TD 491 
 .P7 
 Copy 1 
 
T D 
 
LIBRARY OF CONGRESS. 
 
 Chap. __ Copyright No. 
 
 ShelfDD....^ ^ I 
 
 UNITED STATES OF AMERICA. 
 
Catalogue of, 
 
 IbiQb pressure Ib^&raulic 
 
 ittings * and * Flanges 
 
 . , ffoll^*6 ipatent . . 
 auD^ 
 
 IFntormation for mae In DesiQuino 
 
 ^Rydraullc* Plants «« 
 
CATALOGUE OF 
 
 HIGH PRESSURE HYDRAULIC 
 
 FITTINGS AND FLANGES. 
 
 (folly's patent.) 
 
 AND 
 
 INFORMATION FOR USE>' IN DESIGNING 
 
 hydraulic/plants. 
 
 john'^latt, 
 
 MEMBER OF THE AMERICAN SOCIETY OF MECHANICAL ENGINEERS^ 
 AND ASSOC. M. INST. C. K. 
 
 m 
 
 
 
 \^\ u^" ^--^r 
 
 "TIGHT JOINT" FLANGE. \ 
 
 Tio-xacrr toii^tt 
 
 ; AUfitS1896 
 
 159-161 BANK STREET, 
 
 HlUV$)'^ 
 
^ 
 
 f 
 
 <^% 
 
 Copyi-ight. 1^96. 
 
 BY 
 
 TIGHT JOINT COMPANY. 
 New York. 
 
 im^ 
 
PREFACE. 
 
 In the following pages it has been our aim to place before 
 the hydraulic engineering world particulars of our well- 
 known ''Tight Joint" and its adaptation to fittings and 
 flanges specially designed to suit their needs. 
 
 We are glad to be able to report that engineers can now 
 procure fittings and flanges that will insure their being able 
 to make tight joints, and that the trouble and annoyance of 
 leaky joints they have heretofore had to contend w4th, can be 
 obviated by the use of our specialties. 
 
 For the compiling of the ' ' Information for use in designing 
 Hydraulic Plants " we are indebted to Mr. John Piatt, the well- 
 known high pressure hydraulic engineer, of 97 Cedar St., New 
 York City. Much of the information is taken from notes col- 
 lected by him, both in this country and while associated with 
 Mr. James Piatt, Member of Council of the Institute of Mechan- 
 ical Engineers, who has done so much to further the develop- 
 ment of high pressure hydraulic machinery, A number of 
 the tables have been specially conipiled and others taken from 
 Mr. William Kent's ''Mechanical Engineer's Pocket Book," 
 Mr. Henry Adams's "Hand-book for Mechanical Engineers." 
 and other engineering note -books. 
 
 We trust that the information given will be found of benefit 
 to those who undertake the designing of hydraulic machinery, 
 and we shall be glad if its users will kindly draw^ our attention 
 to any errors of omission or commission, and also make any 
 suggestions that may tend to make the '* Information " more 
 valuable. 
 
ERRATA. 
 
 l\ige 27, 
 
 Table of W. I. & S. pipe 
 should read, 
 
 No. of til reads per inch, 
 48 
 
 18 
 
 14 
 
 14 
 
 llt^ 
 
 lU 
 
 IH 
 
 ili^ 
 8 
 
 Faxje 37. 
 
 Capacities of Cylinders. 
 
 Diani. 
 
 Inches. 
 
 18 
 
 1 
 
 Load at 
 1500 lbs. 
 
 199050 
 
 Page 3Jf. 
 
 Thickness of cylinder 
 should read, 
 
 Rankine gives. 
 
 VAs~+~p 
 X r 
 s — p 
 
 Page 39. 
 
 Seventh line from bottom 
 of page should read, 
 . Efficiency per cent. 
 
 80 ' 76 72 
 
 Page 41. 
 
 Thirteenth line from to]) 
 of page should read, 
 
 V pipe reduced to f " at one 
 point. 
 
 Formulae for areas of 
 valves should read, 
 
 W = Weight of ram, &c. 
 Page 43. 
 Formula should read, 
 w k'- f m 
 a = — 
 
PART I. 
 
 HIGH PRESSURE HYDRAULIC 
 FITTINGS AND FLANGES. 
 
 (Folly's Patent.) 
 
Description of Tight Joint Hydraulic 
 Fittings and Flanges. 
 
 •' Tight Joint " fittings have established such a reputation 
 for ammonia work, and proved so very satisfactory under the 
 heaviest pressures obtainable, that we have decided to manu- 
 facture a line of Standard High Pressure Hydraulic Fittings 
 and Flanges, making use of the best hydraulic experience of 
 this country and England. 
 
 (1) SECTIONAL CUT OF FITTING. 
 
 The ''Tight Joint" itself will be readily understood from 
 Figure 1 , and the following description : 
 
 The pipe is screwed into the fitting as in the case of ordinary 
 low pressure work, and does not butt against a shoulder. The 
 joint is made by means of a lead collar 1-4 in. wide by 3-16 in. 
 deep, cast in the fitting three or four threads from the end. 
 
 .7 
 
8 
 
 TIGHT JOINTS. 
 
 Holes leading into the recess are tapped for 1-4 in. set screws. 
 one or more set screws being used, according to the size of the 
 fittings. The lead collar is formed on a mandrel of slightly 
 smaller size than the fitting, so that the lead is left projecting 
 a very little beyond the threads. If a pipe be screwed into 
 the fitting it will exj^and the lead packing, causing it to tightly 
 fill the screw threads, and if the joint is not made tight by this 
 means, one or more turns of the compressing screw will crowd 
 the lead around the pipe and make it absolutely and perma 
 nently tight. 
 
 Malleable Iron. 
 
 'TIGHT joint" coupling. 
 
 Having described our system of making screwed joints tight, 
 we will now look into the question of high pressure fittings 
 and compare the old practice of making joints with our own. 
 
 Two methods are adopted in generarpractice, the one de- 
 pends upon screwing the pipe into the fitting so tightly that a 
 leak cannot take place, this necessitates a perfect thread and 
 also that very considerable force be used in screwing the pipe 
 into the fitting, so much being necessary at times that 
 it is no unusual thing to burst a fitting. The second method 
 — a preferable one— is to let the end of the pipe butt against 
 some material, such as leather or copper, and thus make a 
 joint between the two pipes; in this case it is not necessary 
 that tlie pipes be screwed so tightly into the fitting, but to 
 insure a perfect joint under high pressure great care has to 
 be taken in preparing the end of the pipe. In piping up a 
 plant having a number of turns it is necessary that the pipes 
 
TIGHT JOINTS. 9 
 
 shall be cut off absolutely to length; and in the case of 
 flanges, in erection it is even necessary to take down one 
 piece of pipe a number of times to alter the length so that 
 the flange can be sci'ewed around to bring the boltholes in 
 their proper position. 
 
 Those who have had to do with piping up for high pressure 
 will appreciate the difficulties they encounter in erection and 
 will at once see the advantage they will secure from using 
 our type of fittings. 
 
 It will be seen from Figure 1 that in the case of the Tight 
 Joint, as long as the edge of the pipe projects a quarter of an 
 inch beyond the lead collar a perfect joint can be assured, 
 hut the end of the pipe may be carried as much as f of an 
 inch beyond this point. In this way a considerable latitude 
 is possible and erection made very easy. 
 
 As an example of what has been done in this direction with 
 Tight Joints, we would refer to the piping for the High Pres- 
 sure Hydraulic Elevator Systems in the Girard Life Building 
 in Philadelphia and the American Tract Society Building in 
 New York, put in by Otis Brothers Company. In the latter 
 plant several hundred fittings were used, and some idea of 
 the intricacy of the p'ping may be obtained from Figures 3 
 and 4. 
 
txfl 
 
 fcj) 
 
 X 
 
 
 
 Xi 
 
 00 
 
 
 '^ 
 
 3 
 
 o 
 
 CD 
 
 11 
 
 >^ 
 
 
 
 
 a> 
 
 
 
 
 u 
 
 c 
 
 o 
 
 
 CO 
 
 nfl 
 
 
 c 
 
 o 
 
 Q- 
 
 OJ 
 
 Q-h- 
 
 CO 'k- 
 
 ^ E 
 
 .E c 
 o 
 
 bn 
 o 
 ■•-• 
 o 
 
 CL 
 
 10 
 
fe','*^ ' ' A'-^vf^ 
 
 k 
 
 11 
 
12 TIGHT JOINTS. 
 
 On testing these two plants (which carry a working pres- 
 sure of 750 lbs.) not a single leaky joint was found 
 
 A great many experiments have been made with the Tight 
 Joint fittings and everything has been done that was possible 
 to test their efficiency. 
 
 Prof. D. 8. Jacobus, of the Stevens Institute, made a series 
 of tests, and the following are some extracts from his report : 
 
 •• i-incli and | inch Brass Tees — Made to leak and tighten 
 lip at 800 pounds per square tnch steam pressure. 1.700 pounds 
 })er square inch gas pressure, and 8.000 pounds per square 
 inch iieavy refined petroleum oil pressure. 
 
 •• 1 inch Iron Tee, No. 2. — Made to leak and tighten up at 
 5.000 and 10.000 pounds crude petroleum oil pressure nnd 
 5,000 and 10.000 pounds water pressure. Withstood 15,000 
 pounds per square inch crude oil pressure withoiit leakage 
 and 16,000 pounds water pressure. 
 
 "1-inch Brass Hydraulic Tee, No. 2. — Made to leak and 
 tighten up at 5,000 pounds per square inch water pressure." 
 
 From these experiments it will be seen that it is possible by 
 tightening up the small set-screw to compress the lead and to 
 make it flow in such a manner that a leak at five or six thou- 
 sand pounds per square inch can be taken up and a joint made 
 perfectly tight without taking the pressure off the system. 
 
 To sliow^ that expansion and contraction have no effect what- 
 ever upon the joints we would refer to the following report 
 made by Mr. Charles O'Connor, superintendent of the Pratt 
 Works of the Standard Oil Company : 
 
 " I have tested your fitting and find it to be in every sense 
 just as you recommend it. The tests were made in the fol 
 lowing manner: I built a coil of 2-inch pipe, using six (6) of 
 your 2inch Return Bends, making 12 joints. On first test 
 we found that at 800 pounds air pressure (under water) there 
 were two small leaks, and by setting up one or two turns on 
 set-screws they became tight. I was somewhat doubtful as 
 to the joints remaining tight where there would be great ex- 
 pansion and contraction, so I raised coil out of water and 
 turned steam through it at 80 pounds pressure until coil was 
 
TIGHT JOINTS. 
 
 18 
 
 as hot as steam would make it, then I turned off steam, sub- 
 merged coil in cold water and again applied 300 pounds air 
 pressure and found every joint tight." 
 
 That the working of a large hydraulic system during an 
 extended period has no effect upon the joint has been proved 
 by its use in High Pressure Hydraulic Elevators, Hydraulic 
 Riveters, Presses, General Hydraulic Systems, High Pres- 
 sure Steam, 1.500 per a " Air Pressure and a very extended 
 use in all classes of Ammonia Work. 
 
 All fittings and flanges are made of air furnace malleable 
 iron having a tensile strength of from fifty to sixty thousand 
 pownds per square inch. We do not use the so-called 
 malleable iron poured from a cupola, and can thus insure 
 fittings being sound and reMable. 
 
 All fittings are tested by hydraulic pressm^e before leaving 
 the works, as per table on page 3^1. 
 
 (5) 
 
 -f4'"""^^l't^-/i''-H 
 
 'TIGHT JOINT FLANGE UNION5 
 
 The flange unions are furnished complete with bolts and 
 guttapercha rings. Single flanges, either male or female, can 
 be used for connecting to valves or cylinders. The tables of 
 flanges on pages 15 and 16 will furnish the dimensions neces- 
 sary for engineers to design the details of their connections 
 to suit the fittings we carry in stock. 
 
14 TIGHT JOINTS. 
 
 The joint between the flanges is the * Armstrong " standard 
 and made, preferably, witli a round guttapercha ring. This 
 makes the best and most durable joint, though leather or lead 
 can also be used for this purpose. 
 
 Tlie threaded openings of the flange unions are made tight 
 by the use of the " Tiglit Joint ' lead collar and set-screws de- 
 scribed on page 7. Tlie combination of this device vrith the 
 '* Armstrong " flange joint makes an absolutely reliable hy- 
 draulic flange union. 
 
 The foUowiiig tables give the standard sizes of Flanges for 
 750 and 1 500 lbs. per square inch. 
 
TIGHT JOINTS. 
 
 15 
 
 )«5s^- ^-H 
 
 Table of '^ Tight Joint*' Flanges. 
 750 lbs. Working Pressure. 
 
 
 A 
 
 B 
 
 c 
 
 D 
 
 E 
 
 F 
 
 G 
 
 H 
 
 K 
 
 L 
 
 M 
 
 N 
 
 o 
 
 p 
 
 Q 
 
 R 
 
 1 
 
 Size 
 of 
 
 
 oS C8 
 
 ^ 5 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Bolts 
 
 ^ 1 
 
 i 
 
 .84 
 
 H 2i 
 
 ii8i 
 
 li 
 
 If 
 
 1 
 
 1 
 
 H 
 
 A 
 
 li 
 
 i 
 
 4 
 
 lA 
 
 f 
 
 f 
 
 1 
 
 f 
 
 1.05 
 
 H 
 
 2i 
 
 H 
 
 n 
 
 li 
 
 3 
 
 1 
 
 f 
 
 i 
 
 A 
 
 14 
 
 i 
 
 4 
 
 Hf 
 
 1 
 
 1 
 
 1 
 
 1 
 
 1.31 
 
 H 
 
 34 
 
 i 
 
 3 
 
 li 
 
 3i 
 
 14 
 
 1 
 
 f 
 
 i 
 
 If 
 
 i 
 
 1 
 
 Iff 
 
 lA 
 
 i 
 
 1 
 
 U 
 
 1.66 
 
 5i 
 
 3| 
 
 1^ 
 
 34 
 
 If 
 
 3| 
 
 li 
 
 4 
 
 1 
 
 i 
 
 24 
 
 A 
 
 14 
 
 3A 
 
 14 
 
 f 
 
 2 
 
 H 
 
 1.9 
 
 5f 
 
 3i 
 
 1 s 
 
 TV 
 
 3f 
 
 If 
 
 31 
 
 If 
 
 4 
 
 1 
 
 i 
 
 3f 
 
 A 
 
 14 
 
 Oil 
 
 If 
 
 f 
 
 2 
 
 2 
 
 2.37 
 
 7 
 
 4 
 
 1 
 
 5 
 
 2 
 
 31 
 
 14 
 
 i 
 
 1 
 
 i 
 
 3 
 
 5 
 
 14 
 
 2fi 
 
 34 
 
 i 
 
 2 
 
 n 
 
 2.87 
 
 71 
 
 4i 
 
 H 
 
 5f 
 
 3i 
 
 44 
 
 If 
 
 i 
 
 14 
 
 A 
 
 3i 
 
 f 
 
 14 
 
 3A 
 
 24 
 
 1 
 
 2 
 
 8 
 
 3.5 
 
 8^ 
 
 5i H 
 
 6i 
 
 34 
 
 5 
 
 If 
 
 i 
 
 14 
 
 5 
 
 4 
 
 f 
 
 14 
 
 m 
 
 3i 
 
 1 
 
 4 
 
 4 
 
 4.5 
 
 91 
 
 641 A 
 
 n 
 
 3 
 
 5i 
 
 2 
 
 f 
 
 If 
 
 A 
 
 4i 
 
 A 
 
 If 
 
 m 
 
 44 
 
 li 
 
 5 
 
 5 
 
 5.5 
 
 m 
 
 7|1A 
 
 84 
 
 34 
 
 7 
 
 3i 
 
 i 
 
 14 
 
 f 
 
 6 
 
 4 
 
 2 
 
 m 
 
 5i 
 
 It 
 
 6 
 
 
 
 6.62 
 
 m 
 
 9 
 
 Ih 
 
 10 
 
 44 
 
 8 
 
 24 
 
 1 
 
 If 
 
 1 
 
 7 
 
 4 
 
 3i 
 
 6« 
 
 H 
 
 u 
 
 7 
 
16 
 
 TIGHT JOINTS. 
 
 n-y^^- ^-H 
 
 Table of Tight Joint Flanges.— 1 ,500 lbs- Working 
 
 Pressure. 
 
 sis 
 
 A 
 
 B 
 
 c 
 
 D 
 
 E 
 
 F 
 
 G 
 
 H 
 
 K 
 
 L 
 
 M 
 
 N 
 
 o 
 
 p 
 
 Q 
 
 R 
 
 Size 
 of 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 
 Bolts 
 
 =2 2: 
 
 a: 
 
 1 
 
 .67 
 
 3i 
 
 If 
 
 l"k 
 
 2i 
 
 1 
 
 u 
 
 l 
 
 5 
 Iff 
 
 9 
 
 Tii" 
 
 A 
 
 1 
 
 i 
 
 13 
 
 31 
 ¥5 
 
 i 
 
 i 
 
 1 
 
 i 
 
 .84 
 
 31 
 
 H 
 
 ii 
 
 2i 
 
 li 
 
 If 
 
 1 
 
 f 
 
 1 1 
 
 18 
 
 A 
 
 li 
 
 i 
 
 1 
 
 lA 
 
 f 
 
 i 
 
 1 
 
 f 
 
 1.05 
 
 4i 
 
 2i 
 
 ii 
 
 3| 
 
 
 2i 
 
 lA 
 
 A 
 
 f 
 
 i 
 
 u 
 
 i 
 
 1 
 
 HI 
 
 1 
 
 1. 
 
 1 
 
 1 
 
 1.31 
 
 H 
 
 Si 
 
 11 
 
 3i 
 
 If 
 
 3| 
 
 li 
 
 i 
 
 1 
 
 i 
 
 If 
 
 A 
 
 H 
 
 lit 
 
 lA 
 
 f 
 
 1 
 
 H 
 
 1.66 
 
 H 
 
 3i 
 
 H 
 
 3t 
 
 3 
 
 21 
 
 If 
 
 i 
 
 ^ 
 
 i 
 
 2i 
 
 A 
 
 li 
 
 2A 
 
 H 
 
 f 
 
 2 
 
 U 
 
 1.9 
 
 6 
 
 3i 
 
 1 5 
 T6 
 
 4i 
 
 2i 
 
 3i 
 
 H 
 
 i 
 
 1 
 
 i2| 
 
 A 
 
 li 
 
 m 
 
 If 
 
 i 
 
 2 
 
 2 
 
 2.37 
 
 7 
 
 4i 
 
 ItV 
 
 H 
 
 H 
 
 3f 
 
 l| 
 
 f 
 
 H 
 
 i 
 
 3 
 
 f 
 
 U 
 
 m 
 
 2i 
 
 1 
 
 2 
 
 2i 
 
 2.87 
 
 7f 
 
 4f 
 
 lA 
 
 S| 
 
 H 
 
 4i 
 
 3 
 
 1 
 
 li 
 
 A 
 
 3i 
 
 1 
 
 H 
 
 3A 
 
 n 
 
 H 
 
 2 
 
TIGHT JOINTS. 
 
 17 
 
 Sizes Carried in Stock for 750 lbs. Working 
 Pressure. 
 
 COUPLINGS. 
 
 ELBOWS. 
 
 TEES. 
 
 FLANGE 
 UNIONS. 
 
 REDUCING 
 BUSHINGS. 
 
 i 
 
 i 
 
 i 
 
 
 
 i 
 
 f 
 
 1- 
 
 f 
 
 — 
 
 f 
 
 i 
 
 i 
 
 i 
 
 i 
 
 i 
 
 i 
 
 1 
 
 f 
 
 f 
 
 i 
 
 1 
 
 1 
 
 1 
 
 1 
 
 1 
 
 H 
 
 li 
 
 li 
 
 li 
 
 U 
 
 U 
 
 H 
 
 li 
 
 u 
 
 H 
 
 3 
 
 2 
 
 2 
 
 2 
 
 2 
 
 2k 
 
 2^ 
 
 2^ ■ 
 
 2^ 
 
 3i 
 
 3 
 
 B 
 
 3 
 
 3 
 
 3 
 
 4 
 
 4, 
 
 4 
 
 4 
 
 4 
 
 5 
 
 5 
 
 5 
 
 5 
 
 5 
 
 6 
 
 6 
 
 6 
 
 6 
 
 6 
 
 Sizes Carried in Stock for 1,500 lbs. Working 
 Pressure. 
 
 COUPLINGS. 
 
 ELBOWS. 
 
 TEES. 
 
 FLANGE 
 
 UNIONS. 
 
 REDUCING 
 BUSHINGS. 
 
 i 
 
 i 
 
 i 
 
 — 
 
 i 
 
 f 
 
 f 
 
 t 
 
 f 
 
 * 
 
 * 
 
 i 
 
 i 
 
 i 
 
 i 
 
 f 
 
 f . 
 
 f 
 
 i 
 
 i ■ 
 
 1 
 
 I 
 
 1 
 
 1 
 
 1 
 
 li 
 
 li 
 
 U 
 
 U 
 
 li 
 
 n 
 
 U 
 
 U 
 
 U 
 
 U 
 
 3 
 
 3 
 
 2 
 
 2 
 
 3 
 
 n 
 
 2* 
 
 . ' n 
 
 2i 
 
 n 
 
18 
 
 TIGHT JOINTS. 
 
 Sizes Carried in Stock for 3,000 lbs. Working 
 Pressure. 
 
 COUPLINGS. 
 
 ELBOWS. 
 i 
 
 TEES. 
 
 FLANCJE 
 UNIONS. 
 
 REDUCING 
 BUSHINGS. 
 
 i 
 
 1 
 4 
 
 i 
 
 i 
 
 1 
 
 1 
 
 1 
 
 ■ 1 
 
 S 
 
 i 
 
 i 
 
 i 
 
 i 
 
 i 
 
 i 
 
 i 
 
 f 
 
 f 
 
 f 
 
 1 
 
 1 
 
 1 
 
 1 
 
 1 
 
 n 
 
 U 
 
 H 
 
 H 
 
 li 
 
 u 
 
 U 
 
 U 
 
 n 
 
 u 
 
 2 
 
 2 
 
 2 
 
 — 
 
 2 
 
 2* 
 
 n 
 
 2i 
 
 — 
 
 - 3i 
 
 4 
 
 4 
 
 4 
 
 — 
 
 4 
 
 
 6 
 
 6 
 
 — 
 
 6 
 
 Sizes Carried in Stock for 6,000 lbs. Working 
 Pressure. 
 
 COUPLINGS. 
 
 ELBOWS. 
 
 TEES. 
 
 FLANGE 
 UNIONS. 
 
 REDUCING 
 BUSHINGS. 
 
 i 
 
 i 
 
 4 
 
 1. 
 4 
 
 i 
 
 f 
 
 t 
 
 1 
 
 f 
 
 t. 
 
 i 
 
 i 
 
 • i 
 
 ^ 
 
 i 
 
 * 
 
 f 
 
 f 
 
 f 
 
 f . 
 
 1 
 
 1 
 
 1 
 
 1 
 
 1 
 
 U 
 
 li 
 
 li 
 
 li 
 
 H 
 
 li 
 
 H 
 
 H 
 
 n 
 
 H 
 
TIGHT JOINTS. 19 
 
 The Reducing Bushings have the lead collar and set-screws 
 the same as our regular fittings and can be supplied to meet 
 any desired changes in size . 
 
 The Flange Unions are in pairs (male and female) furnished 
 complete with bolts and pure guttapercha rings. 
 
 We can make to order Flanges and Fittings to stand any 
 desired pressure. 
 
I 
 
 PART 11. 
 
 INFORMATION 
 
 FOR USE 
 
 IN DESIGNING HYDRAULIC PLANTS. 
 
 COMPILED BY 
 
 JOHN PLATT, Member of the American Societ}^ of Mechanical Engineers, 
 Assoc M. Inst. C. K. 
 
INTRODUCTION. 
 
 The following tables, formulae and general information have 
 been compiled in the hope that they will be found of use by 
 those who use hydraulic fittings and have to deal with the 
 general question of hydraulic pressure transmission. 
 
 The tables of wrought iron and steel pipe are for standard 
 sizes. We have given at the head of each table pressures for 
 v^hich the various thicknesses of pipe can be used. The 
 makers, as a general rule, will not guarantee their pipe for 
 any pressure, but pipe of a good quality from a reliable maker 
 will be found to be perfectly good for the pressures stated. 
 
 With regard to formula for thickness of hydraulic cylinders, 
 considerable discretion is necessary when using any formula 
 for thick, cylinders, and unl6ss those attempting to use such 
 formula have considerable shop experience, we would recom- 
 mend the taking of the thickness from the table used by Sir 
 W. G. Armstrong. 
 

 HYDRAULIC DATA. 
 
 25 
 
 Circumferences, Areas, Squares, Etc., 
 
 Advancing by Decimals — .1 to 9.8. 
 
 Diameter. 
 
 Circum- 
 ference . 
 
 Area. 
 
 Square. 
 
 Cube. 
 
 Square 
 Koot. 
 
 Cube 
 Root. 
 
 .1 
 
 .814 
 
 .00785 
 
 .01 
 
 .001 
 
 .816 
 
 .464 
 
 .2 
 
 .628 
 
 .0814 
 
 
 04 
 
 
 008 
 
 
 447 
 
 
 585 
 
 .8 
 
 .942 
 
 .0706 
 
 
 09 
 
 
 027 
 
 
 548 
 
 
 669 
 
 A 
 
 1.26 
 
 .1256 
 
 
 16 
 
 
 064 
 
 
 688 
 
 
 787 
 
 .5 
 
 1.57 
 
 .1968 
 
 
 25 
 
 
 125 
 
 
 707 
 
 
 794 
 
 .0 
 
 1.88 
 
 .2827 
 
 
 36 
 
 
 216 
 
 
 775 
 
 
 843 
 
 .7 
 
 2.20 
 
 .8848 
 
 
 49 
 
 
 848 
 
 
 887 
 
 
 888 
 
 .8 
 
 2.51 
 
 .5026 
 
 
 64 
 
 
 512 
 
 
 894 
 
 
 928 
 
 .9 
 
 2.83 
 
 .6862 
 
 
 81 
 
 
 729 
 
 
 949 
 
 
 965 
 
 1. 
 
 8.14 
 
 .7854 
 
 1 
 
 
 1 
 
 
 
 
 
 
 .1 
 
 8.46 
 
 .9508 
 
 1 
 
 21 
 
 1 
 
 33 
 
 
 049 
 
 
 082 
 
 .2 
 
 8.77 
 
 1.181 
 
 1 
 
 44 
 
 1 
 
 73 
 
 
 095 
 
 
 063 
 
 .8 
 
 4.08 
 
 1.827 
 
 1 
 
 69 
 
 2 
 
 20 
 
 
 140 
 
 
 091 
 
 .4 
 
 4.39 
 
 1.539 
 
 1 
 
 96 
 
 2 
 
 74 
 
 
 188 
 
 
 119 
 
 .5 
 
 4.71 
 
 1.767 
 
 2 
 
 25 
 
 3 
 
 37 
 
 
 225 
 
 
 145 
 
 .6 
 
 5.02 
 
 2.011 
 
 2 
 
 56 
 
 4 
 
 10 
 
 
 265 
 
 
 170 
 
 .7 
 
 5.34 
 
 2.270 
 
 2 
 
 89 
 
 4 
 
 91 
 
 
 304 
 
 
 193 
 
 .8 
 
 5.65 
 
 2.545 
 
 8 
 
 24 
 
 5 
 
 83 
 
 
 342 
 
 
 216 
 
 .9 
 
 5.96 
 
 2.835 
 
 8 
 
 61 
 
 6 
 
 86 
 
 
 378 
 
 
 289 
 
 2. 
 
 6.28 
 
 3.142 
 
 4 
 
 
 8 
 
 
 
 414 
 
 
 260 
 
 .1 
 
 6.59 
 
 3.464 
 
 4 
 
 41 
 
 9 
 
 26 
 
 
 449 
 
 
 281 
 
 .2 
 
 6.91 
 
 3 801 
 
 4 
 
 84 
 
 10 
 
 65 
 
 
 483 
 
 
 301 
 
 .3 
 
 7.22 
 
 4.155 
 
 5 
 
 29 
 
 12 
 
 17 
 
 
 517 
 
 
 820 
 
 .4 
 
 7.53 
 
 4.524 
 
 5 
 
 76 
 
 13 
 
 82 
 
 
 549 
 
 
 339 
 
 .5 
 
 7.85 
 
 4.909 
 
 6 
 
 25 
 
 15 
 
 63 
 
 
 581 
 
 
 357 
 
 .6 
 
 8.16 
 
 5.309 
 
 6 
 
 76 
 
 17 
 
 58 
 
 
 612 
 
 
 375 
 
 .7 
 
 8.48 
 
 5.726 
 
 7 
 
 29 
 
 19 
 
 68 
 
 
 643 
 
 
 392 
 
 .8 
 
 8.79 
 
 6.158 
 
 i 
 
 84 
 
 21 
 
 1]5 
 
 
 673 
 
 
 409 
 
 .9 
 
 9.11 
 
 6.605 
 
 8 
 
 41 
 
 24 
 
 .89 
 
 
 708 
 
 
 426 
 
 3. 
 
 9.42 
 
 7.069 
 
 9 
 
 
 27 
 
 
 
 732 
 
 
 442 
 
 .2 
 
 10.05 
 
 7.548 
 
 ' 10 
 
 "24 
 
 32 
 
 "77 
 
 
 789 
 
 i \ 
 
 474 
 
 .4 
 
 10.68 
 
 8.558 
 
 i M 
 
 i 
 
 '.56 
 
 39 
 
 ; 30 
 
 
 .844 
 
 1 1 
 
 '.504 
 
26 
 
 HYDRAULIC DATA. 
 
 Circumferences, Areas, Squares, Etc., 
 Advancing by Decimals. .1 to 9.S. — Continued. 
 
 Diameter. 
 
 Circum- 
 ference. 
 
 Area. 
 
 Square. 
 
 Cube. 
 
 Square 
 Root. 
 
 Cube 
 Root. 
 
 8 6 
 
 11.80 
 
 10.18 
 
 12.96 
 
 46.66 
 
 1.897 
 
 1.588 
 
 
 8 
 
 11.98 
 
 11 
 
 84 
 
 14 
 
 44 
 
 54 
 
 87 
 
 1 . 949 
 
 
 560 
 
 4 
 
 
 12.56 
 
 12 
 
 57 
 
 16 
 
 
 64 
 
 
 2 
 
 
 587 
 
 
 2 
 
 18.19 
 
 18 
 
 85 
 
 17 
 
 64 
 
 74 
 
 09 
 
 2.049 
 
 
 618 
 
 
 4 
 
 18.82 
 
 15 
 
 21 
 
 19 
 
 86 
 
 85 
 
 18 
 
 2.098 
 
 
 689 
 
 
 6 
 
 14.45 
 
 16 
 
 62 
 
 21 
 
 16 
 
 97 
 
 84 
 
 2.145 
 
 
 668 
 
 
 8 
 
 15.08 
 
 18 
 
 10 
 
 28 
 
 04 
 
 110 
 
 6 
 
 2.191 
 
 
 687 
 
 5 
 
 
 15.70 
 
 19 
 
 68 
 
 25 
 
 
 125 
 
 
 2.286 
 
 
 710 
 
 
 2 
 
 16.88 
 
 21 
 
 24 
 
 27 
 
 04 
 
 140 
 
 6 
 
 2 280 
 
 
 782 
 
 
 4 
 
 16.96 
 
 22 
 
 90 
 
 29 
 
 16 
 
 157 
 
 5 
 
 2.824 
 
 
 754 
 
 
 6 
 
 17.59 
 
 24 
 
 68 
 
 81 
 
 86 
 
 175 
 
 6 
 
 2.866 
 
 
 776 
 
 
 8 
 
 18 22 
 
 26 
 
 42 
 
 88 
 
 64 
 
 195 
 
 1 
 
 2.408 
 
 
 797 
 
 6 
 
 
 18.84 
 
 28 
 
 27 
 
 86 
 
 
 216 
 
 
 2.449 
 
 
 817 
 
 
 2 
 
 19.47 
 
 80 
 
 19 
 
 88 
 
 44 
 
 28S 
 
 8 
 
 2 490 
 
 
 887 
 
 
 4 
 
 20 10 
 
 82 
 
 17 
 
 40 
 
 96 
 
 262 
 
 1 
 
 2.580 
 
 
 857 
 
 
 6 
 
 20.78 
 
 84 
 
 21 
 
 48 
 
 56 
 
 287 
 
 5 • 
 
 2 569 
 
 
 876 
 
 
 8 
 
 21 86 
 
 86 
 
 82 
 
 46 
 
 24 
 
 814 
 
 4 
 
 2 608 
 
 
 895 
 
 7 
 
 
 21 99 
 
 88 
 
 48 
 
 49 
 
 ^ 
 
 84*8 
 
 
 2 646 
 
 
 918- 
 
 
 2 
 
 22 61 
 
 40 
 
 72 
 
 51 
 
 84 
 
 878 
 
 2 
 
 2 688 
 
 
 981 
 
 
 4 
 
 28 24 
 
 48 
 
 01 
 
 54 
 
 76 
 
 405 
 
 2 
 
 ' 2 720 
 
 
 949 
 
 
 6 
 
 28 87 
 
 45 
 
 86 
 
 57 
 
 76 
 
 489 
 
 
 2 757 
 
 
 966 
 
 
 8 
 
 24 50 
 
 47 
 
 78 
 
 60 
 
 84 
 
 474 
 
 6 
 
 2 798 
 
 
 988 
 
 8 
 
 
 25 18 
 
 50 
 
 27 
 
 64 
 
 
 512 
 
 
 2 828 
 
 2 
 
 
 
 2 
 
 25 76 
 
 52 
 
 81 
 
 67 
 
 24 
 
 551 
 
 4 
 
 2 864 
 
 2 
 
 017 
 
 
 4 
 
 26 88 
 
 55 
 
 42 
 
 70 
 
 56 
 
 592 
 
 t 
 
 2 898 
 
 2 
 
 088 
 
 
 6 
 
 27 01 
 
 58 
 
 09 
 
 78 
 
 96 
 
 686 
 
 1 
 
 2 988 
 
 2 
 
 049 
 
 
 8 
 
 27*64 
 
 60 
 
 82 
 
 77 
 
 44 
 
 681 
 
 5 
 
 2 966 
 
 2 
 
 065 
 
 9 
 
 
 28*27 
 
 68 
 
 62 
 
 81 
 
 
 729 
 
 
 8 
 
 2 
 
 080 
 
 
 2 
 
 28*90 
 
 66 
 
 48 
 
 84 
 
 64 
 
 778 
 
 i 
 
 8 088 
 
 2 
 
 095 
 
 
 4 
 
 29*58 
 
 69 
 
 40 
 
 88 
 
 86 
 
 880 
 
 6 
 
 8 066 
 
 2 
 
 110 
 
 
 6 
 
 80 15 
 
 72 
 
 88 
 
 92 
 
 16 
 
 884 
 
 t 
 
 8 098 
 
 2 
 
 125 
 
 
 8 
 
 80/78 
 
 75 
 
 48 
 
 96 
 
 04 
 
 941 
 
 2 
 
 8! 180 
 
 2 
 
 140 
 
HYDRAULIC DATA. 
 
 27 
 
 
 Q 
 
 
 
 52; 
 
 
 
 i-H 
 
 
 
 H 
 
 
 
 « 
 
 
 
 <!\ 
 
 
 <D 
 
 a 
 
 
 
 I— 1 
 m 
 
 U4 
 
 ^ 
 
 ^ 
 
 
 H 
 
 H 
 
 m^ 
 
 p^ 
 
 g 
 
 
 
 
 
 <1) 
 
 05 
 
 ■ Q 
 
 C/) 
 
 3 
 
 
 
 
 
 '^ 
 
 
 
 
 
 -o 
 
 CO 
 
 m 
 
 c 
 
 OS 
 
 
 
 H 
 
 
 c 
 
 t^ 
 
 w 
 
 
 
 05 
 
 
 L. 
 
 
 
 ■4-> 
 
 t^ 
 
 ^ 
 
 x: 
 
 (/I 
 
 H 
 
 bfi 
 
 H 
 
 W 
 
 T 
 
 ;? 
 
 fe 
 
 
 
 Ph 
 
 
 
 L. 
 
 ct 
 
 H 
 
 i? 
 
 iz; 
 
 
 
 W 
 
 ^ 
 
 
 (i5 
 
 H 
 
 
 
 
 
 
 ^ 
 
 
 
 « 
 
 
 
 
 
 
 
 ^ 
 
 
 Contents of 
 
 ooe foot 
 in length. 
 
 c 
 
 
 
 
 
 10 Oi-iO ^-^lOlO(^Dooco^ 
 5Sir'^^f^ot--*QOocoo 
 
 OOOOOOtHtHCQcOCOOIC 
 
 T— ( 1—1 
 
 No. of 
 
 Threads 
 
 per inch 
 
 of screw. 
 
 
 QO^X)'^T^'^T-lrHTHrHaOX)QOX) 
 
 Nominal 
 
 weight 
 
 per foot 
 
 of length. 
 
 a 
 
 
 Ph 
 
 ^ 10 00 ri CO CQ :o t- IC O iO t- 
 
 tH ^ c^:j o.-? CO ic t- ^ 00 
 
 T-H r-l T-H 
 
 P ce 
 
 02 
 
 a 
 
 a 
 
 in 
 
 OOiOCOOOiCOiOOOOOCOOSQO 
 ^THCOiOOO^OCOt-COt-OiOO 
 
 tH GQ CO ^ L- CQ Oi 00 
 T— 1 1— 1 GQ 
 
 ^ 'Jl 
 
 «3 
 
 a 
 
 00 oi T-H CO ^ -* 10 ^ CO 10 00 
 
 tH T-i tH T-H tH T-l CQ CQ O:? 0^ C^"i 
 
 
 Actual 
 
 Outside 
 
 Diam. 
 
 c 
 
 '^ r- 'xt^ JO th r^ t- <© 0^ 
 
 iOCOOOOCOOOiCOOOiOlOlOCD 
 
 rHrH^T-HCQOlCO-T^iOCO 
 
 l5a 
 
 a 
 
 <:d Oi 0^ GQ -vH 00 T-H CD G^i TiH ?o 
 CO^COOOOCOOO^OOOO 
 
 ^ rH tH CQ C^-? 0? --t- iO 
 
 Noniinal 
 Inside 
 Diam. 
 
 CO 
 
 
 
 -Hir*. :ct» He' mH< H^ ^^' '-+^' 
 
 rH rH T-H 0? 0> CO -+ J.O CO 
 
28 
 
 HYDRAULIC DATA. 
 
 
 
 (D 
 
 C 
 
 o 
 
 O 
 
 i. 
 
 bfi 
 c 
 o 
 
 (/) 
 
 X 
 
 o 
 
 CO ^, 
 
 -a 
 
 c 
 
 o 
 o 
 
 c 
 
 H 
 
 a. 
 
 ;^ 
 
 g 
 
 5 
 
 o 
 
 o 
 
 o 
 
 t— I 
 
 H 
 X 
 
 o 
 
 c 
 c 
 
 o 
 
 o 
 
 
 Pi 
 C 
 
 
 o o ^ c^> r: :c; c: i^'T — ' ^ 05 T*< cC' 
 
 O 
 
 ^|2 
 
 eg 
 
 ■s|s" 
 
 ^ 
 
 
 
 
 
 '"^ '^ Oi CC i- O W CQ ^- t:t t- rfH X 
 
 fl 
 
 iOi>OLT^OOO:CC^:»Ciii«)0 
 
 
 
 
 ^'i^ 
 
 P 
 
 ^ ^ c:j :c cc ici- o T*< o x> 
 
 ^.^^10^ 
 
 ■^T— fC^'^^CrHXL'^ 
 
 IC ^ X o ^ :c O 10 X O IC iC cc 
 
 • ^' rH tH r-I O^' CQ CO T^* iC 5C 
 
 05<M'^eci'ri^-ciC0'-^05T-^t-LT 
 
 Ci '^^ LO t- C: ^7^1 T:^ C5 so X X X L- 
 
 T-(' T-( 1-i c<i (m' CO* -Ti^ ic 
 
 ^T-rHCQC^COrJ^LOX;- 
 
HYDRAULIC DATA. 
 
 29 
 
 o 
 
 
 
 a 
 
 w 
 
 
 a 
 
 
 
 
 
 
 <i) 
 
 H 
 
 
 4-> 
 
 < 
 
 
 CO • 
 
 P 
 
 
 Ti 
 
 CC 
 
 o 
 
 
 Ph 
 
 
 c 
 
 cc 
 
 g 
 
 o 
 
 pq 
 
 
 
 V. 
 
 ^ 
 
 Q 
 
 ■T" 
 
 o 
 
 ^ 
 
 4-> 
 
 o 
 
 <; 
 
 
 »o 
 
 
 3 
 
 o 
 
 Eh 
 
 h-l 
 
 o 
 
 5 
 
 Ah 
 
 J/: 
 
 02 
 
 < 
 
 c 
 
 O 
 
 ^ 
 » 
 
 
 (0 
 
 Ph 
 
 C 
 
 cd 
 
 
 PQ 
 
 1. 
 
 4-> 
 
 w 
 
 CD 
 
 o 
 
 H 
 
 JD 
 
 o 
 
 
 3 
 
 ^ 
 
 
 O 
 
 
 
 Q 
 
 
 
 o o <^ ^ 
 
 O 
 
 C^CiCO'^rHQOOlCCQT-IOS 
 
 OOO^CO^OOlrHOCQ-^ 
 
 OOOOOOOtHC^^<;00 
 
 Nominal 
 weig^ht 
 
 per foot of 
 length. 
 
 
 COOOOOIOOOOOOOO 
 05 IC CC -^^ O ^_ -* CO L- t- r-^ T-^ 
 
 ' ^oicO iO O Ci CO t-' 'rt^ t- S 
 T-H 1-1 C.J CO lO 
 
 t— 1 
 
 c/1 
 
 -^^COt-^CO^THCiO-iCOO 
 
 tH CQ ^ i> C^i O 
 
 
 CO 
 
 o 
 
 C^-) C5 — • O GO O ^ CO O 00 IC X 
 O? O^ CO CO CO ^ ^ lO CO CO t- t- 
 
 
 ill 
 
 
 
 t- ^ lO ^ CO t- t- O O CO C^i 
 CO 00 O CO CO 05 CO 00 lO lO iO CO 
 
 * T-I tH tH i-I C'? CQ CO* tJH IC CO' 
 
 Actual 
 Inside 
 Diam. 
 
 
 00-^O)X00Q0CilO00COCOCO 
 0"i C^ -^ lO '00 O ^_ t- G<i tH O O 
 
 ' ^ r-^ ^ cico ^ iri 
 
 
 i 
 ■g 
 
 c 
 
 t-H 
 
 tH T-H rH C^^ (7) CO ^ »C CO 
 
30 HYDRAULIC DATA 
 
 Table of Tensile Strength in Pounds, 
 Per Square Inch. 
 
 Metals and Alloys. 
 
 Brass, Cast .^ Average 18,000 
 
 Bronze, or Gun Metal 36,000 t6 50.000 
 
 Copper, Cast Average 19,000 
 
 Bolts '' 36.000 
 
 Iron. Cast. 13.500 to 29.000 " 16.500 
 
 '• Malleable (Air furnace) 35.000 to 55.000 
 
 '' Wrought 46,000 to 56,000 
 
 Steel. Cast 65,000 to 85.000 
 
 •• Crucible 90,000 to 120,000 
 
 '' Rivet . .55,000 to 65,000 
 
 •• Bessemer Bar 65,000 to 90.000 
 
 Malleable iron should always be poured from the air 
 furnace and made from white charcoal iron'(Nos. 3 to 5) and 
 then annealed from ten to twenty days. This material can 
 be used for hydraulic fittings, valves, etc., and has the tenac- 
 ity given above. The so-called malleable iron, poured from 
 a cupola and made of gray iron and annealed from five to ten 
 days, has a tenacity of from 20.000 to 32,000 lbs. per square 
 inch, and should not be used for hydraulic or machine work 
 
HYDRAULIC DATA. 
 
 81 
 
 Safe Loads for Bolts. 
 
 Stress, 10,000 pounds per Square inch for Steel. 
 7.000 •• - '^ •• - Iron. 
 
 Diameter, 
 
 Area at 
 
 Bottom 
 
 of Thread. 
 
 Safe load in 
 Sieel, 
 
 Safe load in 
 Iron. 
 
 No, of 
 Threads 
 per Inch. 
 
 i 
 
 .126 
 
 1.260 
 
 .882 
 
 18 
 
 t 
 
 .2i'2 
 
 2.020 
 
 1.414 
 
 11 
 
 f 
 
 .80 
 
 8.000 
 
 2 . 100 
 
 10 
 
 i 
 
 .42 
 
 4.200 
 
 2.940 
 
 9 
 
 1. 
 
 .55 
 
 5.500 
 
 8 . 850 
 
 8 
 
 H 
 
 .69 
 
 6.900 
 
 4.880 
 
 7 
 
 H 
 
 .89 
 
 8.900 
 
 6.280 
 
 7 
 
 If 
 
 l.oc, 
 
 10.600 
 
 7.420 
 
 6 
 
 n 
 
 1.29 
 
 12.900 
 
 9.080 
 
 6 
 
 n 
 
 1.51 
 
 15 100 
 
 10.570 
 
 H 
 
 If 
 
 1.75 
 
 17 . 500 
 
 12.150 
 
 5 
 
 n 
 
 2.05 
 
 20.500 
 
 14.850 
 
 5 
 
 2 
 
 2.80 
 
 28 . 000 
 
 16.100 
 
 4^ 
 
 H 
 
 8.02 
 
 80.200 
 
 21.140 
 
 4^ 
 
 H 
 
 8.72 
 
 87.200 
 
 26.040 
 
 4 
 
 The Size of Bolt Heads and Nuts. 
 
 Diameter of bolt = 1 . 
 
 Diameter of head and nut, square or hexagon = Iffrom 
 side to side. 
 
 Diameter of head and nut. hexagon = 2, over angles. 
 Thickness of head = f of diameter of bolt. 
 Thickness of nut = diameter of bolt. 
 
HYDRAULIC MEMORANDA. 
 
 A cubic foot of water contains 7.480519 gallons. 
 
 A gallon of water contains 231 cubic inches, and weighs 
 8.83111 pounds. (U. S. Standard. ) 
 
 Tlie friction of water in pipes is as the square of the ve- 
 locity. 
 
 The height of a column of fresh water, equal to a pressure 
 of one pound per square inch, is 2.31 feet. (In usual compu- 
 tation this is taken at 2 feet, thus allowing for ordinary fric- 
 tion . ) 
 
 The mean pressure of the atmosphere is estimated at 14.7 
 pounds per square inch, so that with a perfect vacuum it will 
 sustain a column of water 33.9 feet high. 
 
 To find the pressure in pounds, per square inch, of a column 
 of water, multiply the height of the column in feet by .434 — 
 Approximately we say that every foot elevation is equal to 
 one-half pound pressure per square inch; this allows for ordi- 
 nary friction. 
 
 In designing hydraulic machinery, a rule should be made 
 that in all cases a leather shall work against brass or hydrau- 
 lic bronze, and never against cast iron. Hemp packing 
 should always be used to work against iron, and not come in 
 contact with brass. Hemp packing and stuffing boxes can 
 readily be used, with a working pressure of 1500 lbs. per sq. in. ; 
 and by the use of Du Val metallic packing in a stuffing box, 
 with pressures as high as 5,000 lbs. per sq. in. 
 
HYDRAULIC MEMORANDA. 
 
 m 
 
 Working and Test Pressures. 
 
 Working Pressure. Test Pressure. 
 
 400 lbs . per sq. in 1 ,^50 lbs. per sq. in . 
 
 750 '^ - " 2,000 " " 
 
 1,500 '• " " 3,500 •• •' 
 
 3,000 '• •' " 5,000 •' '• 
 
 5,000 '• '' - 7,500 '• '^ 
 
 In good practice it is always well to test the parts of all 
 hydraulic machines, etc. , working at a given pressure, to the 
 corresponding test pressure given in the table above. 
 
 Table of Gallons. 
 
 United States. 
 New York. . . . 
 Imperial 
 
 Cubic 
 
 Inches in a 
 
 Gallon. 
 
 231. 
 
 221.81918 
 
 Weight of 
 a Gallon 
 
 in Pounds 
 Avoirdu- 
 pois. 
 
 8.33111 
 8.00 
 10.00 
 
 Gallons in 
 
 a Cubic 
 
 Foot. 
 
 7.480519 
 7.901285 
 6.232102 
 
 Weight of a 
 cubic foot 
 of water, 
 English 
 standard, 
 62 . 3210286 
 lbs . Avoir- 
 dupois. 
 
 Useful N 
 
 lumbers 
 
 >■ 
 
 
 Cubic Inches 
 
 X by 
 
 .00058 
 
 =: 
 
 Cubic Feet 
 
 Circular Inches 
 
 X ' 
 
 .00546 
 
 =z 
 
 Square Feet 
 
 Cubic Feet 
 
 X - 
 
 7.48 
 
 = 
 
 U. S. Gallons 
 
 Cubic Inches 
 
 X 
 
 .004329 
 
 zzz 
 
 U. S. Gallons 
 
 Cylindrical Inches 
 
 X 
 
 .0034 
 
 = 
 
 U. S. Gallons 
 
 U. S. Gallons 
 
 X 
 
 .13367 
 
 — 
 
 Cubic Feet 
 
 Cylin. Ft. of Water 
 
 X 
 
 6. 
 
 = 
 
 U. S. Gallons 
 
 Cubic Ft. of Water 
 
 X - 
 
 62.5 
 
 = 
 
 Pounds Avoirdu 
 
 Cu. In. of Water 
 
 X 
 
 .03617 
 
 = 
 
 " " [pois 
 
 Cylin. In. of Water 
 
 X 
 
 .02842 
 
 = 
 
 .. 
 
 268.8 U. S. Gallons of water 
 
 
 — 
 
 One Ton 
 
 35.88 Cu. Ft. of Water 
 
 
 =: 
 
 One Ton 
 
84 HYDRAULIC MEMORANDA. 
 
 Thickness of Hydraulic Cylinders.— (Formulae.) 
 
 Merriman gives the following : 
 
 s = allowable maximum stress in metal . 
 
 p z= pressure in same units. 
 
 R — outside radius. r p 
 
 r = interior radius . t = •■ — 
 
 t = thickness. s — p 
 
 Rankine gives : 
 
 ^s + p 
 
 R - ^ X r 
 
 s — p 
 
 The foregoing formulae apply only to ''thick cylinders," 
 and must be used with discretion, as will be seen from tlie 
 particulars given below. 
 
 To bring these formulae within practical limits at all, the 
 allowable maximum stress, "s," should not be taken at more 
 than 4,000 lbs. per n' for the comparatively low values of 
 "p," which gives "t" a value that will not make a "thick" 
 cylinder. 
 
 From a table used by Sir W. G. Armstrong, the following 
 thicknesses for cast-iron cylinders for a working pressure of 
 1,000 lbs. per a " are taken, and these can be relied on for 
 practical work: 
 
 Diam. of Cylinder, Inches, 2 3 4 5 6 7 
 Thickness of " " 0.832, 1.042, 1.146, 1.354, 1.552, 1.77, 
 
 Diam. of Cylinder, Inches, 8 9 10 11 12 13 
 Thickness of " " 1 . 875, 1 . 979, 2 . 02, 2 . 34, 2 . 578, 2 . 734, 
 
 Diam, of Cylinder, Inches, 14 15 16 17 18 19 
 Thickness of " " 2.89,3.046,3.19,3.32, 3.45, 3.58, 
 
 Diam. of Cylinder, Inches, 20 21 22 23 24 
 Thickness of '* " 3.697,3.802,3.906,4.01,4.114 
 
HYDRAULIC MEMORANDA. 35 
 
 For any other pressures, multiply by the ratio of that pres- 
 sure to 1,000. 
 
 Mr. Wm. Kent says: "These figures correspond nearly to 
 the formula t — 0.175 d + 0.48, in which t = thickness, 
 and d = diameter in inches up to 16 " diameter, but for 20 
 inches diameter, the addition of 0.48 is reduced to 0.19, 
 and at 24" it disappears." 
 
 Cast-iron should not be used for pressures exceeding 
 2,000 lbs. per d ', and it is better to use steel castings or 
 forged steel for cylinders which would be over 6" thick in 
 cast iron. 
 
36 HYDRAULir MEMORANDA. 
 
 Capacities of Cylinders and Rams. 
 
 Diameter. 
 
 
 Load at 
 
 C'ubic Ids. 
 
 (lallons 
 
 Gallons 
 
 
 Area. 
 
 1,500 lbs. 1 " 
 
 per Foot 
 
 per Foot 
 
 per Incii 
 
 Inches. 
 
 . 7854 
 
 in lbs. 
 
 of Cylinder 
 
 of Cylinder. 
 .040 
 
 of Cylinder. 
 
 1 
 
 1,178 
 
 9.42 
 
 .0038 
 
 H 
 
 .904^ 
 
 1,491 
 
 11.93 
 
 .051 
 
 .0042 
 
 H 
 
 1.227 
 
 1,840 
 
 14.72 
 
 .063 
 
 .0052 
 
 If 
 
 1.484 
 
 2,227 
 
 17.8 
 
 .077 
 
 . 0064 
 
 H 
 
 1.707 
 
 2,650 
 
 21.20 
 
 .091 
 
 .0076 
 
 U 
 
 2.078 
 
 3,110 
 
 24.87 
 
 .107 
 
 .0089 
 
 If 
 
 2.^05 
 
 3,607 
 
 28.86 
 
 .124 
 
 .0108 
 
 u 
 
 4,140 
 
 33.18 
 
 .143 
 
 .0119 
 
 3 
 
 8.141 
 
 4,711 
 
 37.69 
 
 .163 
 
 .0186 
 
 n 
 
 3.546 
 
 5,319 
 
 42.55 
 
 .184 
 
 .0158 
 
 n 
 
 3.976 
 
 5,964 
 
 47.71 
 
 .206 
 
 . .0171 
 
 n 
 
 4.430 
 
 6,645 
 
 53.16 
 
 .280 
 
 .0191 
 
 n 
 
 4.908 
 
 7,862 
 
 58.90 ■ 
 
 .254 
 
 .0211 
 
 H 
 
 5.411 
 
 8,116 
 
 64.98 
 
 .281 
 
 .0234 
 
 2f 
 
 5.939 
 
 8,908 
 
 71.26 
 
 .308 
 
 .0257 
 
 2* 
 
 6.491 
 
 9.786 
 
 77.89 
 
 . .887 
 
 .0281 
 
 a 
 
 7.068 
 
 10,602 
 
 84.81 
 
 . 367 
 
 .0306 
 
 H 
 
 8.295 
 
 12442 
 
 99.5.4 
 
 .430 
 
 .0858 
 
 ■n 
 
 9.621 
 
 14,481 
 
 115.45 
 
 .50 
 
 .0416 
 
 n 
 
 11.04 
 
 16.560 
 
 183.48 
 
 .573 
 
 . 0477 
 
 4 
 
 12.56 
 
 18,840 
 
 150.72 
 
 '652 
 
 .0543 
 
 H 
 
 14.18 
 
 21.270 
 
 169.92 
 
 .785 
 
 .0612 
 
 H 
 
 15.90 
 
 23.850 
 
 190.80 
 
 .826 
 
 .0688 
 
 4f 
 
 17.72 
 
 26,580 
 
 212.64 
 
 .920 
 
 .0767 
 
 5 
 
 19.68 
 
 29,445 
 
 285.56 
 
 1.02 
 
 .0850 
 
 H 
 
 21.64 
 
 32,460 
 
 259.68 
 
 1.124 
 
 .0936 
 
 5+ 
 
 28.75 
 
 35,625 
 
 285.0 
 
 1.28 
 
 . 1025 
 
 .">* 
 
 25.96 
 
 38,940 
 
 811.52 
 
 1.348 
 
 .1123 
 
 6 
 
 88.27 
 
 42,405 
 
 339.24 
 
 1.468 
 
 .122 
 
 H 
 
 80.67 
 
 46,005 
 
 368.04 
 
 1-59 
 
 . 132 
 
 (i.V 
 
 83.18 
 
 49.770 
 
 398.16 
 
 1.72 
 
 .143 
 
 <if 
 
 35.78 
 
 53.670 
 
 429.36 
 
 1 1.85 
 
 . 154 
 
 T 
 
 38.48 
 
 57,720 
 
 461.76 
 
 i 1.99 
 
 .165 
 
 u 
 
 41.28 
 
 61,920 
 
 495.36 
 
 2.14 
 
 .178 
 
 7i 
 
 44.17 
 
 66,255 
 
 530.04 
 
 2.29 
 
 .190 
 
HYDRAULIC MEMORANDA. B7 
 
 Capacities of Cylinders and Ra.Yns.— Continued. 
 
 Diameter. 
 
 
 Load at 
 
 Cubic Ins 
 
 Gallons 
 
 Gallons 
 
 
 Area 
 
 1,500 lbs a " 
 
 per Foot 
 
 per Foot 
 
 per Inch 
 
 Inches. 
 
 
 in lbs. 
 
 of Cylinder. 
 
 of Cylinder. 
 
 of Cylinder'. 
 
 n 
 
 47.17 
 
 70,755 
 
 566.04 
 
 2 45 
 
 .20 
 
 8 
 
 50.26 
 
 75,390 
 
 603.12 
 
 2.61 
 
 .217 
 
 H 
 
 53.45 
 
 80,175 
 
 641.40 
 
 2.77 
 
 .230 
 
 8i 
 
 56.74 
 
 85,110 
 
 680.88 
 
 2 94 
 
 .245 
 
 8f 
 
 60.13 
 
 90,195 
 
 721.56 
 
 8.12 
 
 .260 
 
 9 
 
 63 . 61 
 
 95,415 
 
 768.32 
 
 3.80 
 
 .275 
 
 Qi 
 
 67.20 
 
 100,800 
 
 806.40 
 
 3.49 
 
 .290 
 
 H 
 
 70 88 
 
 106,320 
 
 850.56 
 
 3.68 
 
 .806 
 
 n 
 
 74 66 
 
 111,990 
 
 895.92 
 
 3.87 
 
 322 
 
 10 
 
 78.54 
 
 117,810 
 
 942.48 
 
 4 08 
 
 JS40 
 
 10^ 
 
 86.59 
 
 129,885 
 
 1039.0 
 
 4.50 
 
 . 875 
 
 11 
 
 95.08 
 
 142,545 
 
 1140.8 
 
 4.93 
 
 .410 
 
 lU 
 
 103.8 
 
 155.700 
 
 1245.6 
 
 5.39 
 
 .449 
 
 12 
 
 118.0 
 
 169.500 
 
 1856.0 
 
 5.87 
 
 .489 
 
 12^ 
 
 122.7 
 
 184,050 
 
 1472.4 
 
 6,87 
 
 .530 
 
 18 
 
 182.7 
 
 190,050 
 
 1592.4 
 
 6.89 
 
 . 574 
 
 Vdk 
 
 148.1 
 
 214.650 
 
 1717.2 
 
 7.48 
 
 .619 
 
 14 
 
 158 . 9 
 
 230,850 
 
 1846.8 
 
 8.00 
 
 .666 
 
 14^ 
 
 . 165.1 
 
 247.650 
 
 1981.2 
 
 8.57 
 
 .714 
 
 15 
 
 176.7 
 
 265.050 
 
 2120.4 
 
 9.17 
 
 .764 
 
 I'H 
 
 188.6 
 
 282.900 
 
 2263.2 
 
 9.80 
 
 .816 
 
 16 
 
 201.0 
 
 301,500 
 
 2412.0 
 
 10 44 
 
 .87 
 
 16^ 
 
 213 8 
 
 320,700 
 
 2565.6 
 
 11.10 
 
 .925 
 
 17 
 
 226.9 
 
 340.850 
 
 2722.8 
 
 1 1 . 78 
 
 .981 
 
 in 
 
 240.5 
 
 360,750 
 
 2886.0 
 
 12.49 
 
 1 .04 
 
 18 
 
 254.4 
 
 381,600 
 
 3052.8 
 
 13.21 
 
 1.10 
 
 18i 
 
 268.8 
 
 403.200 
 
 3225.6 
 
 13.96 
 
 1.16 
 
 19 
 
 288.5 
 
 425,250 
 
 3402.0 
 
 14.72 
 
 1.22 
 
 19i 
 
 298.6 
 
 447,900 
 
 3583.2 
 
 1^51 
 
 1 .29 
 
 ^20 
 
 314.1 
 
 471,150 
 
 3769.2 
 
 16.81 
 
 1.36 
 
HYDRAULIC PRESSURE 
 TRANSMISSION. 
 
 INTRODUCTION. 
 
 Water under high pressure (700 lbs. per z and upward,) 
 affords] a ready and satisfactory method of transmitting power 
 to a distance, and is particularly adapted to the movement of 
 heavy loads at moderate velocities, by cranes and elevators . 
 It is also the most efl&cient way of operating large tools for 
 pressing and joining metals, as in riveting, flanging, punch 
 ing, shearing, forging and also for the operation of turret- 
 in battle ships, and of disappearing gun carriages, high duty 
 elevator plants, etc. , etc. 
 
 That it can be made to operate tools quickly is shown 
 from the fact that forging presses are now made to make from 
 50 to 60 strokes per minute. The system usually consists of 
 one or more pumps, capable of developing the required 
 pressure: accumulators, which are vertical- cylinders with 
 heavily weighted plungers passing through stuffing boxes, by 
 which a quantity of water may be accumulated at the pressure 
 to which the plunger is weighte<:l: and of the distributing 
 mains to the presses, cranes or other machinery to be operated. 
 
 MECHAXICAL VALUE OF WATER rXDEE 
 ACCUMULATOR PRESSURE. 
 
 TJie gross amount of energy of the water under pressure 
 (stored in the accumulator.) measured in foot poimds, is its 
 volume in cubic feet X its pressure in pounds per square foot. 
 The horse power of a given quantity, steadily flowing, is 
 
HYDRAULIC PRESSURE TRANSMISSION. 39 
 
 144 p Q 
 
 H. p. =r ^ .2618 p Q 
 
 550 
 in which Q = quanity flowing in feet per second, 
 and p = j)ressure in pounds per square inch. 
 Theoretically, the mechanical value of water under an 
 accumulator pressure of 700 lbs. per n " (549.78 per circu- 
 lar inch), is 100,800 foot lbs., or 45 foot tons pea- cubic foot of 
 water, irrespective of the time in which it is consumed. 
 This gives 3.0545 H. P. per cu. ft. per minute, or one H. P. 
 requires 0.32738 per cu. ft per minute. Approximately, this 
 equals 1 H. P. from 2 gallons of water, but practically, allow- 
 ing for all losses, 3^ gallons are required. 
 
 THE EFFICIENCY OF HYDRAULIC APPARATUS. 
 
 The useful effect of a direct acting cylinder, ram or 
 plunger is usually taken at 93 per cent. , though in practice 
 it is found that the friction loss varies from 5 per cent, to 
 18 per cent, according to the condition of the packing, 
 which makes the Armstrong practice of 86 per cent, safer 
 to use in ordinary work. The folio wing table is given by 
 Mr. Percy Westmacott as the efficiency of a ram with 
 chain and pulley multiplying gear, properly proportioned 
 sxidi well lubricated. 
 
 Multiplying 
 
 2 to 1 4 to 1 6 to 1 8 to 1 10 to 1 12 to 1 14 to 1 16 to 1 
 Efficiency, per cent. 
 
 80 72 72 67 63 59 54 50 
 
 With large sheaves, small steel pins and wire rope, the 
 efficiency has been found as high as 66 per cent, for a 
 multiplying power of 20 to 1. 
 
 Henry Adams gives the following formula for effective 
 pressures in cranes and hoists ; it will be found to correspond 
 with the above. 
 
40 HYDRAULIC PRESSURE TRANSMISSION. 
 
 P = Accumulator pressure in lbs. per d" 
 m = ratio of multiplying power. 
 
 E = effective power in lbs. per z\ including all allow ^ 
 ances for friction. 
 
 E = P (.84 — .02 m) 
 
 SPEED OF HOISTING BY HYDRAULIC POWER. 
 
 The maximum allowable speed for warehouse cranes is 6- 
 ft. per second; for platform cranes and lifts, 4 ft. per second; 
 for passenger and wagon hoists with heavy loads. 2 feet per 
 second. Mr. Henry Adams is authority for the statement that 
 ••The maximum speed under any circumstances should never 
 exceed 600 ft. per minute.' But recent elevator practice haa 
 shown that a speed of from TOO to 800 ft. per minute can be 
 attained . 
 
 VELOCITY OF ^VATER THROUGH PIPES 
 AXD VALVES. 
 
 The following table gives the velocity in feet per second at 
 pressures from 700 lbs. to 5.000 lbs. . which the water will ac- 
 quire if discharged into the atmosphere through an approx- 
 imately frictionless aperture. Velocities for intermediate 
 pressures may be calculated from the formula: — 
 
 Velocity in feet per second = r2.19 v' pressure in lbs. = '. 
 
 Iq lbs. Pressure per 
 Square Inch. 
 
 700 
 
 1500 
 
 2000 
 
 3000 
 
 4000 
 
 5000 
 
 Velocity in feet per 
 second 
 
 326 
 
 472 
 
 548 
 
 670 
 
 772 
 
 862 
 
 With an accumulator pressure of 700 lbs. per z the natural 
 velocity (theoretically) is 326 ft . per second . It is found in 
 
HYDRAULIC PRESSURE TRANSMISSION. 41 
 
 practice that not more than one-tenth of this can be obtained 
 through the pipes and one third through the valves, in order 
 to maintain the proper speed of the machinery. The loss 
 from friction in the pipes is about 1 lb. per n " per 100 feet in 
 length, after they have been laid some time, 1 lb. additional 
 for each bend, and 10 lbs. for each branch. It is usual in cal- 
 culating to take the speed of the water through valves at not 
 more than 98 feet per second . 
 
 Experiments with water at 1600 lbs. per n " flowing into 
 a flanging press cylinder 20" diameter, through a i" pipe con- 
 tracted at one point to i", gave a velocity of 114 feet per second 
 in the pipe, and 456 feet at the reduced section. Through a 
 i" pipe reduced to f" at one point, the velocity was 213 feet 
 per second in the pipe, and 381 at the reduced section. In a ^ 
 inch pipe without contraction, the velocity was 355 feet per 
 second. 
 
 AREAS OF VALVES FOR MACHINERY UNDER 
 ACCUMULATOR PRESSURE.— (Formvi^af..) 
 
 A = Area of lifting ram. 
 
 m =r Ratio of multiplying power. 
 
 V = Velocity of load in feet per second. 
 
 V = " " water through valve in feet per second. 
 W = Length of ram, cross-head, sheaves, chain, etc., in lbs. 
 a = Area of lifting valve (mitred spindle) . 
 
 a' = " " lowering " " " 
 
 A V A V 
 
 m V m V^ 13 8 W 
 
 When cylinder is horizontal, then A 
 
 W 
 
 = area of returning ram. 
 
 700 
 
42 HYDRAULIC PRESSURE TRANSMISSION. 
 
 AREA OF PORTS IN SLIDE F^LFE-^.— (Formulae.) 
 
 (V-SHAPED OPENINGS.) 
 
 V = velocity of load in feet per second, 
 m -— Multiplying power . 
 A = Area of ram in n " 
 
 A V 
 Area of pressure port = 
 
 Area of exhaust port = 
 
 m 
 1.5 A V 
 
 ra 
 
 LIFTING RAMS FOR HYDRAULIC CRANES.- 
 
 (FORMULAE. ) 
 
 W = Load to be lifted in pounds . 
 
 w = Weight of ram, cross-head, chain or sheaves. 
 
 1 = Height of lift in feet. 
 
 m = Multiplying power. 
 
 e = Coefficient of effect = (.84 — .02 m) 
 
 a = Area of ram in n " 
 
 p = Accumulator pressure in lbs. per d " 
 
 W m 
 For horizontal cvlinders : a 
 
 vertical 
 
 
 p 
 
 c 
 
 
 w 
 
 m 
 
 + 
 
 w 
 
 
 P 
 
 c 
 
 
 w 
 
 m 
 
 — 
 
 w 
 
 Inverted '* a, — 
 
 P c 
 
HYDRAULIC PRESSURE TRANSMISSION. 43 
 
 TURNING RAMS FOR HYDRAULIC CRANES.— 
 (Formulae.) 
 w = load in tons, 
 k = rake in foot 
 
 1 = length between bearings in feet, 
 d = diameter turning drum in feet, 
 p = accumulator pressure in lbs. per a " 
 m = multiplying power, (usually 2 to 1 . ) 
 a = area turning ram per d " 
 f — a constant. 
 
 W R 2 f m 
 
 a = 
 
 1 d p 
 
 f = 70 for cranes up to li tons 
 f =r 60 *• " " '^ 4 " 
 f = 50 " '^ " " 10 ^' 
 
INDEX. 
 
 PAGE. 
 
 Armstrong Standard Flange Joint 1^ 
 
 Armstrong's Table of Hydraulic Cylinder Thicknesses 34 
 
 American Tract Society Building Elevator Plant 9 
 
 Atmospheric Pressure. 32 
 
 Accumulators 38 
 
 Allowable Speed of Cranes, Lifts, Etc. , 40 
 
 Areas of Valves (Mitre Seat) 41 
 
 " Ports in Slide Valves 42 
 
 Areas, Table of 25, 26 
 
 Brass, Tensile Strength of 30 
 
 Bronze, " '' " 30 
 
 Bessemer Bar Steel, Tensile Strength of 30- 
 
 Bushings, Eeducing 18 
 
 Bolts, Safe Loads for 31 
 
 '' Copper, Cast, Tensile Strength of 30 
 
 Box, Stuffing 32 
 
 Castings (Steel), Tensile Strength of 30 
 
 Cast Steel '' " '' 30 
 
 •' Iron " '' '' 30 
 
 Crucible Steel '' '' '' 30 
 
 Cupola, Malleable Iron from " " 30 
 
 Copper Bolts, Cast '' " '^ 30 
 
 Circumferences, Table of 25, 26 
 
 Cylinders, Thickness of Hydraulic 34 
 
 Capacities of Rams 36, 37 
 
 Cranes, Speed of Warehouse and Platform. 40 
 
 " Lifting Rams for 42 
 
 ' ' Turning Rams for 43 
 
 Collar, Lead Collar in Joint 8, 9 
 
 Cubes, Table of 25, 26 
 
 Du Val, Metallic Packing 32 
 
 Energy of Water Under Pressure 38 
 
 Efficiency of Rams 39 
 
 " Multiplying Gear 39 
 
 * ' Rams with Wire Rope . , 39 
 
 Elevators. Passenger 38 
 
 Otis 9 
 
 Flanging Press 41 
 
46 INDEX. 
 
 PAGE. 
 
 Flange Unions 13 
 
 Flanges. Table of 750 lbs 15 
 
 '' 1.500 lbs 16 
 
 Forged Steel. Tensile Strength of 80 
 
 Friction of Water in Pipe 41 
 
 ' ' Loss from . 41 
 
 Fittings, 3.000 and 5.000 lbs 18 
 
 ' • Size of 750 lb 17 
 
 '• '' 1,5001b 17 
 
 Guttapercha Ring 13 
 
 Gear, Efficiency of Multiplying 39 
 
 Gallons, Table of 33 
 
 Hydraulic Cylinders. Thickness of 34 
 
 ' ' Memoranda 32 
 
 • • Pressure Transmission 38 
 
 Hemp Packing 32 
 
 H. P. Water Under Pressure 39 
 
 Hoisting. Speed of 40 
 
 Hoists, Wagon ' ' " 40 
 
 Iron, Cast, Tensile Strength 30 
 
 Malleable, 
 Wrought, 
 Pipe 
 
 30 
 30 
 30 
 
 Jacobus, Prof. D. S., Report , 12 
 
 Joint. Leather 14 
 
 Guttapercha 13 
 
 '• Flange 13 
 
 Kent, William 3, 35 
 
 Loss from Friction 41 
 
 ' ' in Valves 41 
 
 ' ' in Pipes 41 
 
 Lifting Rams for Cranes 42 
 
 Lead Collar in Joint 8, 9 
 
 Leather Joint 14 
 
 Leathers 32 
 
 Loads for Bolts, Safe 31 
 
 Multiplying Gear, Efficiency of 39 
 
INDEX. 47 
 
 PAGE 
 
 Metallic Packing, Du VaL 82 
 
 Malleable Iron Air Furnace 80 
 
 " ' • from Cupola. ,.....; HO 
 
 Memoranda. Hydraulic 32 
 
 Merriman's Formula for Thickness Hydraulic Cylinders . . 34 
 
 Numbers, Useful. 38 
 
 Otis Elevator Plant. 9, 10, 11 
 
 Ordinary Pipe Sizes 27 
 
 Passenger Elevators. 88 
 
 Pressure Transmission, Hydraulic 38 
 
 Under Water 88 
 
 ' ' Atmospheric 82 
 
 Pressures, Working and Test 38 
 
 Press, Flanging 41 
 
 Platform Cranes 40 
 
 Packing Leathers 82 
 
 Hemp 32 
 
 Du Val Metallic 32 
 
 Pipe, Wrought Iron 27 
 
 " Steel 28 
 
 " Friction of Water in 41 
 
 ' ' Ordinary 27 
 
 ' ' Loss from Friction in 41 
 
 " X Strong 28 
 
 '' XX - 29 
 
 Recess for Lead 8 
 
 Reducing Bushings 18 
 
 Report, Jacobus 12 
 
 Rankin's Formula for Thickness of Hydraulic Cylinders. J^4 
 
 Rams, Lifting for Cranes 42 
 
 ' ' Turning " " 48 
 
 ' ' Capacities of 86, 87. 
 
 " Efficiency of 89 
 
 Ring, Guttapercha 18 
 
 Rope (Wire), Efficiency with 89 
 
 Rivet Steel, Tensile Strength of 30 
 
 Size of Fittings. 750 lbs 17 
 
 " " '' 1,500 '' 17 
 
 Stock of Fittings l-"). 16, 1 7, 18 
 
48 INDEX. 
 
 PAGE. 
 
 Steel. Tensile Strength of Forged Steel 30 
 
 '' Pipe, '^ " '' 28 
 
 '' Cast, '' " '* 30 
 
 '' Rivet, '' '' " 30 
 
 ' ' Bessemer Bar, Tensile Strength of 30 
 
 " Castings, " " '' 30 
 
 Safe Loads for Bolts ." 31 
 
 Squares, Table of 25, 26 
 
 Strength. Table of Tensile Strength 30 
 
 Stuffing Box 82 
 
 Speed of Hoisting 40 
 
 " Allowable 40 
 
 Table of Flanges, 750 lbs 15 
 
 " " '' 1,500 " 16 
 
 -' " Hydraulic Cylinder Thicknesses. Armstrong's. . . 34 
 
 " ^' Gallons 33 
 
 '^ Tensile Strength 30 
 
 Tensile Strength, Table of 30 
 
 Thickness of Hydraulic Cylinders 34 
 
 Tract Society Building Elevator Plant , . . .9, 10, 11 
 
 Test and Working Pressures .' 33 
 
 Turning Rams for Cranes 43 
 
 Unions, Flange ; 13 
 
 Useful Numbers 33 
 
 Velocity of Water .*....... 40 
 
 Valves, Loss from Friction in 41 
 
 ' ' Area of 41 
 
 ' ' Areas of Port and Slide 4:^ 
 
 Water, Velocity of 40 
 
 ' ' in Pipe, Friction of 40 
 
 ' ' Under Pressui'e 38 
 
 Wire Rope, Efficiency with. 39 
 
 Wagon Hoists 40 
 
 Wrought Iron Pipe 27, 28, 29 
 
 Wrought Iron, Tensile Strength of 30 
 
 Working and Test Pressures 33 
 
 Warehouse Cranes, Platform 40 
 
 William Kent 3, 35 
 
 X Strong Pipe, Table of Sizes 28 
 
 XX '' " ^' " " 29 
 
cc 
 
 Tk^i^I' joiiVT" 
 
 Ammonia, Steam and Compressed Air Fittings. 
 
 A complete line of Elbows, Tees, Couplings, Return Bends, 
 
 Flange Unions, Reducing Fittings and Bushings 
 
 carried in stock. 
 
 Wii.1, Not Leak From KxpaNvSion and Contraction. 
 
 TIGHT JOINT COMPANY, 
 
 159-161 BANK STREET, NEW YORK. 
 
 97 Cedar Street, New York City, 
 
 CONSULTING HYDRAULIC ENGINEERS. 
 
 Special attention paid to the laying out and piping up of 
 Hydraulic and High Pressure Systems. 
 
r 
 
 ^1 ^wiMvjncoo 
 
 021 218 343 A