 
 OIL PTS. 
 
 REMARKS AND REPAIRS 
 
 Engine. 
 
 
 
 
 
 
 
 
 Motor.. 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 WJSBST1R 
 
 HEATERS 
 
 IH 
 
 OUT IDATSRUN 
 
 CON- 
 DITION 
 
 WHEN 
 CLEANED 
 
 Compound 
 Pounds 
 
 REMARKS AND REPAIRS 
 
 Ho. 1 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 No. 2 
 
 
 
 
 
 
 
 
 
 SAfiTY 
 VALVES 
 
 VEEN 
 TESTED 
 
 BLOWS 
 AT PRESS 
 
 CON- 
 DITION 
 
 REMARKS AND REPAIRS 
 
 No. 1 
 
 
 
 
 
 io.a 
 
 
 
 
 
 Ho.3 
 
 
 
 
 No. 4 
 
 
 
 
 
 Io.5 
 
 
 
 
 
 NO. OF LOADS OF; 
 CARS OF COAL BU 
 CARS OF ASH REh 
 LOADS OF COAL R 
 WEIGHT OF COAL 
 WEIGHT OF ASH.. 
 
 ISH REMOVED 
 RNEO 
 
 
 
 
 SUPPLIES VJf 
 GENERAL RE 
 
 
 1OVED 
 
 
 ECEIVE 
 BURNE 
 
 D 
 3 
 
 riARKS 
 
 
 
 
 FROM TO.... 
 
 SIGNED 
 
 "Working size of this sheet 12x16. 
 
 80 
 
 ENGINEER
 
 DAILY ENGINE ROOM REPORT* 
 
 Date_ 
 
 EQUIPMENT 
 
 STARTED 
 
 STOPPED 
 
 Hours Ru 
 
 Cylinder 
 i Oil 
 Pts. 
 
 REMARKS AND REPAIRS 
 
 Engine No. 1 . . 
 Engine No. 2 . . 
 Engine No. 3 . 
 Engine No. 4.. 
 
 1 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Engine lo. 5.. 
 
 
 
 
 
 
 
 
 
 
 ELEVAiOR 
 ' PDMPS 
 
 STARTED 
 
 STOPPED 
 
 HoursRun <ffj* 
 
 REMARKS AND REPAIRS 
 
 Pump No. 1 ... 
 
 
 
 
 
 
 
 
 Pump No. 2... 
 
 
 
 
 
 
 
 
 
 
 
 PumpKo.3... 
 Pump No. 4... 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 ELRVATOR 
 
 Auxiliaries 
 
 BURIED 
 
 STOPPED 
 
 HoursRnn 
 
 Cylinder 
 Oi Pts. 
 
 REMARKS AND REPAIRS 
 
 Pump No. 1 ... 
 Pump No. 2 ... 
 
 
 
 
 
 
 
 
 
 
 
 
 REFRIGERAT'G 
 
 STARTED 
 
 STOPPED 
 
 HoursRun 
 
 Condenser 
 Press 
 
 S. W; S 53! R^^S AND REPAIRS 
 
 Comp'rNo. 1.. 
 
 
 
 
 
 
 
 JEED-UMPS 
 
 STARTED 
 
 STOPPED HoursRun 
 
 FeedWat'r 
 
 5-s^ 
 
 Pump So. 1 ... 
 
 
 
 
 
 
 
 
 Pump No. 2 ... 
 
 
 
 
 
 
 
 
 
 FILTER 
 
 WHEN 
 WASHED 
 
 Condition 
 
 
 
 
 
 HEATING 
 SYSTEM 
 
 EXHAUST 
 
 LIVE 
 STEAM 
 
 a-* y. vc 
 3|i I 
 
 u'm Pump 
 
 tarted S-opped Hr..R U n .j^ a e court u.i, n.i nm 
 
 
 
 On Off 
 
 
 
 Pu m pS 
 
 tarted Stopped H-.,.. ' j^,po,,|o|o n |o ff 
 
 GENERAL REMARKS.-.. 
 
 SIGNED 
 
 ..TO 
 
 *Working size of this sheet 12x16. 
 
 81 
 
 ENGINEER
 
 TROUBLE TICKET. 
 
 DATE 
 
 ROOM NO. 
 
 TIME REC'D 
 
 A. M. 
 
 P. M. 
 
 NATURE OF TROUBLE 
 
 MATERIAL USED 
 
 TIME 0. K. 
 
 TIME PUT IN 
 
 REPAIRED BY 
 
 A. M. 
 
 P. M. 
 
 
 
 
 
 RECEIVED BY 
 
 PHONE 
 
 OFFICE 
 
 'Working size of this sheet 6x9 
 82
 
 INDEX 
 
 Page 
 
 Absorption Plant 72 
 
 Absorption Refrigeration 40 
 
 Air Chambers on Discharge 27 
 
 on Suction 26 
 
 " Compressed Pressure 36 
 
 Temperature of 37 
 
 " Compressor Clearance- 36 
 
 . " Condensing 37 
 
 " Lifts . 36 
 
 ' Pressure in Compressor 36 
 
 Alternate Method Test 56 
 
 A. S. M. E. Boiler Trial Rules 50 
 
 Ammonia, Aqua 40 
 
 Compressor 40 
 
 Gas 76 
 
 Table of 74 
 
 Analysis of Coal 55 
 
 " of Flue Gases 55 
 
 Apparent Clearance in Compressor '. . . . . 36 
 
 Aqua-Ammonia 40 
 
 Artificial Ice 41 
 
 Ashes 55 
 
 Automatic Damper Regulator 35 
 
 Engine n 
 
 Auxiliary Valves on Pumps . . 29 
 
 g^ & W. Boiler 18, 19, 20 
 
 Back Pressure, Compound Engine 13 
 
 Bagging 23 
 
 Balanced Slide Valve 6 
 
 Belt Double Power off 39 
 
 Driven Pump 29 
 
 Belting 39 
 
 Blister on Boiler Plate 23 
 
 Blowing off Point 19 
 
 Blow-off Pipe 18 
 
 Boiler and Furnace ... 34 
 
 B. & W . . . . 18, 19, 20 
 
 Bag in 23 
 
 Blow-off 18 
 
 Braces 18 
 
 Cahall 21 
 
 Circulation 18,22 
 
 Crown Sheet 16 
 
 Cutting in of 19 
 
 Drift Pin . 16 
 
 Efficiency . . 34, 56 
 
 Feeding Economy 15 
 
 Feed Pipes, Where Placed .... . . 20
 
 Boiler Feed Pump, How to Drive . 
 Feed Water, Hardness 
 Furnace 
 " Headers 
 
 Page 
 29 
 
 42 
 34 
 16 
 
 Heads, Dished 
 " Heine 
 
 15 
 
 2O 
 
 Inspection 
 
 
 Inspection of Brace .... 
 
 18 
 
 Lap Joint 
 
 17 
 
 Legs Stays 
 
 17 
 
 Iowa 
 
 23 
 
 Lugs, How Attached .... 
 
 . . . . 18 
 
 " Lugs 
 
 18 
 
 Man-holes 
 
 15 
 
 Mud Drums 
 
 . . . . 16 
 
 Plate Bag in 
 
 23 
 
 Plate Blistered 
 
 23 
 
 Plate Straight 
 
 24 
 
 Pulsation in 
 
 14 
 
 Put into Service 
 
 19 
 
 Report 
 
 . . . . 80 
 
 Rivets 
 
 M 
 
 " Rivets, Strength 
 
 15 
 
 Seams 
 
 15 
 
 " Staying 
 
 16 
 
 Stays 
 
 14 
 
 Stays, Diagonal 
 
 17 
 
 Stays in Tension .... 
 
 18 
 
 Steaming and Circulation 
 Stirling ; 
 
 22 
 
 23 
 
 " Strain . 
 
 2O 
 
 Test 
 
 50 
 
 To Lay Up 
 
 19 
 
 Trial, Rules 
 
 50 
 
 Tubes 
 
 .... 14 
 
 Tube Caps 
 
 16 
 
 Tube Split to Mend .... 
 
 21 
 
 Tubes, Straight or Curved 
 
 16 
 
 Water Level in 
 
 22 
 
 Braces, Through 
 
 18 
 
 Breaker Vacuum 
 
 32 
 
 Brine Solution 
 
 75 
 
 Building Ventilation 
 
 70 
 
 Butt Straps, How Placed .... 
 
 15 
 
 " Strap Joint, Advantages of ... 
 
 20 
 
 Qahall Boiler 
 Calcium Solution 
 
 21 
 
 75 
 
 Caloric Test 
 
 55 
 
 Calorimeter Test 
 
 42 
 
 Card Indicator 
 
 41 
 
 Cast Iron Mud Drums 
 
 19 
 
 Caulking Tools 
 
 15 
 
 Centrifugal Pump 
 
 28 
 
 " Suitable for .... 
 
 28 
 
 " Work in .... 
 
 25 
 
 Chimney Draft 
 
 35 
 
 Flues 
 
 34 
 
 H. P. . 
 
 63 
 
 Circulation in Boiler 
 
 l8, 22 
 
 84
 
 Page 
 
 Clearance as Effected by Connecting Rod 10 
 
 Effect on Economy 6 
 
 in Air Compressor 36 
 
 Closed Heater 31 
 
 Coal Analysis ' 55 
 
 '' at Test 50 
 
 " Burning Furnace 34 
 
 " Cost of, & Steam 34 
 
 : Moisture 54 
 
 " Ultimate Analysis 57 
 
 Cocks Condenser 33 
 
 Code of 1899 50 
 
 Cold Water Valves for Pumps 27 
 
 Combustion, Complete 34 
 
 Compound Gauge "... 43 
 
 Engine 12 
 
 Engines Back Pressure .13 
 
 Engines vs. Simple . 
 
 Engine Types 13 
 
 Engines, Why Used 12 
 
 Compressed Air Valves for. Pumps ....... 27 
 
 Compression Plant 7 2 
 
 Refrigeration 40 
 
 to Change 5 
 
 Compressor Ammonia 40 
 
 Clearance 36 
 
 Condensing 37 
 
 Condenser Cooling Surface of 32 
 
 Horse Power 32 
 
 Jet 12,31 
 
 Jet and Surface 32 
 
 Priming 33 
 
 Surface 12,31 
 
 Tubes 31 
 
 Types and Uses 31 
 
 Water Per Hour 32 
 
 Condensing Air Compressor 37 
 
 Engine Cocks 33 
 
 Condensing vs. Non-Condensing Engines 8 
 
 Connecting Rod, Length of 10 
 
 Connecting Rod Length Effect on Guide Pressure .... 9 
 
 Contraction of Steel Tire 38 
 
 Cooling Surface in Condenser . 32 
 
 Corliss Valve 7 
 
 Cost of Coal 34 
 
 Cost of Steam 34 
 
 Cost to Produce Draft 34 
 
 Covering Pipe 65 
 
 Crab & Bolt 22 
 
 Crank Angles 13 
 
 Cross Head Pressure 9 
 
 Head, to Disconnect 9 
 
 Crown Sheets 16 
 
 Cut-off Effect of a Riding Valve 6 
 
 Four Valve 7 
 
 Four Valve, Two Eccentrics 
 
 Late Advantages 8 
 
 None in Duplex Pump 27 
 
 Single Eccentric 7 
 
 to change 5 
 
 85
 
 Page 
 
 Cut-off With Slide Valve Engine 5 
 
 Cushion in Pump 27 
 
 Valve 28 
 
 Cylinder Temperature Drop 41 
 
 )amper Regulator 35 
 
 Dash Pots 8 
 
 Deep Well Air Lift 36 
 
 Deep Well Pump 36 
 
 Detachable Valve Gear High Speed 9 
 
 Valve Gear, How Closed . 8 
 
 Diagonal Stay 14 
 
 Stays, Length of 17 
 
 Dimension of Pipes 64 
 
 Discharge Air Chamber 27 
 
 Air Pressure 36 
 
 Double Belt, Power of . 39 
 
 Draft 35 
 
 Forced 35 
 
 From Fan 35 
 
 Gauge 42 
 
 Induced 35 
 
 Mechanical 35 
 
 Mechanical, Cost . 34 
 
 Drift Pins 16 
 
 Drilled Holes 24 
 
 Duplex Pump to Set Valves 27 
 
 " Pump-Stroke . ... . . . . . . . 25 
 
 Pump Valve Lap 27 
 
 T7conomizer and Draft 35 
 
 Fuel 31-34 
 
 Tubes to Clean 33 
 
 Economy Effect of Clearance on 6 
 
 of Feed Pump 15 
 
 of Injector 15 
 
 of Steam Pumps 25 
 
 of Super-heat in Steam 10 
 
 of Variously Driven Pumps 29 
 
 Eccentric Single Cut-off 7 
 
 Eccentrics Advantage of Two . . . 12 
 
 Two Cut-off 8 
 
 1899 Code of 50 
 
 Efficiency of an Injector 29 
 
 of Boiler 56 
 
 " of Boiler Furnace 34 
 
 Electric Elevator . 39 
 
 Elevator Electric 39 
 
 High Pressure Hydraulic .... 39 
 
 " Light or Loaded 39 
 
 " Passenger 39 
 
 Plant . 39 
 
 " Report from 77 
 
 Engine Automatic H 
 
 Classes of 12 
 
 " Clearance 10 
 
 " Compound 12 
 
 Compound Back Pressure 13 
 
 " Compound Types of 13 
 
 " Compound, Why Used 12
 
 Page 
 
 Engine Condensing Cocks 33 
 
 Condensing to Start 32 
 
 " Condensing with two Eccentrics ...... 12 
 
 Condensing or Non-Condensing 8 
 
 Economy with Superheat 10 
 
 " Four Valve Advantages 7 
 
 Four Valve Cut-off 7 
 
 Gas 38 
 
 High Speed Valve Gear 9 
 
 Lead . 10 
 
 Power to Change 9 
 
 Report 78 
 
 Room Report 81 
 
 Simple vs. Compound 8 
 
 Slide Valve 5 
 
 Slide Valve Advantage 7 
 
 Superheated Steam in 10 
 
 Throttling n 
 
 to Change Valve Setting " 9 
 
 " to take Charge of 10 
 
 Engineers Duty 10-19 
 
 Evaporation Test 56 
 
 Water, Cost of 34 
 
 Exhaust in Compound Engines 13 
 
 pan Draft 35 
 
 Feed Pipes 34 
 
 Pump 15 
 
 Water Heater & Injector 29 
 
 Hardness 42 
 
 Heater 33 
 
 in Economizer 35 
 
 Pipes. Location of 20 
 
 too Hot for Injector 29 
 
 Ferris Wheel 38 
 
 Fire Protection 40 
 
 Flues Chimney 34 
 
 Flue Gases 55 
 
 Fly Ball Governor Failure 8 
 
 Foot Valve 27 
 
 Force Feed Lubrication 8 
 
 Forced Draft ' -35 
 
 Lubrication 6 
 
 Four Valve Engine Advantages 7 
 
 Cut-off 7 
 
 Fuel Economizer 31-34 
 
 and Draft 35 
 
 Tubes to Clean 33 
 
 Full Stroke Steam in Pump 27 
 
 Furnace Boiler 34 
 
 Efficiency . 34 
 
 & Boiler 34 
 
 Fusible Plugs 19 
 
 Plug to Melt 21 
 
 (~Jas Ammonia 76 
 
 Gas Engine 38 
 
 Producer 38 
 
 Gauge. Compound . . 43 
 
 Draft 42 
 
 87
 
 Page 
 
 Gauge, Glass & Level 22 
 
 Glass Valve Shut-off 22 
 
 Loop . 42 
 
 Pressure 42 
 
 Gauges, Pressure and Vacuum 43 
 
 Globe Valve, How Placed 40 
 
 Governor Belt Break 8 
 
 Defects in 8 
 
 Fly Ball Failure 8 
 
 Inertia 11 
 
 Range II 
 
 Throttling n 
 
 Throttling on Gas Engine 38 
 
 Gravity Heating System 41 
 
 Gridiron Valve 7 
 
 Guide Pressure 9 
 
 T-Iammer Test 14 
 
 Water 40 
 
 Hand Hole Bolt, to Protect 22 
 
 " Crab, Lost 21 
 
 " " " to Protect 22 
 
 " Plate Burned off 21 
 
 " Riveting 24 
 
 Height of Pump Lift 26 
 
 Heine Boilers 20 
 
 Heat Balance 56 
 
 " in Injector 50 
 
 Heater and Injector 29 
 
 " Closed 33 
 
 " Open 33 
 
 Heaters Types 3 1 
 
 Heating Steam Risers , 71 
 
 Heating System, Gravity 41 
 
 System Vacuum 42 
 
 High Pressure Elevator 39 
 
 Valves 39 
 
 Horse Power for Ventilation 7 
 
 " of Chimney 63 
 
 " " " Condenser 32 
 
 Hot Water Pump 26 
 
 to an Injector 29 
 
 Valves for Pump 27 
 
 " Well Temperature 3 2 
 
 Hydraulic Elevator 39 
 
 Jce, Artificial 4 1 
 
 " Transparent 4 1 
 
 Indicator Card Long as Possible , . 41 
 
 Induced Draft 35 
 
 Inertia Governor .11 
 
 Injector and Feed Water Heater 29 
 
 Injector Economy 15 
 
 Efficiency 29 
 
 Failure to Work 29 
 
 Heat in So 
 
 How it Works 3 
 
 How it Uses Steam . 29 
 
 Principle of 30 
 
 With Heater 33
 
 injector With Hot Water 
 
 29 
 
 Inspection of a Boiler 
 
 14 
 
 Iowa Boiler 
 
 23 
 
 J et Condenser 
 
 12,31,32 
 
 Kent Chimney Formulas 
 
 63 
 
 J^ap Joint 
 1 on Pump Valves 
 
 17 
 27 
 
 Late Cut-off Advantages 
 
 
 Laying up a Boiler 
 
 19 
 
 Lead, in Steam Engine 
 
 10 
 
 Unequal 
 
 6 
 
 Lift of a Pump 
 
 26 
 
 Locomotive Crown Sheets 
 
 16 
 
 Stav Bolts 
 
 J 7 
 
 Lost Motion in Valve Gear ........ 
 
 ' . 28 
 
 Lubrication Force Feed 
 
 8 
 
 Forced System 
 
 6 
 
 Lugs How Attached 
 
 18 
 
 Material of 
 
 18 
 
 JVJa chine Riveting 
 Manholes Reinforced 
 
 24 
 15 
 
 Mechanical Draft Cost 
 
 34 
 
 Fan 
 
 35 
 
 Memoranda 
 
 83 
 
 Metal Pump Valves 
 
 27 
 
 Moisture in Coal 
 
 54 
 
 Motor Driven Pump 
 
 20 
 
 Mud Drums 
 
 76 
 
 in Brick Work 
 
 16 
 
 of Cast Iron 
 
 19 
 
 "NJational Presidents 
 N. A. S. E. Directory 
 
 49 
 49 
 
 N. A. S. E. Preamble 
 
 49 
 
 Non-Condensing vs. Condensing Engines .... 
 
 8 
 
 Office Building Elevator 
 Open Heaters 
 
 39 
 
 packed Plunger Pump . 
 Passenger Elevator . . . . . 
 
 25 
 39 
 
 Pipe Covering 
 
 " Suction 
 
 6 5 
 25 
 
 Pipes Water Hammer in 
 
 40 
 
 Standard Dimension 
 
 64 
 
 " Pitting in 
 
 40 
 
 Piston Pump 
 
 25 
 
 Rod, to Disconnect 
 
 9 
 
 Valve vs. Slide Valve 
 
 6 
 
 Pitting in Pipes /. . 
 
 40 
 
 Plant, Elevator 
 
 39 
 
 Pluneer Pump 
 Poppet Valves 
 
 25 
 7 
 
 Poppet Valves and Super Heated Steam .... 
 
 4! 
 
 Pop Safety Valve Failure to Close ...... 
 
 22
 
 Page 
 
 Pop Safety Valves How Set 19 
 
 Power Driven Pump 29 
 
 of Belt . 39 
 
 ' Engine, to change 9 
 
 for Refrigeration . . 72 
 
 " Required for Elevator . 39 
 
 Preamble N. A. S. E. . 49 
 
 Pressure Gauge 42 
 
 of Air in Compresser 36 
 
 on Guides 9 
 
 " on Receiver 12 
 
 of Steam in Receiver 10 
 
 Priming Condenser 33 
 
 Producer, Gas 38 
 
 Pulsation in Boilers 14 
 
 Pump Air Chamber 27 
 
 " on Suction 26 
 
 Auxiliary Valve 29 
 
 Boiler Feed 15 
 
 Centrifugal 28 
 
 Centrifugal Work Done in _ 25 
 
 Cushion in 27 
 
 Valve 28 
 
 Deep Well 36 
 
 Direct vs. Power Driven 29 
 
 Duplex Stroke 25 
 
 Economy 25 
 
 for Hot Water 26 
 
 Foot Valve 27 
 
 Height above Supply 26 
 
 How Lift Water 26 
 
 Piston Type 25 
 
 Plunger Type 25 
 
 Rotary 28 
 
 Steam, Full Stroke 27 
 
 Steam, Size for Economy 25 
 
 Strainer 25 
 
 Suction Pipe 25 
 
 Valves 27 
 
 Lap 27 
 
 " Lost Motion . 28 
 
 To Set . . 27 
 
 Punched Holes 24 
 
 Real Clearance in Compressor 36 
 
 Receiver and Cranks 13 
 
 Pressure in 10 
 
 " Pressure Failure of . 12 
 
 Why Used 13 
 
 Refrigeration 40 
 
 Absorption Process 72 
 
 Compression Plant 72 
 
 Power for 72 
 
 Test 72 
 
 Tonnage 72 
 
 Regulator, Damper 35 
 
 Re-inforcing Plates 18 
 
 Riding Cut-off Valve 6 
 
 Rivet Holes Punched and Drilled 24 
 
 Spacing 14 
 
 90
 
 Page 
 
 Rivets Double Shear 15 
 
 Single Shear 15 
 
 Size of 14 
 
 Strength 15 
 
 Riveting Machine and Hand 24 
 
 Rotary Pump 28 
 
 Rubber Pump Valves 27 
 
 Qafety Valve Blowing 22 
 
 " " Blow-off Point 19 
 
 Safety Valve Dead Weight 24 
 
 Tandem 24 
 
 " " to Set Same 20 
 
 Setting Pump Valves 27 
 
 Shearing Strength . 24 
 
 Simple vs. Compound Engines . 8 
 
 Single Eccentric Cut-off 7 
 
 Sizes of Pipes 64 
 
 Slide Valve, Balanced 6 
 
 ' Engine 5 
 
 Advantages 7 
 
 " Lead 6 
 
 " " vs. Piston Valve 6 
 
 Smoke During Test 55 
 
 Standard Method Test .'........ 56 
 
 Stand Pipes for Fire 40 
 
 Starting Condenser Engine 32 
 
 Stays Diagonal vs. Through 14 
 
 Stay Bolts 16 
 
 Application of 17 
 
 Defective 17 
 
 Steam Air Compressor 37 
 
 Calorimeter, Use of 42 
 
 Cost to Evaporate '34 
 
 Drop in Temperature 41 
 
 Gauge 42 
 
 Heating Risers 71 
 
 In an Injector How Used 29 
 
 Line Pitting 40 
 
 Pump Auxiliary Valve 29 
 
 Pipe Covering 65 
 
 Pressure in Receiver 10 
 
 Quality of . . 53 
 
 Radiation 71 
 
 Superheat Economy 10 
 
 Superheated 41 
 
 Throttled to Pump T 25 
 
 Valves . 39 
 
 Valves on Pump 27 
 
 " Velocity in Injector 30 
 
 Steel Tire 38 
 
 Stirling Boiler 23 
 
 Strainer for Pump 25 
 
 Strains in Boilers .20 
 
 Stroke of Duplex Pump . . . 25 
 
 Strength Shearing 24 
 
 Tensile 24 
 
 " Torsional 24 
 
 Submerged Tube Sheet 18 
 
 Suction, Air Chamber on ,26
 
 Page 
 
 Suction, Foot Valve 27 
 
 " Gas Producer 38 
 
 Lift 26 
 
 of Hot Water . 26 
 
 Pipe 25 
 
 Water Grit in 25 
 
 Superheat in Steam Economy of 10 
 
 Superheated Steam Defined . 41 
 
 " Disadvantages of 41 
 
 Superheater ... 31 
 
 Surface Condenser . . . 12,31,32 
 
 Switchboard Report .... 79 
 
 Air for Ventilation 70 
 
 Ammonia . 74 
 
 Ammonia Gas 76 
 
 B. H. P. Evaporation 61 
 
 Brine Solution 75 
 
 Building Ventilation 70 
 
 Calcium Solution 75 
 
 Coal Heat Value 62 
 
 Coal & Oil . . . 62 
 
 Evaporation, Factor of 60 
 
 Evaporation per B. H. P. . 61 
 
 Factor of Evaporation 60 
 
 Flue Velocities 71 
 
 B. H. P. Steam Consumption 61 
 
 Kent's Chimney Formulas 63 
 
 Oil and Coal 62 
 
 Pipe Sizes 64 
 
 Radiation 7 1 
 
 Refrigeration, Amount of Gas 76 
 
 Report on Boilers 80 
 
 Report on Elevator 77 
 
 Report on Engine 78 
 
 Report of Engine Room 81 
 
 Steam 66-70 
 
 Steam Consumption for I. H. P 61 
 
 Steam Discharges 62 
 
 Steam. Risers 7 1 
 
 Switch Board 79 
 
 Trouble 82 
 
 Ventilation . . . . : 7 
 
 Tandem Safety Valves 24 
 
 Tank Heads Dished 15 
 
 Temperature Drop in Cylinder 41 
 
 in Hot Well 32 
 
 of Compressed Air 37 
 
 Tensile Strength 24 
 
 Test Alternate Method 56 
 
 Evaporative 56 
 
 " Refrigeration 7 2 
 
 " Standard Method 56 
 
 Throttled Steam to Pump . 
 
 Throttling Engine 
 
 " Governor ll 
 
 " Governor or Gas Engine 38 
 
 Tire, Steel . ... 38 
 
 Tonnage in Refrigeration 7 2 
 
 Tools, Caulking 15
 
 
 
 Page 
 
 Toi 
 
 
 
 Trouble Report 
 
 . . . , . . ' 82 
 
 True Water Level 
 
 22 
 
 Tube Caps 
 
 16 
 
 " 
 
 Headers, nipple .... 
 
 16 
 
 " 
 
 Sheet Submerged 
 
 18 
 
 " 
 
 Split, How to Mend 
 
 21 
 
 " 
 
 Condenser .... 
 
 ..... 31 
 
 " 
 
 Curved or Straight 
 
 16 
 
 " 
 
 to Fasten in Head 
 
 14 
 
 Tubular Boiler Inspection 
 
 14 
 
 Ui 
 
 timate Analysis of Coal 
 
 57 
 
 "yacuum 
 
 32 
 
 
 Breaker 
 
 32 
 
 
 Gauge 
 
 43 
 
 
 Heating System 
 
 42 
 
 
 How Lost .... 
 
 32 
 
 Va 
 
 ve, Corliss 
 
 7 
 
 
 Cushion 
 
 28 
 
 
 for Pumps .... 
 
 27 
 
 
 Gear, High Speed . . . 
 
 9 
 
 
 Gear Detachable How Closed 
 
 8 
 
 
 High Speed 
 
 
 
 Lost Motion in 
 
 
 
 Gears and Superheated Steam . 
 
 41 
 
 
 Globe, How Placed 
 
 40 
 
 
 High Pressure .... 
 
 - - . . 39 
 
 
 Gridiron 
 
 7 
 
 
 Lap 
 
 
 
 Piston 
 
 5 
 
 
 Poppet . . . ... 
 
 7 
 
 
 Setting to Change 
 
 9 
 
 
 Slide 
 
 6 
 
 Ventilation 
 
 7 
 
 
 H. P. for 
 
 70 
 
 Velocity in Flues 
 
 71 
 
 ' 
 
 of Steam in Injector 
 
 . . . 30 
 
 Ver 
 
 tical Boiler Stavs 
 
 17 
 
 'yV'ater Circulation in Boiler 
 
 . . . . . 18 
 
 
 " Cost to Evaporate 
 
 34 
 
 Water for Condenser .... 
 
 32 
 
 " 
 
 in Feed Economizer 
 
 35 
 
 " 
 
 Hammer . ... 
 
 40 
 
 " 
 
 Hard for Boilers 
 
 42 
 
 " 
 
 Hot for Pump .... 
 
 26 
 
 " 
 
 Hot to an Injector 
 
 29 
 
 " 
 
 Leg, How Stayed 
 
 17 
 
 " 
 
 Level in Glass 
 
 22 
 
 " 
 
 Sand and Grit in ... 
 
 25 
 
 " 
 
 Suction 
 
 25,26 
 
 ' 
 
 Supply Below Pump 
 
 26 
 
 " 
 
 Tender Duties 
 
 IQ 
 
 
 Tube Boiler Circulation 
 
 18 
 
 
 Headers 
 
 16 
 
 " 
 
 Mud Drums 
 
 16 
 
 " 
 
 " " Tube Caps 
 
 16 
 
 Well, Hot Temperature 
 
 32 
 
 Work Done in Centrifugal Pump 
 
 25
 
 ELECTRICITY 
 
 Page 
 
 45 
 
 Alternating Current 44 
 
 Alternating Current Generator .... ... 45 
 
 Alternator, to Start up 47 
 
 Battery, Storage 46 
 
 Boosters 46 
 
 Booster Set 44 
 
 (Compound Wound Generator 46 
 
 " Motor 47 
 
 Conductor 45 
 
 Constant Current Generator 47 
 
 Converter, Rotary 46 
 
 Current Alternating .44 
 
 Direct 44 
 
 Quantity 45 
 
 Direct Current 44 
 
 J^conomical Voltage 45 
 
 Electric Magnet 45 
 
 Electric Elevator 39 
 
 " Terms 45 
 
 Elevator Electric - ... 39 
 
 Explosion of Lamp 46 
 
 JTields of Generator 45 
 
 Field- Strength and Speed ........ 4 
 
 Force, Magnetic 45 
 
 Frequency, Changes 46 
 
 Qenerator Compound 46 
 
 " Constant Current 47 
 
 Field 45 
 
 Jnduced Magnet 45 
 
 Induction Motor 48 
 
 T amps in Series < 46 
 
 ' Lead 47 
 
 TV/Tagnet Electric 45 
 
 IVA Electro 45 
 
 " Induced 45 
 
 Natural 45 
 
 Magnetic Force, Limits of 45 
 
 Motor Compound ... 47 
 
 Driven Pump 29 
 
 " Induction ... 48 
 
 Series . . 47 
 
 94
 
 Page 
 
 Motor Shunt .... ....... 47 
 
 Speeds & Field Strength ........ 48 
 
 " Synchronous .......... 48 
 
 Natural Magnet ........... 45 
 
 ............ 45 
 
 Effect on Amperes ........ 45 
 
 pilot Lamp Explosion ......... 46 
 
 Potential ............ 45 
 
 Resistance ...... ...... 45 
 
 Rotary Converter .......... 46 
 
 gecondary Windings . ...... 44 
 
 Series Lamps ........... 46 
 
 Series Wound Motor .......... 47 
 
 Shunt Wound Motor ...... .... 47 
 
 Solenoid Purpose of .......... 44 
 
 Step Down Transformer . . . . . . . . 44. 46 
 
 " Up Transformer ......... 44 
 
 Storage Batteries ... ....... 46 
 
 Sub-Station Apparatus ........ . 46 
 
 Synchronous Motor ........ 48 
 
 'transformer ..... . ..... 44 
 
 Step Down ......... 46 
 
 .............. 45 
 
 Voltage ............ 45 
 
 Voltage Combined Load ......... 45 
 
 Windings ..... , ...... 44
 
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 TJT 
 
 THE LIBRARY 
 UNIVERSITY OF CALIFORNIA 
 
 Santa Barbara 
 
 THIS BOOK IS DUE ON THE LAST DATE 
 STAMPED BELOW.
 
 UC SOUTHERN 
 
 000630890 2