US2653550A - Power transmission - Google Patents

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US2653550A
US2653550A US189028A US18902850A US2653550A US 2653550 A US2653550 A US 2653550A US 189028 A US189028 A US 189028A US 18902850 A US18902850 A US 18902850A US 2653550 A US2653550 A US 2653550A
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fluid
pressure
rotor
passage
chamber
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US189028A
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Duncan B Gardiner
Ernst F Klessig
Henry C Parsons
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Vickers Inc
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Vickers Inc
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface

Description

pt- 29, 19 3 D. B. GARDINER ET AL 3,
POWER TRANSMISSION 3 Sheets-Sheet 1 Filed not. 7, 1950 INVENTORS DUNCAN B. GARDINER ERNST F. KLESSIG BgjENRY C. PARSONS F l G. 2
ATTORN EY p 1953 D. B. GARDINER ET AL 2,653,
POWER TRANSMISSION 5 Sheets-Sheet 2 Filed Oct. '7, 1950 FIG.3
[NVENTORS CAN B. GARDINER D E ST F. KLESSIG HENRY C. PARSONS BY FIG.4
ATTORNEY p 1953 D. B. GARDINER ET AL ,6 3,
4 POWER TRANSMISSION Filed Oct. 7, 1950 3 Sheets-Sheet 5 FIG. 5
& l-NVENTORS DUNCAN B. GARDINER FIG.6 ERNST F. KLESSIG HENRY C. PARSONS BY ATIORNEY Patented Sept. 29, 1953 UNITED STATES PATENT OFFICE POWER TRANSMISSION Application October 7, 1950, Serial No. 189,028
This invention relates to power transmissions, and is particularly applicable to those of the type comprising two or more fluid pressure energy translating devices, one of which may function as a pump and another as a fluid motor.
The invention is more particularly concerned with a vane type motor or pump for use in power transmissions of this character.
The invention comprises an improvement in devices of this type wherein a slotted rotor carrying a plurality of reciprocating vanes is mounted within a working chamber, the inner contour of which forms a Vane track against which the outer ends of the vanes are adapted to be urged into contact.
It is essential for efficient operation to utilize some force in addition to centrifugal force in order to maintain contact of the vanes with the track. In pumps of this type one convenient method has been to connect the high pressure or outlet side of the device to the inner ends of the vanes. However, where the device is to be operated as a motor it is insufiicient to connect the inlet side to the inner ends of the vanes. It is necessary to provide a higher pressure at the inner ends of the vanes than is present at the inlet side of the motor. As the vanes pass through the inlet zone of the motor inlet pressure tends to separate the vanes from the track which would cause leakage and free wheeling of the motor. In addition, for proper starting of the motor, at crossover between the fluid zones, and for proper reversal it is essential that the vanes be maintained in contact with the track.
It isalso impractical, if the device is to operate as a reversible motor, to continually connect one side of the device to the inner ends of the vane slots. The high pressure or inlet side of the device becomes the low pressure or outlet side of the device upon reversal.
One example of a fluid pump of the type mentioned is disclosed in the copending application of Duncan B. Gardiner, et a1., Serial No. 81,146, now Patent No. 2,544,988. The above application discloses a pressure chamber immediately adjacent one side of the rotor. A side plate is floatably mounted in the chamber adapted to be maintained in fluid sealing engagement with the rotor by pressure fluid directed to the chamber. The outlet side of the device is continually connected to this chamber and also delivered from the chamber to the inner ends of the vane slots. Due to the fact that the outlet side of the device is continually connected to the chamber it is not readily adaptable for use as a reversible fluid motor.
6 Claims. (01. 103-136) This invention provides the advantages of the device disclosed in the aforementioned application, but in addition may be operated both as a reversible fluid pump or motor. It provides the advantages of a pressure actuated, floating side plate, but in addition may be operated as a reversible motor. This advantage is obtained by providing a pressure chamber which is isolated from the fluid zones of the device and having a separate external connection port. Means are provided for connecting the pressure chamber to the, inner ends of the vane slots. Thus, the main pressure source may be connected to the chamber with simple and economical valving providing the differential in pressures between the inner and outer ends of the vanes. An auxiliary source of pressure fluid may also be connected to the chamber.
It is therefore an object of this invention to provide an improved rotary vane pump or motor of the reversible type.
It is another object of this invention to provide in a reversible rotary vane pump or motor an economical and simplified structure for connecting a source of pressure fluid to the inner ends of the vane slots for maintaining the outer ends of the vane in contact with the vane track regardless of the direction of operation of the device. This source of pressure fluid may be either the pressure fluid delivered by the device when operating as a pump or the pressure fluid delivered thereto when operating as a motor, or may constitute an auxiliary source of pressure fluid.
It is still another object of this invention to provide a device of the type mentioned having a floating sideplate which is maintained in fluid sealing engagement against the rotor by pressure fluid delivered to a pressure chamber which is isolated from the fluid inlet and delivery zones of the device.
It is a further object of this invention to provide a device of the type mentioned having a pressure chamber with a sideplate mounted therein, which sideplate isolates the chamber from the fluid zones of the device, which also serves to deliver pressure fluid from the chamher to the inner ends of the vane slots and also connects one of the fluid zones of the device to one of the external connection ports.
It is another object of this invention to provide a low 'cost device of the above-mentioned type having advantages contributing to efliciency, reliability, and long life as well as case of maintenance.
Further objects and advantages of the present invention will be apparent from the following description, reference being bad to the accompanying drawings wherein a preferred form of the present invention is clearly shown.
In the drawings:
Figure 1 is a sectional view of the preferred form of the present invention taken on line I--I of Figure 2.
Figure 2 is a plan view of the present invention.
Figure 3 is a view taken on line 33 of Figure 1.
Figure 4 is a view taken on line 44 of Figure 1.
Figure 5 is a view taken on line 5-5 of Figure 1.
Figure 6 is a view taken on line 66 of Figure 1.
Figure '7 is a diagrammatic view of a hydraulic power transmission system incorporating a preferred form of the present invention.
Referring now to Figure 1 there is shown a reversible rotary vane pump or motor designated generally by the numeral ID, the body of which comprises a cam ring I2 suitably sandwiched between and connected by bolts I4 to a main right end housing member I6 and a left end housing member I8.
The inner contour of the cam ring I2 is substantially elliptical in shape as shown more clearly in Figures 4 and 6, and forms a vane track indicated generally by the numeral against which the outer ends of a plurality of reciprocating vanes 22, carried by a rotor 24, are adapted to be held in contact. The vanes 22 reciprocate within substantially radial slots 26 of the rotor 24, said slots having enlarged portions at their inner ends indicated by the numeral 28. Duplicate grooved circular pressure channels 36 extend to a slight depth from each face of the rotor to the inner ends of the slots 26.
The rotor 24 is mounted within the cam ring I2 so that the axis of the rotor 24 is concentric to the axis of the ring by means of a shaft 32, splined at 34 to the mating spline of the rotor. The shaft 32 is rotatably mounted in a stepped bore 35 and supported on radial and thrust bearings 36 and 38 completely within the right end housing member I6. The shaft is provided with a seal 40 and any leakage may be drained by means of an external drain port 42 connected to the stepped bore 35.
With the rotor 24 mounted within the cam ring I2, two opposing working chambers 44 and 46 are formed through which the vanes pass as the rotor turns. These working chambers may be appropriately divided into diametrically op posed sets of fluidzones, each set of which may be either inlet or outlet zones depending on the direction of operation of the device. One set of fluid zones comprises that portion of the working chambers 44 and 46 registering with a pair of diametrically opposed arcuately shaped fluid openings .8 and 50. The fluid openings 48 and 50 comprise the terminus of two branches SI and 52 (Figure 3) of a fluid passage 54 adapted for either an inlet or outlet passage, which passage registers with an external connection port 56 in a flange member 58 suitably bolted to the housing member I6. The other set of fluid zones comprises that portion of the working chambers 44 and 46 registering with another pair of diametrically opposed arcua-tely shaped fluid openings 60 and 62 in a side plate 64 which is floatably mounted in a recess 66 of the housing member I8, the open 4 end of which is closed by the cam ring I2 and rotor 24. The construction of the side plate 64 is such that when mounted in the recess 66 a pressure chamber 68 is formed in the recess 66 which is completely isolated by the side plate from the working chambers and fluid zones, and also isolated by the side plate from a passage 69 in the housing I8 which opens at one end to the recess and which at its opposite end registers with an external port II formed in a flange member 13 suitably bolted to the housing member I8.
The side plate 64 is adapted to be maintained in engagement against the cam ring I2 and in fluid sealing engagement with the rotor 24 by means of pressure fluid admitted to the pressure chamber 68 through an external port ID in the housing I8 leading directly to the chamber. The side plate 64 may be maintained initially, and at extremely low pressures, in engagement against the cam ring I2 and in fluid sealing engagement with the rotor 24 by a spring I2.
The fluid zones in the working chambers 44 and 46, which register with the side plate openings 60 and 62, are connected to the passage 69 by means of a set of drilled passages I4 and I6 in the side plate which are connected to the opening 60, and a duplicate set of drilled passages I8 and 88 connected to the opening 62, and a grooved fluid channel 82 extending around the periphery of the side plate. Each set of drilled passages leads to and connects its respective associated side plate arcuate opening to the grooved channel while the grooved channel connects the drilled passages to the passage 69.
The side plate 64 is also provided with a plurality of ports extending completely therethrough from one face to the other face thereof, indicated by the numeral 84, and which register with the circular pressure channel 30 of the rotor 24. The ports 84 are adapted to conduct pressure fluid from the chamber 68 to the rotor pressure channel 30 from whence it is conducted to the enlarged inner portions 28 of the vane slots 26 for the purpose of maintaining the outer ends of the vane 22 in contact with the vane track 26. The side plate 64 is prevented from rotary movement by means of two dowel pins 88 which ex- .tend through the cam ring I2 into both casing member I6 and side plate 64, which dowel pins also serve to correctly align the adjoining members.
Suitable oil seals 90 and 92 are provided in the end housing members I6 and I8 adapted to be on opposite sides of the cam ring I2 to aid in preventing seepage. In addition, the side plate is provided with a groove for the insertion of a seal 94 to prevent seepage from the pressure chamber 68 to the fluid channel 82.
The housing member I6 is provided with a flat end surface indicated by the numeral 96 which serves as an end wall adapted to cooperate with the flat mating surfaces of the cam ring l2 and rotor 24. The end housing member I8 is also provided with a flat surface at the open end of the recess, indicated by the numeral 98, which cooperates with the fiat mating surface of the cam ring I2.
The entire surface of the side plate 64, opposite to that facing the rotor 24, and indicated by the numeral I00, is exposed to the pressure in the pressure chamber 68 in order to maintain the side plate in engagement against the cam ring I2 and in fluid sealing engagement with the rotor 24 so as to maintain the proper running clearance therebetween. Running clearance between 5 the rotor 24 and the surface of the side plate 84, facing the rotor 24, said surface being indicated by the numeral I02, is provided by the difference in thickness between the cam ring and that of the rotor.
Referring to Figure '7, there is shown a hydraulic power transmission system wherein the device I8 is adapted to be operated as a reversible fluid motor. There is shown in such figure a fluid pump I04 connected by a supply line I06 to a reservoir I08 and by a pressure delivery conduit III! to the pressure port II2 of a conventionally constructed four-way directional control valve H4. The valve H4 is also provided with motor ports H6 and H8 which are respectively connected to the external connection ports 56 and H of the motor I by means of conduits I20 and I22, and with a tank port I23, which is connected to the reservoir by a conduit I25. A suitable relief valve I24 is incorporated in the pressure delivery conduit IIO which will exhaust to the reservoir I08 excessive pressure fluid by means of an exhaust conduit I26.
A back pressure valve, indicated by the numeral I28 is also incorporated in the pressure delivery conduit IIO ahead of which is connected a conduit I30 leading to the external port I0 in the housing member I8 of the device I0. The back pressure valve I28 may be of the type having a ball valve I32 biased to the closed position by a spring I34 which has a resistance predetermined by the difference in pressure required at the inner and outer ends of the vanes. A spring resistance may be provided, for example, of thirty pounds per square inch to maintain a differential pressure of thirty pounds per square inch between the inner and outer ends of the vanes as they pass through the fluid inlet zones.
For the purpose of convenience, the operation of the device will be described as a fluid motor, and as connected in a transmission as disclosed in Figure '7 although it should be understood that an auxiliary source of pressure fluid may be utilized and other means utilized for controlling the pressure of the fluid directed to the pressure chamber 68, and that the device may also be operated as a reversible fluid pump. It should also be noted that for the purpose of more clearly illustrating the construction and operation of the device that the fluid openings 48 and 50 have been shown in dotted lines in Figure 4 while the fluid openings 60 and 62 and the drilled passages 14, :16, E8, and 80 have been shown in dotted lines in Figure 6.
In operation, assuming that the directional control valve H4 is in a position connecting the pressure port II2 to the motor port H6, and the motor port II8 to the tank port I 23, pressure fluid is delivered from the pump I04 by means of conduit IIO to the control valve H4, and. from the control valve II4 to the external connection port 55 of the device I8. From the external connection port 56 fluid is delivered by the passage 54 to the fluid branches and 52 and through the fluid openings 48 and 50 to the fluid zones of the working chambers 44 and 46 registering therewith. Fluid pressure, acting on the outer ends of the vanes 22 in said zones, causes the rotor to be rotated in a clockwise direction as observed from the shaft end.
As the vanes pass over that portion of the working chamber, with which the fluid openings 60 and 62 register, fluid will be displaced to the external connection port II by means of the side plate fluid openings 60 and 82, drilled passages 6 I4 and I8, and I8 and 80, fluid channel 82, and the passage 69. From the external connection port II fluid is displaced to the reservoir I08 by means of conduit I22, motor port II8, tank port I23 of control valve II 4, and conduit I25. Simultaneously, with the conducting of pump fluid to the external connection port 56 of the motor I0, pressure fluid is also conducted by the conduit I30 to the external connection port 10 thereof, and to the pressure chamber 68. The pressure of the fluid conducted to the pressure chamber 68 will exceed that delivered to the fluid zones in registry with the fluid openings 48 and by an amount equal to the resistance of the spring I34 of the valve I28, which for example may be pre-set to establish a differential of thirty pounds per square inch. Due to the fact that the underside of the vane slots are in continuous communication with the pressure chamber 68 by means of the plurality of ports 84 in the side plate, and the rotor pressure channel 30 which registers with said ports, there will be a differential of thirty pounds per square inch between the pressure existing at the outer ends of the vanes passing through the inlet fluid zone and that existing at the inner ends of the vanes. Consequently, the outer ends of the vanes will be constantly maintained in contact with the vane track 20.
If the directional control valve I I4 is operated to reverse the directional operation of the device I0 pressure fluid from the pump I0 will be conducted by the conduits IIO and I22 to the ex ternal connection port II. Fluid displacement from the motor I0 will be conducted through the external connection port 56 to the reservoir I08 by means of conduit I20, ports H6 and I23 of control valve H4, and conduit I25. Pressure fluid delivered to the external port II from pump I04 is directed to the fluid zones of the working chambers registering with the arcuate fluid openings I4 and 16 by means of passage 69, fluid channel 82 in the side plate 64, by drilled passages M and I6 to the fluid opening 60, and by drilled passages I8 and 80 to the fluid opening 62. Pressure fluid acting against the outer ends of the vanes in the fluid zones registering with the openings and 62 will cause counterclockwise rotation of the rotor as observed from the pressure chamber end of the device.
As the vanes pass through the fluid zones regis tering with the arcuate openings 48 and 50 in the housing I6, fluid will be displaced therethrough and thence to the tank I08 by means of the branch passages 5| and 52, passage 54, external port 56, conduit I20, directional control valve ports II 6 and I23 and conduit I25. Regardless of the reversal of rotation of the device the same difierential pressure will exist at the inner and outer ends of the vanes. As the vanes pass through the fluid zones, which at the moment happen to be the fluid inlet zones, a lower pressure differential will exist than that existing between the inner and outer ends of the vanes passing over the fluid zones, which at the moment are fluid outlet zones because the latter are connected to the tank. However, a pressure is continually present at the inner ends of the vanes sufficient to maintain the outer ends of the vanes in contact with the vane track 20, and in particular, a suflicient differential in pressure may be maintained between the inner and outer ends of the vanes as they pass through the fluid zones, which at the moment happen to be a fluid inlet zone. I
Pressure fluid is conducted to the inner ends 7, of the vane slots in the same manner as described for the opposite direction of rotation.
It should. be noted that the side plate, when mounted in the recess of the housing member l3, aids in forming a pressure chamber which is isolated from the fluid inlet and outlet zones of the device. The side plate is so constructed that it will conduct pressure fluid from the isolated pressure chamber to the rotor pressure channel so as to maintain the outer ends of the vanes in contact with the vane track. The side plate is also so constructed that it will direct fluid in one instance from what is the outlet fluid zone of the device to an external connection port operating as an outlet port, while for reverse operation it will conduct fluid from the same external connection port operating as an inlet port to the aforementioned fluid zone, now functioning as an inlet fluid zone. This formation of the isolated pressure chamber makes it possible to simply and economically selectively control the pressure at the inner ends of the vanes. The device may also be efficiently utilized as a pump.
It should be further noted that the pressure fluid delivered to the isolated pressur chamber is also utilized for maintaining the side plate in fluid sealing engagement against the cam ring and the rotor.
While the form of embodiment of the invention as herein disclosed constitutes a preferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claims which-follow.
What is claimed is as follows:
1. A reversible, rotary fluid pressure energy translating device comprising a body forming a main fluid displacement chamber having a rotor therein to provide circumferentially spaced fluid displacement zones either of which may be a fluid receiving zone while the other is a fluid delivery zone, a first fluid passage in the body formed entirely on one side of the displacement chamber and connected to one of said zones, a second fluid passage in the body entirely on the opposite side of the displacement chamber and connected to the other zone, each of said passages having a connection port at the outside of the body, a pressure plate overlying said opposite side of the displacement chamber and rotor and forming with the body a pressure chamber for urgin the pressure plate toward the rotor, said pressure plate having means normally separating the said zones and the pressure chamber from each other, and means forming a separate fluid passage for supplying fluid under pressure to said pressure chamber.
2. A reversible, rotary fluid energy translating device comprising a stator having a. recess, a rotor mounted in the recess and forming two fluid displacement zones either of which may be a fluid inlet zone or a fluid outlet zone, a fluid passage in the stator completely on one side of the rotor, said passage having a connection port at the outside of the stator and leading to one of the fluid displacement zones, a second recess on the opposite side of the rotor immediately adjacent the first recess and having a greater periphery than the first recess to provide a shoulder forming a rigid abutment at one side of the rotor, a pressure responsive cheek plate slidably mounted in the second recess and forming therewith a pressure chamber, one side of the cheek plate being exposed to pressure in the chamber for maintaining the opposite side thereof in, fluid sealing engagement against the rigid abutment and the rotor, a second passage opening to the second recess at a point intermediate the rotor and the pressure chamber, said passage having a connection port at the outside of the stator, means forming a sliding fluid sealing contact with th walls of the second recess around the periphery of the cheek plate and between the pressure chamber and the opening of the second passage into the recess, and means connecting the second external connection port and passage with the other fluid displacement zone.
3. A reversible, rotary fluid pressure energy translating device comprisin a stator having a rotor mounted therein and forming fluid displacement zones either of which may be a fluid inlet zone While the other is a fluid outlet zone, means forming a recess in the stator adjacent the fluid displacement zones and including a rigid abutment, means forming two fluid passages in the stator one on each side of the rotor, each passage having a connection port at the outside of the stator, one passage being connected to one of the fluid zones and the other passage opening to the recess, a pressur plate slidably mounted in the recess and forming a pressure chamber, one side of the plate being exposed to pressure in the chamber for maintaining the opposite side of th plate in fluid sealing engagement against the abutment and the rotor, a flow passage in the pressure plate leading from the other fluid zone to the opening of the other fluid flow terminal passage, said pressure plate separating the zones and the pressure chamber from each other, and means forming a sliding fluid sealing contact with the walls of the recess around the periphery of the pressure plate and between the pressure chamber and the opening of the other fluid flow terminal passage into the recess.
l. A reversible rotary fluid pre ure energy translating device comprising a stator, rotor mounted in the stator and forming two fluid zones either of which may be a fluid n et zone while the other is a fluid outlet zone, a t passage in the stator completely on one side of the rotor and connected to one of said zones, said passage having a connection port at the outside of the stator, a recess in the stator on the opposite side of the rotor and formin rigid abutment immediately adjacent the rotor, a pressure plate slidably mounted in the recess and forming therewith a pressure cham er, one side of the pressure plate being exposed to pressure in the chamber for maintaining the opposite side thereof in fluid sealing engagement against the rigid abutment and the rotor, a second passage in the stator completely on the side of the rotor opposite to that of the first passage and opening to the recess at a point inte nediate the rotor and the pressure chamber, said passage having a connection port on the outside of the stator, a flow passage in the cheek plate leading from the other fluid zone to the opening of the second passage, and means forming a sliding fluid scaling contact with the walls of the recess around the periphery of the cheek plate and between the pressure chamber and the opening of the second passage into the recess.
5. A reversible rotary vane pump or motor comprising a housing having a working chamber, the contour of which forms a vane track, a slotted rotor in the chamber carrying a plurality of stantially radially movable vanes, the outer ends of which are adapted to be maintained in engagement with the vane track, said working chamber and rotor forming fluid zones adapted to be either inlet or outlet zones and through which the vanes pass as the rotor turns, a recess in the housing adjacent the working chamber and forming a rigid abutment to one side of the rotor, a pressure plate slidably mounted in the recess and forming a pressure chamber, said plate being maintained in fluid sealing engagement against the abutment and rotor by pressure fluid conducted to the chamber, means formin two terminal passages in the housing one on each side of the rotor, each passage having a connection port at the outside of the stator, one passage leading to one of the fluid zones and the other of which opens to the recess, a flow passage in the pressure plate leading from the other fluid zone to the opening of the other passage, said pressure plate separating the fluid zones and the pressure chamber from each other and separating the pressure chamber from the other passage, and a separate fluid passage for supplying fluid under pressure to the pressure chamber.
6. A reversible rotary vane pump or motor comprising a housing having a working chamber, the contour of which forms a vane track, a
slotted rotor in the chamber carrying a plurality I being maintained in fluid sealing engagement against the abutment and rotor by pressure fluid conducted to the chamber, means forming two terminal passages in the housing one on each side of the rotor, each passage having a connection port at the outside of the stator, one passage leading to one of the fluid zones and the other of which opens to the recess, a flow passage in the pressure plate leading from the other fluid zone to the opening of the other passage, said pressure plate separating the fluid zones and the pressure chamber from each other, means forming a sliding fluid sealing contact with the walls ofthe recess around the periphery of the pressure plate and between the pressure chamber and the opening of the other passage into the recess and a separate passage for supplying fluid under pressure to the pressure chamber.
DUNCAN B. GARDINER. ERNST F. KLESSIG. HENRY C. PARSONS.
References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 465,907 Whipple Dec. 29, 1891 1,010,956 Read Dec. 5, 1911 1,771,863 Schmidt July 29, 1930 1,989,900 Vickers Feb. 5, 1935 2,098,652 Buckbee Nov. 9, 1937 2,266,820 Smith Dec. 23, 1941 2,312,655 Lauck Mar. 2, 1943 2,312,891 Ferris Mar. 2, 1943 2,487,721 Minshall Nov. 8, 1949 2,525,619 Roth et a1 Oct. 10, 1950 2,544,988 Gardiner et a1 Mar. 13, 1951
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US2809595A (en) * 1954-01-26 1957-10-15 American Brake Shoe Co Pump casing construction
US2820417A (en) * 1954-05-10 1958-01-21 American Brake Shoe Co Fluid pressure energy translating device
US2884865A (en) * 1954-06-07 1959-05-05 Vickers Inc Power transmission
US2902943A (en) * 1955-10-05 1959-09-08 Superior Industries Rotary low pressure gas pump and method of operating the same
US2921535A (en) * 1956-09-17 1960-01-19 Clinton M Welch Fluid translating device
US2924182A (en) * 1955-08-31 1960-02-09 American Brake Shoe Co Fluid pressure energy translating device
US3057304A (en) * 1960-02-03 1962-10-09 Gen Motors Corp Vane pump
US3214940A (en) * 1963-01-08 1965-11-02 Thor Power Tool Co Impulse tool
US3238848A (en) * 1963-04-08 1966-03-08 Standard Pneumatic Motor Compa Pneumatic motor
US3713757A (en) * 1971-03-18 1973-01-30 Gen Motors Corp Hydraulic energy translating device
US4795325A (en) * 1981-10-30 1989-01-03 Hitachi, Ltd. Compressor of rotary vane type
US6481992B2 (en) 2000-02-11 2002-11-19 Delphi Technologies, Inc. Vane pump
US6599111B2 (en) * 2000-10-30 2003-07-29 Unisia Jecs Corporation Vane pump having an intake groove through a side wall member
US20080253913A1 (en) * 2005-09-30 2008-10-16 Christian Langenbach Vane Pump
US20090291010A1 (en) * 2004-12-16 2009-11-26 Achim Koehler Vane pump

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US2809595A (en) * 1954-01-26 1957-10-15 American Brake Shoe Co Pump casing construction
US2820417A (en) * 1954-05-10 1958-01-21 American Brake Shoe Co Fluid pressure energy translating device
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US2921535A (en) * 1956-09-17 1960-01-19 Clinton M Welch Fluid translating device
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US4795325A (en) * 1981-10-30 1989-01-03 Hitachi, Ltd. Compressor of rotary vane type
US6481992B2 (en) 2000-02-11 2002-11-19 Delphi Technologies, Inc. Vane pump
US6599111B2 (en) * 2000-10-30 2003-07-29 Unisia Jecs Corporation Vane pump having an intake groove through a side wall member
US20090291010A1 (en) * 2004-12-16 2009-11-26 Achim Koehler Vane pump
US7878779B2 (en) 2004-12-16 2011-02-01 Robert Bosch Gmbh Vane pump with housing end wall having an annular groove and a pressure groove that communicate via a curved connecting groove
US20080253913A1 (en) * 2005-09-30 2008-10-16 Christian Langenbach Vane Pump
US7845922B2 (en) * 2005-09-30 2010-12-07 Robert Bosch Gmbh Vane pump

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