Show THE HONORINE PUMPING PLANT AND LONG LO DISTANCE STEAM transmission WRITTEN FOR THE MINING REVIEW BY J M CALLOW M E some of the facts connected with the pumping of the honorine at stockton utah may be of interest and value to mine operators the writer was consulted by the management to devise means to control the flow of water there the then existing arrangements being inadequate As the property was being worked under a time bond it was essential 1 that the scheme should not only be the most expeditious one but one entailing the smallest possible first cost the pumps were being beina t driven by compressed air generated by one duplex rand and two straight line Inger the coal consumption when pumping gallons a minute feet was some twelve ton per twenty four hours and the boilers were evaporating approximately pounds of steam per hour the three machines were compressing about 1200 cubic feet of air per minute to 65 pounds which was conveyed to the pumps a distance of over feet adlung tile the course of a very tortuous tunnel in a 3 31 inch pipe the loss of pressure by friction in the pipe when conveying this quantity of air being as much as 30 pounds in the shaft were a cameron and a blake sinkers both delivering under 60 feet head to a duplex janesville station pump which was raising against feet to the tunnel level makings making a total combined lift of feet at the station ump pump P level two ingersoll 10 re heaters had been installed to prevent freezing of the pumps and to gain some greater economy but whatever economy was effected was quite insufficient to enable alie the plant to make any material or apparent impression impressio non on the inflow of water the actual value of the quantity of steam generated if applied to ordinary commercial engines would represent some horse power and as the theoretical work of pumping gallons per minute feet high is but 24 horse power the comparative mechanical efficiency of this combination it will be seen was only 12 per cent after a careful survey of the many conditions complicating the problem the writer did not hesitate to advise the laying of a new 5 inch line in the tunnel and using steam direct on the pumps the idea of carrying steam successfully nearly three quarters of a mile was generally received with much suspicion to which it is now a satisfaction to reply with a record of its perfect working g in i in every particular with compressed air the boilers and fa frari on losses losse sm m british therma units 9 per pel a each 1000 feet or 01 pipe for press of for a at T P press ess of results betow hy 0 53 M steam pounds coel cherf o old Q of poe p in inches anches nn ches pe perho rhoul Lii 1 z 3 4 6 7 9 1 9 10 0 12 as soo 7 92 0 04 Rs ff 5 1000 63 fol ass 90 as z 1500 7 2 zea z eio azo as 88 41 4 5 1 zt e za 2000 SO 1 S sf 97 so za 16 s RZ S aso 1760 1 37 as 6 8 93 55 53 iz IR 2 1 77 77 s az 2 a 8 Is fan 1 ai S 7 as 4 30 24 OZ OS az boo 14 4 1340 1 39 76 68 9 coo 4 also Z i 1 rao 1 3 00 6 ZOO 3 iao SO f 1040 46 4 6 9 too B 8 ats 4 Z sto 50 i ao 1 I 0 GS f za zoo S too 6 SOO 34 0 0 oso OS ats hf 3 y W WS bleam weir der berjer ap jer e h hr I 1 irl eneff 70 in n hl ff d 0 ufa r m n ach e s af J Y caeg off giclio t h s re r e s s 6 6 1 rr P 15 machines were very much overtaxed to pump gallons per minute feet and were constantly scantly breaking down the sinking of the shaft which was the principal object of the operation was practically at a standstill and after six months work had only been lowered about 25 feet after the change to steam direct on the pumps progress in the shaft was soon made at the rate of nearly three feet a day and the same amount of coal is now per forming three times as much work or a mechanical ch anical efficiency for the plant of 36 against the former 32 12 per cent compound pumps in place of the single cylinder ones now used would easily bring the efficiency up to 60 per cent from actual measurements the water of condensation was found to be pounds per hour for the entire length representing 6 per cent of the weight of steam colv conveyed eyed which was 2 per cent better than the writer write promised the details of the pipe line 1 are as a follows length from boilers to first pump feet diameter of pipe 5 inches covering Co verin 1 inch magnesia asbestos three austin steam separators one at 1200 1 feet one at 2400 feet one at feet the first two connected with crane steam traps blowing off into sumps bumps in the tunnel the last one to a no 2 howlands hoelands How lands steam trap the latter was found the much more satisfactory trap trao the others are not to be recommended as they easily stick and require much attention ordinary sleeve expansion joints with brass bushings and safety tie rods about every ao 00 feet the pipe was put in the roof of the tunnel there were 34 different angles t in the pipe f from roin 6 degrees up to 72 degrees exterior angles for angles up to 30 degrees angle washers between the flanges 11 were used above that pipe was bent cast iron flandes flan a ires were used to connect pipe but they ought not to have been except where pipe was perfectly factly straight and the strains would be truly compressive ones at several places where angle washers were used the expansion of the pipe caused excessive strain on the outer edges of the flanges 1 sometimes breaking bolts at other times flanges these weak places were with heavy timbers since the first month no breakage or leaks have re occurred in the pipe of any importance on another occasion forged steel flanges t with steel bolts are the only style that should be used angle washers are also to be condemned and the pipe should at least be bent at all angles above 10 degrees the sleeve expansion joints worked much better than they are usually given credit for doing 6 but for a permanent job double swing elbows or U bends would make a much better job the roof of tunnel is the proper place for the pipe never put it in the floor of the tunnel loss of pressure in the line 12 pounds boller boiler pressure 90 95 pounds the temperature on outside of covering in still air practically no ventilation degrees fahr surrounding air 90 there was no surface connection at the intersection 61 0 the shaft and tunnel the nearest current of air w was as 1000 feet back in the tunnel practically no circulation around pumps and in the shaft temperatures ranged from 90 to degrees bottom of shaft always cool when temperatures in shaft exceeded degrees one of the sinkers was worked on air for a few hours till temperature pera ture at the station was reduced heat was trying at first but men accustomed to it suffered no ill effects the pumps exhausted into the sump at the station pump the sinkers being provided with exhaust pipes for that purpose two factors contribute to the losses in the flow flo w of the steam through pipes first that due to friction second that due to radiation from the sides of the pipe in order that the sum of these two losses may be a maximum the loss in heat beat units caused by friction must be one fifth of that thai caused by radiation below are tables giving the losses in britina thermal units by both friction and radiation for pipes of different lengths and diameters and different quantities of steam carried per hour from which can readily be determined the losses for any condition likely to be met with and the most economical diameter of pipe thereby accurately determined the tables are based on E A Rud igers formu formulas lw I 1 W fl f 1 loss jn in heat units by friction 10 2 da loss in heat units by radiation r 1 d in which W equals weight of steam delivered delivered in rounds pounds per hour fCo efficient of friction of pipe 65 to of pipe in feet of pipe in inches of radiation see table solute terminal pressure Gauge press 5 explaining the tables by taking the honorine cula loss the actual loss by measurement with the line in operation gave 71 percent in B T Us or 6 per cent in weight the loss of pressure in pounds were square inch when pipe is carrying steam with minimum loss from both friction and radiation as in this instance can be determined by the following formula loss pounds pressure per square inch OC d drip r I 1 p w using the same values for d r 1 p and W as before for honorine pipe loss pounds pressure per square inch 0 the boiler pressure must therefore be 90 1069 absolute or 1069 by the gauge as a matter of fact the loss of pressure at the mine was only 12 pounds the honorine pipe was put in on the strength of these same calculations which it radalon daton Ra losses in n british Ther maln 4 e red re nesses of no moti za 1 d GC acnes a 1 C 0 obern r erla q fie u t oice of ppe n inches aches 1 a 3 4 S D 7 8 9 10 az s us 1 1 80 Z 1 VO a 4 c 0 90 azoo 67 1 1 f 9 SO 0 ja ai 7 00 ee az OBO nsf 0 go 90 ac 1 IS 15 ZOO 44 I 1 ta t i az 4 00 78 COO 04 SOO BOO 3 03 ZOO BOO 34 1 01 0 0 90 00 23 60 94 41 4 1 1 s W 0 36 bao 55 ova 73 9 0 2 4 70 65 0 60 83 SOO sl M 0 0 90 r 0 30 34 S 7 68 ZO asso f 1920 sa 7 1 2040 H 0 2 r r avel iava 1 efian 1 I ft fl 0 in slide fauk cults pipe line as ai an example we have hanew pounds 15 1 in covering prom from friction table under 5 inch pipe with pounds of steam this loss will be seen to be B T U per hour for each 1000 feet of pipe then from radiation table under 5 inch pipe with 1 inch covering and 90 pounds pressure boef see the ratio of these two losses to each other is 65 to ai 1 with 4 inch pipe the ratio will be found to be only 17 and with 6 inch as much as 19 showing 5 inches to be the nearest suitable size the sum of these two losses per 1000 feet of pipe is this multiplied by 34 our line being feet long equals B T units per hour total losses referring to a table of the properties of steam see kents M E pocket book the total heat units in I 1 pound of steam at 90 pounds pressure is 1180 this multiplied by gives us B T units in our 50 56 MO steam per hour goo 68 per P cent cal will be seen have been confirmed in its practical 0 operation pe ration there the efficient coefficient co was determined from data derived from the pipe in operation from which the other coefficients co given in the tables have been calculated for other pressures and of covering in the original calculations the efficient coefficient co used was giving a loss of 75 4 7 5 per cent but the experience peri ence with the pipe reduces this to it is important in any pipe line and especially ally a long one to provide for its expansion under steam the efficient coefficient co of expansion for wrought iron is per each degree fahr increase of temperature the temperature pera ture of steam at 90 pounds absolute is degrees the surrounding air is say 60 degrees a difference of degrees the total expansion therefore on a length of feet will be feet so that by placing expansion joints about every feet each joint will have to take up about 15 inches or per feet or for rough figuring say 1 for every 50 feet to convert B T units to pounds weight of water divide the number of heat units by 1185 for pounds steam and by 1180 for 90 pounds steam |