US1148738A - Regulator for mixed-pressure engines. - Google Patents

Description

O. BANNER. REGULATOR FOR MIXED PRESSURE ENGINES.

APPLICATION FILED DEC. I2, 1912.

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CDLUMDIA PLANoaRAPli CO..WASHINGTON. D. C.

Patented Aug.' 3, 1915.

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l i l :oLuAmm PLANQGRM'H co., WASHINGTON. D. c.

OTTO BANNER, OF EASTON, PENNSYLVA NIA, ASSIGrNOR TO INGERSOLL-RAND COMPANY,

OF JERSEY CITY, NEW JERSEY, A CORPORATION OF NEW JVEIRSIElY.`

REGULATOR FOR MIXED-PRESSURE ENGINES.-

Specification. of Letters Patent.

Patented Aug. 3, 1915..

Application filed December 12, 1912. Serial No. 736,254.

To all whom it may concern Y Be it known that I, Or'ro BANNER, a subject of the German Emperor, residing at Easton, in the countyl ofvNorthampton and State of Pennsylvania, have invented a certain new and useful Improvement in Regulators for Mixed-Pressure Engines, of which the following is a specification.

This invention relates to regulators for mixed pressure engines and more particularly to regulators for engines where there is a variable supply of low pressure steam which is used for the main source of motive power for the engine and an auxiliary supply of high pressure steam to be used only when the low pressure steam falls off.

rThe object of the present invention is to provide a. simple, efficient and positive device for regulating first the total supply of steam to the engine according to the load and second to regulate the proportion of high and low pressure steam going to make up the total supply, in accordance with the amount and pressure of one of the steam supplies` usually the low pressure steam. `With this object in view I have devised a regulating means a practical embodiment of which is shown in the accompanying drawing in which Figures 1a, 1b and 1C show a vertical section taken through all the parts of the regulator.

The first main part of theregulator, designated in the Vdrawing as A, consists of a device which determines the total amount of steam required in the engine in accordance with the load carried by it. The device shown in A is designed for use with a centrifugal compressor for producing variable volume from the compressor with slightly varying speed and constant pressure. As shown it comprises a casing 1 set transversely of the shaft 2 of the engine to which it is attached. Geared to the shaft 2 is a pinion 3 which rotates a governor shaft 4 set in bearings 5 and 6 in the casing. Driven by the shaft 4 is a rotary oil pump of ordinary construction comprising intermeshing toothed wheels 7 and 8 which draw oil from the interior' of the casing by a passage' (not shown) and discharge' it into the passage 9 under considerable pressure, say 45 pounds. The construction of this pump is not material. Secured to the shaft 4 is a governor 1 0 comprising"J two inwardly spring pressed governor weights 11 and'12, one of which 12, is pivotally attached to one arm of a bell'crank lever 13 which is pivoted on a pin 14 setv in ya projectinglug -15 on the pinion 3. The other arm 16 of the bell crank lever is pivotally connected by' a link 17 to a lug 18 on a sleeve '19 which slides on the shaft 4. Secured to the sleeve 19 by a pin 20 sliding in slots 21 in the shaft 4 is a valve plunger 22 which is provided with a valve portion 23. Valve portion 23 slides in a valve sleeve 24. vThis sleeve 24 is provided with apertures 25 which are controlled by the valve portion 23 and leads from an oil pressure chamber 26. The chamber 26 is supplied with oil yfrom the passage 9 through a restricted passage 27 the opening of which can be adjusted by a valve 28. lThe valve sleeve 24 is likewise provided with apertures 29 which lead at all times to the interior of the casing 1 so that when the valve portion 23 does not cover the apertures 25 the oil from the chamber 26 can escape into the interior of the casing.

The relative position of the valve 23 and the valve sleeve 24 and hence the amount the apertures 25 are opened is determined not only by the movement of the governor but also by the movement of the valve sleeve 24.

The movement of the sleeve 24 is effected by the rod 30 which though not directly attached to the sleeve 24, moves it by means of a double faced valve 30EL which admits liuid to the chamber 30b through the port 30 from the pressure chamber 26 when the rod 30 moves inwardly, and allows this fluid to escape through the port 301 when the rod 30 moves outwardly, movement of the sleeve in this direction being accomplished by the spring 30e. The rod 30 is attached to piston 31 which is moved in one direction by a spring 32 and in the other vby pressure from the discharge of the compressor operated by the engine, which is carried through the pipe 33 to a cylinder 34 on the side of theV piston opposite the spring 32, this piston being so arranged that it moves inwardly and tends to close the apertures 25 when the pressure drops and vice versa. v

The'operation of thev part A of the regulator so far described is accordingly as follows: When the load on the engine is increased, in other words when more air is drawn off, the speed of the engine, and hence of the governor will fall off which will result in the movement of the valve 23 to the right, tending to close the apertures 25. Likewise, assuming the compressor to be of ordinary design, the pressure in the cylinder 34, which is that of the compressor discharge, will fall and the spring 32 will move the valve sleeve 24 to the-left, also tending to close the apertures 25. As stated above there lis an oil pressure of` about 45 pounds in the passage 9. This passage 9 is connected with the chamber 26 by restricted opening 27. If the opening provided in the apertures 25 by valve 23 is as small or smaller than the opening 27 pressure in the chamber 26 will be the same as that in the passage 9. If however the opening provided by the apertures 25 is larger than the opening 27 the fluid under pressure will escape through kthe apertures 25 and 29 into the interior of the casing more freely than through the opening 27. The pressure in the chamber 26 will therefore be the same or less than that in passage 9 in direct proportion to the size of the opening through the apertures 25 which depends on the relative positions of the valve 23 and the valve sleeve 24. If therefore the load is increased on the engine the effect of this increase on the speed of the engine and the pressure from the compressor will cause the size of the opening through the apertures 25 to be decreased and accordingly a higher pressure produced in the chamber 26. Likewise when the load on the engine is decreased by the demand on the compressor being lessened the increase in the speed of the engine and the pressure of the compressor will cause the valve 23 and the valve sleeve 24 to move so that the opening through apertures 25 is increased allowing the oil pressure in chamber 26 to fall.

From this description it will be seen that the oil pressure in the chamber 26 varies with the load on the engine and hence is an index of the total steam required to drive the engine.l l

Next to be considered is the mechanism for determining what proportion of this total amount of steam required to drive the engine is high pressure and what proportion is low pressure'. This device is indicated by B. From the chamber 26 a pipe 35 runs to the lower end of a valve motor cylinder 36 in which slides a piston 37 against the upper side of which presses a spring 38 tending to move it downwardly against the oil pressure conveyed from the chamber 26 by the pipe 35. To this piston 37 is attached a rod 39 to the upper end of whichr is centrally attached a lever 40. To the ends of the lever 40 are secured the stems of relay valves 41 and 42 serving to control respectively the operation of the live and exsure in pipes 43 and 44 in the following f manner: Oil under pressure in the pump is supplied through pipe 45 to a chamber 46 from thence it passes through restricted passages 47 and 48 controlled by valves 49 and 50 to passagesl and 52 leading respectively to the valves 41 and 42. Valves 41 and 42 slide in valvesleeves 53 and 54 which have apertures. and 56 leading to the interior of the sleeve'from the passages 51 and 52 and apertures 57 and 58 leading to chambers 59 and 60 from which the oil can How back by pipes (not shown) to the oil pump again. Pipe 51 has at alll times free communication with pipe 43 around the valve sleeve 53 while pipe 52 has similar connection with pipe 54. According to the extent therefore to which the valves 41 and 42 close apertures 55 and 56 the oil pressure in pipes 51 and 52 and hence in pipes 43 and 44 will be the same or less than the oil pressure in chamber 46. Valve 41 is provided with a weight 61 which tends to keep it in its lowermost position. Valve 42 is not weighted. It will therefore be seen that as the pressure in chamber 26 and hence in the cylinder 36 varies with the load the piston 37 willmove up or down and will move the lever 40 with it. As the valve 41 is weighted the tendency would be for the movement of the piston to effect only the valve 42 bearing the opening of the aperture 56 and hence the pressure in the pipe 44 which controls the low pressure steam supply. This is in fact what occurs except wheny the low pressure steam is insufficient in which case a further mechanism comes into effect. In alinement with the stem of valve 42 is a rod 62 on which is secured a float 63 submerged in a bath of mercury 65 contained in a cylinder 66. This cylinder is connected by a pipe 67 to afsecond cylinder` 68 which is connected hy a pipe 69 to a source of low pressure steam. The pressure in the cylinder 66 is the same as that of the atmosphere on account of a vent 70. As the pressure of the low pressure steam is under normal conditions above that of the atmosphere the mercury in cylinder 66 will be maintained at a higher level than that in cylinder 68 and accordingly the rod 62 will be maintained out of contact with the valve stem of valve 42 by its float 63. If however the pressure of the low pressure steam falls below the desired amount the level of the mercury in cylinder 66 will fall carrying with it float 63 and the rod 62 whichwill then contact with the upper end of the stem of valve 42 and limit its upward movement.

The operation of the proportioning device B will therefore be as follows: Any

stem. of valve 42 the valve 42 Will alone move. This movement will cause avariation in the eicctive size of the apertures 5Gl and consequently a variation in the oil pressure in the pipe 44 correspondingtothe change of the pressure in the chamber 36. It however the low pressure steam is` insuhcient the rod 62 will contact withV the stem of the valve 42 and prevent this mo-vement upwardly, its downward movement being prevented by weight 61 on valve 41. In such case any movement of piston 37 will result in movement of the valve 41 which will vary the effective opening of` aperture and accordingly the pressure in pipe 43. It will be seen therefore that a change of pressure in the chamber 36, for example an increase of oil pressure due to an increase in load on engine, will produce a corresponding increase of pressure in one or both of the pipes 43 and 44 the relative increase depending on the pressure of the low pressure steam supply. It now remains to describe the mechanism by which these changes of pressure are transmitted to the steam valves of the engine thus regulating the admission of the steam.

The low pressure steam valve mechanism is designated by C and comprises a duplex valve chest 71 provided with valve seats 72 and 73 on which seaty balance valves 74 and 75. Steam is supplied through the inlet opening 76 and discharged to the engine through exhaust openings 77 and 78, the device here shown being designedl for use with a turbine having two low pressure stages. Valves 74and 75 are operated by motors comprising pistons 79 and 80 vwhich slide in cylinders 81 andf82 the lower ends of which are connected with pipe 44 the pressure in which is controlled by the valve 42 previously described. Opposing the upward movement of pistons 79 and `80 are springs 83 and 84. Spring 84 islonger and weaker than the spring 83 accordingly when an increase in the pressure occurs in the pipe 44 valves 74 and 75 will open and admit steam from the inlet pipe 76 to their respective turbine stages. As the spring 84 is weaker than the spring 83 the valve 75 will open rst while the valve 74 will not open until the valve is open to its full extent.

The high pressure steam valve is designated by D and comprises a valve; chest 85 provided with seats 86 on which seats a balance valve 87. Steam is admitted through the inletopening 88 and discharged as here shown to a single high pressure stage through an exhaust outlet 89. Valve 87 is operated by a motor comprising a piston 90 slidin-gin a cylinder 91 the lower end of which is connected vwith the pipe 43. Up-

wardmovement of the piston 90 isopposed by. spring 92.

Taken as a whole the operation of ,the regulator may be briefly described as follows: Suppose that `theload on theengine increases, this will cause the valve 23 andvalve sleeve v24.to `move so that theeective opening ofaperturesz25 isdecreased. This will, prevent vthe freeescape of oil l.pressure from ,the chamber 26r and consequently raise the pressurefth'erein and.A also in the cylinder 36 under the piston 37. This will raisethe piston 37 and ywith it the Vlever arm 40. If the supply of low pressure `steam is ample and the rod 62 is out ofcontact with the stem of valve 42 the valve 42 will move. up wardly shutting olii the escape of oil pres` sure from ypassage 52 and increasing the pressure in pipe 44. This increase in pressure Awill result in a movement of one or both of the valves74 and 75 allowing more =low pressure steam to enter the engine. If

the low pressure stem is insufficient the upward movement of valve 42 will be more or less prevented by the rod 62 and .the upward movement of the piston 37 willresult vin a similar `movement of the valve 41. This will result .in the decrease of the eiective opening of the aperture 55, an increase in the pressure in `pipe 43 and an upward movement yo1. the piston 90 opening the valve 87 and allowing live steam to enter the engine. Furthermore if ata constant load the pressure of the lowpressure steam supply falls off Vthe rod 62 will move downward and tend'to close the valve 42 opening the valve 41 and allowing more high pressure steam to enter the engine. The reverse eiiect is obtained when ythe pressure of the low pressure, steam rises. It will thus be evident that whatever variation there maybe in the lowpressure steam supply the engine will be at all times supplied with asuiiicient amount of additional live steam, if necessary, to take care of any increased load on the engine.

Although .the invention is here shown. as a regulating device for compressors and a means shown for assisting the action of the speed regulator .by the pressure from the compressor the invention is not limited to this as the speed regulator canbe used by itself or any other means of lregulation can be employed which would produce aifluid pressure varying lwith the load on the engine. Furthermore any number of low or high pressure steam valves could be used and it is to be understood that the present showing and description discloses only one specified modification of my invention and other forms andmodifications are included in the spirit and scope of the invention as expressed in the claims.

What I claim is: l

l. In a regulator for mixed pressure engines, high and low pressure valves, fluid operated motors forv moving said valves, governing means for supplying fluid under pressurein accordance with the demand on the engine, a regulating motor operated by said fluid pressure to regulate the total steam admission, valves operatively connected with said motor to admit vfluid pressure to said valve motors, said valves being relatively movable, and means operated by the loW pressure steam to regulate the relative movement, of said valve motor [admission valves.

:2. In a regulator for mixed pressure enginesmeans for supplying fluid pressure in accordance With the load on said engine, a total steam supply controlling motor comprising'a cylinder and a piston Whose position isdetermined by said fluid pressure, a lov/"pressure steam valve ymotor and a high pressure steam valve motor, said moto-rs being operated by fluid pressure, relay valves for admitting'fluid pressure to said steam valve motors, connections between said controlling motor and said relay valves for transmitting movement of the controlling motor to one or both of said relay valves,l said relay valves being capable of movement relative to said controlling motor, and means controlled by the pressure of the loW pressure steam for determining the relative movement of said relay valves.

3. In a regulator for mixed pressure engines, means for supplying fluid pressure in accordance with the load on said engine, a total steam supply controlling motor comprising a piston Whose position is determined by said fluid pressure, high and lovv pressure steam valves, a lever pivotally connected to said total steam supply controlling motor piston, relay valves pivotally connected to the ends of said lever andy adapted for movement With and also relative to said piston to control the fluid pressure in Ysaid steam valve motors, a motor for controlling the relative positions of said relay valves, and means to ldetermine the action of said motor by the loW pressure steam pressure. 'Y

'34. In a regulator for mixed pressure engines, governing means for supplying fluid pressure invacc'ordance with the total steam demand, a regulating motor having a mov.- able elementactuated by said fluid pressure, valves for controlling the highand low pressure steam supply, a lever mechanism joining said valves and said movable element so that motion of said movable element moves one of said valves, While motion of one of said valves When said' movable 4element is stationary moves the other of said valves in the opposite direction, means to hold said high pressure valve stationary When the low pressure steam is sufficient, and a device actuated by the pressure of the low pressure steam supply Which acts to close said loyv pressure valve and open said high pressure valve when said loW pressure steam is insuliicient.

5. In a regulator for mixed pressure engines, high and louT pressure steam valves,

fluid operated motors for moving said valves, a governing means for said engine for supplying fluid pressure in accordance With the total steam demand, a regulating motor comprising a rod the position of which varies With the pressure furnished by said governing means, 'a lever pivoted on said rod, relay valves, for admitting operating fluid to said valve motors, attached to said lever on either side of its pivot point, means to hold one of said relay valves normally closed, so that the other relay valve Will move With the movement of said rod and lever, and a device to close the other valve when the pressure of the steam supply controlled thereby falls, to an extent determined by the fall in pressure, and open the first relay valve to a proportionate extent against said holding means.

6. In a regulator for mixedpressure engines, a governing means for supplying fluid pressure in accordance with the total steam demand, a movable element v-:hose position is determined by said fluid pressure, a lever pivoted on said movable element, a low pressure lsteam controlling valve operatively connected with one end of the lever and a high pressure steam controlling valve operatively connected to the other end of said lever, means to hold one end of said lever ina position to close said'high pressure valve When the low pressure steam is sufficient, and means to` move the other end ofsaid'lever to close the low pressure valve and open thehigh pressure valve when said low pressure steam is insufficient.

7 In a regulator for mixed pressure enines a Governing means su al in@ fluidk 9 2D b D pressure in accordance with the total steam demand, an lelement movable in accordance With said pressure, high and loW pressure steam controlling valves, means to transmit the motion of said movable element to actuate either of said valves, means to hold said high pressure valve in closed position When the low pressure steam supply is insuflicient and allow the motion of said movable element to actuate said low pressure valve, and meansto limit the travel of said low pressure valve in accordance with the pressure of said low' pressure steam supply, and allow further motion of said movable element to overcome said holding means and actuate said high pressure valve.

lic

S. In a regulator for mixed pressure engines, a governing mechanism for supplying fluid pressure in accordance with the total steam demand of the engine, a regulating motor comprising a movable element Whose position is determined by said fluid pres sure, a high pressure steam valve, a low pressure steam valve, means to transmit the motion of said movable element to said low pressure valve, means to hold said high pressure valve closed when the lovv pressure steam is suliicient, means for closing said lovs7 pressure valve When the low pressure steam is insuiiicient and means for transmitting the motion of said low pressure valve in closing to open said high pressure valve.

9. In a regulator for mixed pressure en gines7 a governing means supplying fluid pressure in accordance with the total steam demand, a regulating motor comprising an Copies of this patent may be obtained for element moving in accordance With said fluid pressure, a lever pivoted on said element, a high pressure valve operatively connected with one end of said lever and a low pressure valve operatively connected With the other end, means exciting a constant pressure on one end at said lever tending to close said high pressure valve, and an element actuated by the pressure of the low pressure steam supply toclose said low pressure valve, when said 10W pressure falls, and open said high pressure valve against said constant pressure.

In testimony whereof, I have hereunto set my hand.

OTTO BANNER.

Vitnesses PAUL HOFFMAN, F. A. POPE.

five cents each, by addressing the Commissioner of Patents,

Washington, D. C. v

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