US3343494A - Automatically reversible gear pump - Google Patents

Automatically reversible gear pump Download PDF

Info

Publication number
US3343494A
US3343494A US589150A US58915066A US3343494A US 3343494 A US3343494 A US 3343494A US 589150 A US589150 A US 589150A US 58915066 A US58915066 A US 58915066A US 3343494 A US3343494 A US 3343494A
Authority
US
United States
Prior art keywords
gear
port plate
shaft
port
pump
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US589150A
Inventor
Robert W Erikson
Swedberg Nils Einar
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sundstrand Corp
Original Assignee
Sundstrand Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sundstrand Corp filed Critical Sundstrand Corp
Priority to US589150A priority Critical patent/US3343494A/en
Application granted granted Critical
Publication of US3343494A publication Critical patent/US3343494A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/04Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for reversible machines or pumps
    • 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
    • F04C2/08Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/101Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member with a crescent-shaped filler element, located between the inner and outer intermeshing members

Definitions

  • This invention relates generally to hydraulic pumps for delivering uid under pressure and more particularly to a new and improved gear pump.
  • Another object of the present invention is to provide a new and improved reversible gear type pump of the type having a rotating outer gear driven by an input shaft and an inner gear meshing with the outer gear and eccentrically mounted with respect to the outer gear so that the expanding gear teeth spaces receive inlet fluid and the contracting gear spaces compress and discharge fluid from the pump.
  • An indexible port plate is provided adjacent the relatively rotating outer and inner gears. As the pump begins rotation in one direction torque is transmitted to the port plate, which carries the inner gear, so that the port plate indexes to a position where high pressure fluid ows through a port therein to a stationary outlet passage in a member adjacent the port plate. If the input shaft begins rotation in the opposite direction, torque is transmitted to the port plate, rotating it approximately 180 degrees from the position noted above so that high pressure fluid flows to the stationary outlet recess even though the drive shaft rotates in the opposite direction.
  • Another object of the present invention is to provide a new and improved gear pump of the type described in which the outer ring gear is separate from the input shaft so that the pumping elements may be connected to the input shaft as a unit.
  • the cylindrical drive sleeve mentioned above, which is connected to the ring gear, projects axially therefrom so that it may be tted over one end of the drive shaft and xed thereto and in this manner the input shaft drives the outer ring gear through the sleeve.
  • This provides a unitary and simplified gear pump which may be fitted over and aligned with respect to the drive shaft without concern for the Vaccurate alignment of the pumping elements with respect to other portions ofthe device.
  • a further ⁇ object of the present invention is to provide a new and improved gear pump of the type described above in which the input shaft is vertically disposed to increase the frictional force between the outer ring gear and the port plate to provide the necessary indexing force on the plate.
  • a still further object of the present invention is to provide a new and improved gear pump of the type described above particularly adapted for horizontal installations which includes a resilient spring means for biasing the port plate into engagement with the .ring gear so that the ring gear exerts a suicient frictional force on the port plate to assure proper indexing thereof.
  • Another object of the present invention is to provide a new and improved gear pump of the type described suitable for use with outer .and inner gears of either the well known crescent type or the gear rotor type in which no crescent is utilized.
  • a further object of the present invention is to provide an improved gear pump of the type described above with novel means for relieving excessive uid pressure.
  • FIG. 1 is a longitudinal section of a gear pump embodying the present invention on a vertical compressor shaft Within a reservoir in the compressor;
  • FIG. 2 is a cross-section, taken generally along line 2 2 of FIG. 1, showing eccentrically mounted gears and a crescent in the space between the gears;
  • FlG. 3 is a cross-section taken generally along line 3 3 yof FIG. 1 illustrating one face of the port plate;
  • FIG. 4 is a cross-section taken generally along line 4 4 of FIG. 1 showing one face of the cover plate;
  • FIG. 5 is a Ifragmentary view taken generally along line 5 5 in FIG. 1 showing the other side of the port plate;
  • FIG. 6 is a longitudinal section of another form of the present invention particularly suited for use with horizontal compressor shafts
  • FIG. 7 is an elevational view, partly in cross-section, of still another form of the invention with gear rotor type gears;
  • FIG. 8 is a longitudinal section of another form of the present invention.
  • FIG. 9 is a cross-section taken generally along line 9 9 in FIG. 8 showing one side of the cover plate; and FIG. 10 is a cross-section taken generally along line 10 10 of FIG. 8 showing the gear assembly.
  • a vertically disposed shaft 10 is the main drive shaft for a compressor, the details of which form no part of the present invention and are therefore not shown. Suffice it to state that the shaft 10 may be driven by a suitable three phaser electric motor.
  • a reservoir is located within thev compressor housing 11 and holds a suitable supply of lubricating uid for the various bearings in the compressor.
  • the present hydraulic gear pump generally designated by the numeral 14 is mounted on the outboard end of the compressor shaft 10.
  • Shaft 10 drives the pump 14 which draws fluid from withinrthe reservoir 11 and pumps fluid through a'central passage 15 in shaft 10 to the various bearing locations.
  • a generally cylindrical housing member 17 has a mounting ange 18 thereon adapted to be xed to a stationary portion of the compressor by suitable fastening means (not shown).
  • a bore 20 is provided in the upper end of the housing 17 for a bearing 21 which surrounds vthe outboard end of the input shaft 10.
  • the outboard end of the housing 17 has a bore 22 therein larger than and aligned with the bore 20.
  • a generally cylindrical cover plate or member 25 closes the housing 17, and defines stationary inlet and outlet ports for the gear pump, as shown in FIGS.V 1 and 4.
  • Suit-V able threaded fasteners 26 fix the cover plate 25 to the housing 17.
  • an inlet port 27 extends through the cover member 25 and is in constant communication with fluid in the reservoir 11.
  • a generally T-shaped outlet recess 28 is formed in the inside surface 29 of the cover member 25.
  • Recess 28 includes a central leg 30 symmetrical about the center of the cover member and a radially projecting leg 31.
  • a stop pin 33 is iixed Within the cover member 25 and extends inwardly towards the shaft 10 a short distance as shown in FIGS. 1, 4 and 5.
  • a generally cylindrical indexible port plate 35 is provided for maintaining the high pressure outlet of the pump 14 in communication with outlet recess 28.
  • two generally arcuate ports 37 and 38 are provided in the inwardly facing surface of the port plate 35.
  • Ports 37 and 38 may be either outletl or inlet ports depending upon the direction of rotation of input shaft 10.
  • Diametrically opposed passages 39 and 40 communicate with the ports 37 and 38, respectively, and extend through to the outward face of the port plate 35. Passages 39 and 40 are spaced from the center of the port plate 35 a distance to communicate with either inlet port 27 or the leg 31 of the outlet recess 28 in the cover member 25.
  • the port plate 35 has an outwardly facing peripheral recess 42 extending approximately 180 degrees plus the Width of the stop pin 33.
  • the recess 42 slidably receives the stop pin 33 so that, as shown in FIG. 5, the pin 33 will prevent counterclockwise movement of the port plate 35k beyond the position shown.
  • pin 33 Upon clockwisel rotation of the port plate 35, pin 33 will prevent rotation of the port plate beyond the positionrwhere the passages 39 and 40 are reversed as shown in broken lines in FIG. 3.
  • a hollow shaft 44 is xed within and extends through the port plate 35 projecting therefrom to the outboard end of the input shaft 10.
  • the interior of the hollow shaft 44 continuously communicates with the elongated leg 30 of the outlet recess 28 and the passage 15 in the drive shaft 10. Note that the axis of shaft 44 is spaced fromV the axis of the input shaft 10 so that depending upon the indexed position of the port plate 35, the interior'of shaft 44 will be aligned with either the upper or the lowerend of the recess leg 30 in the cover member 25.
  • An outer ring ygear 46 is provided with inwardly di- Y rected spaced teeth 47.
  • Gear 46 is symmetrical about the axis of rotation of input shaft 10 and is driven thereby by a cylindrical drive sleeve 49 surrounding and engaging the outboard end of the input'shaft 10,'the periphery of the outer ring gear 46, and a portion of the indexible port plate 35.
  • Sleeve 49 is pinned to the input Vshaft 10 and fixed by suitable means to the ring gear 46 so that the outer gear is driven continuously by shaft 10.
  • Sleeve 49 slidably engages the periphery of the port plate 35 to support the same and to assist in indexing the port plate.
  • Ring gear 46 has a radial surface 51 which frictionally engages the inward face of the port plate 35 to also assist in indexing the port plate. It should be understood that the indexing of the port plate 35 occurs only during pump starting and that during normal running operation the port plate 35 remains stationary ⁇ and the ring gear 46 and the drive sleeve 49 rotate with respect to the port plate 35.
  • the bore 22 in the housing is spaced from the sleeve 49 so that it does not retard rotation of the sleeve or the indexing of the port plate 35.
  • An internal pinion or gear 53 is rotatably mounted on the hollow shaft 44 and has outwardly extending teeth 54 meshing with the teeth 47 on the outer gear 46 asY shown in FIGS. l and 2.
  • low pressure fluid will be drawn in from port 37 in the valve plate and carried by the spaces be tween the gears which in association with the crescent 56 define chambers, to the contracting area of the gears adjacent the port 38 where the fluid is compressed and discharged through the port.
  • the pump 14 may be mounted on the outboard end of' the compressor shaft 10 without maintaining an accurate alignment between the port plate 35 or the gears withY the stationary cover member 2,5 which defines the stationary outlet port.
  • the indexible port i plate 35 andthe gears 46 and 53 may be fitted as an aligned unit onV the end of the compressor shaft simply by fitting the drive sleeve 49 over the shaft and fixing it thereto. Thisserves to align not only the ring gear 46 with respect to the shaft, but also the port plate 35 so that during indexing thereof it rotates about the axis of shaft 10. Small misalignmentsv between the port plate 35V S and the inlet and outlet ports in the cover member 25 do not adversely affect the operation of the pump.
  • port 7 and passage 39 communicate with inlet port 27 and the diverging or expanding spaces between the gears 46 and 53.
  • High pressure uid from the converging spaces which are approximately diametrically opposed to the diverging spaces as shown in FIG. 2, pass through port 38, outlet passage 40 and into the outlet recess 28.
  • High pressure fluid in the outlet recess 28 flows through the hollow shaft 44 and into the axial passage 15 in the compressor shaft 10 to the various bearing locations for lubrication thereof.
  • the present device maintains a unidirectional output through a stationary outlet passage by effectively indexing the gears and port plate so that the high pressure and low pressure ports in the valve plate always communicate respectively with the outlet and the inlet ports in a stationary port member regardless of the direction of rotation of the pump input shaft.
  • FIG. 6 a gear pump of the type described adapted to be driven by a horizontally oriented compressor drive shaft.
  • a pump housing 18 is provided similar in construction to the housing 17 except that it has an axial extension 60 with a counterbore 22 therein.
  • a radial inlet passage 62 extends through the housing 6 18 and is adapted to carry low pressure fluid to the pump 14.
  • a non-rotatable, axially slidable valve member is provided in bore 22'.
  • a stop pin 33' fixed within the valve member 25', slides within the recess 42 in the indexible valve plate 35 in the same manner as in the pump 14.
  • the stop pin 33 performs the additional function of preventing rotation of the valve member 25' without retarding its axial movement.
  • pin 33 slides within an axial groove 61 in the bottom of bore 22.
  • the cover plate 63 encloses the pump and is fixed to the open end of housing member 18' by suitable threaded fasteners 65.
  • a tapered compression spring 66 engages the inside surface of the cover 63 and is seated at its other end in a central recess in valve member 25. In this manner the valve member 25 is continuously urged into engagement with the face of the indexible port plate 35. If the pump 14' develops an excessive fluid pressure, the force of hydraulic uid acting against valve member 25 will move it slightly axially against the force of compression spring 66 permitting iiuid leakage between the valve member and the face of the port plate 35, thus relieving the excessive pressure. Fluid leakage may also occur due to separation between the port plate and the gears or between the gears and the input shaft, and in these instances the high and low pressure chambers are short circuited.
  • FIG. 6 embodiment The operation of the FIG. 6 embodiment is the same as that of the FIGS. l to 5 embodiment, except that the frictional indexing force of gear face 51 on the indexible port plate 35 and the sealing engagement between the parts is produced as a result of the biasing effect of spring 66. In this manner the present device is usable as well in horizontal installations.
  • the outer gear member 70 When used in the present pumping device, the outer gear member 70 would be driven by the cylindrical drive sleeve 49 in the same manner as outer ring gear 46.
  • the inner gear 71 would be rotatably mounted on pinion shaft 44 in the same manner as inner gear 53.
  • the operation of the gear rotor pump would be substantially the same as that described above.
  • the pump 114 is seen to include a housing member 118 forming part of the housing of an associated compressor having a sleeve bearing 121 supporting the outboard end of compressor shaft 110.
  • Shaft has a suitable center bore 115 which serves as the outlet passage for the pump in either direction of rotation.
  • the housing member 118 has a central recess 122 for receiving the pumpingy elements and an inlet passage 162 communicating with the recess.
  • a cover member 125 is fixed to the recessed end of the housing 118, andy has formed therein a chamber-'127 kcommunicating with recess 122 and inlet passage 162.
  • Chamber 1 27 extends radially and communicates with an arcuatel inlet portY 127A also formed in the cover 125.
  • port 127A Opposite the port 127A (which is a low pressure port) is an arcuate port 128 which is a high pressure port in the cover 125.k Port 128 continuously communicates with a radial passage or recess 131 which communicates continuously withthe outlet passage 115 in the shaft 110.
  • the outer gear is somewhat lar-ger than the outer diameter of shaft 110 so that a suitable annular adapter 149A is provided fixed to shaft 110 and sleeve 149 by radially extending key pins 150.
  • outlet recess in said cover member in continuous communication with the interior of said hollow shaft, said outlet recess extending radially in said cover member to selectively communicate with said arcuate ports in said port plate, an inlet passage in said cover member located to selectively communicate with the arcuate ports in said Vport plate, whereby inlet uid enters through said inlet passage and passes through one of said arcuate ports, and high vpressure outlet liuid passes through one of saidy arcuate ports, into said outlet recess, through said hollow shaft and out said input shaft passage regardless of they direction of rotation of said inputvshaft.
  • said Y outer ring gear is separatefrom said in-put shaft and llasV an outer Ydiameter substantially equalV to the input shaft diameter, a cylindrical sleeve surrounding a portion ofsaid input shaft and said outer ring gear, said sleeveVY being -xed to said input shaft and said gear t-o transfer Y torque therebetween, said sleeve extending around a portion of said port plate and supporting said plate for rotation about the axis of said input shaft, said sleeve slidable Vand frictionally engaging Vsaid port plate so that the sleeve indexes said port plate,y a housing surrounding said gears and port plate, said cover member being fixed to said k housing member, the inner surface of said housing being spaced from said sleeve Iand port plate so that the port plate may be readily indexed.
  • a gear pump comprising: an input shaft adapted to be rotated about an axis, an outer gear driven by said inputY shaft, an inner gear meshing with said outer gear and rotatable about an axis spaced from said input shaft axis, anV indexible port plate adjacent said gears having ports therein adapted to convey uid to and from, said gears, said inner gear axis being fixed with respect to said ⁇ port plate, a relativel stationary port member having inlet and outlet ports therein adapted to selectively communicate with said indexible ports to maint-ain a unidirectional pump output irrespective of the direction of rotation of said input shaft, means separate from said stationary port member for supporting said port plate for rotation about the input shaft axis to assure the propel alignment therebetween, said outer ring gear being separate from said input shaft, and mean-s for connecting and aligning said outer ring to said shaft whereby the port plate, the inner gear, and the outer gear may be connected as a unit and aligned with respect to the input shaft.
  • a combination as defined in claim 4 wherein said means for relieving excessive pressure in said outlet port includes a resiliently biased sealing plate between the end of said input shaft and said gears.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Description

sept. 26 1957 R. w. ERlKsoN ETAL 3,343,494
AUTOMATICALLY REVERSIBLE GEAR PUMP Filed Sept. l2, 1966 5 Sheets-Sheet l l l l g A e 20 1| ,lvl 2i g Q9 J8 v' I l v' l l L 56pm J7 1 E 2, 3- x z VL Sept. 26, 1967 R. w. ERIKSON mp 3,343,494
AUTOMATICALLY REVERSIBLE GEAR PUMP Filed Sept. 12, 1966 3 Sheets-Sheet 2 LUC' SCP- 25, 1967 R. w. ERxKsoN ETAL 3,343,494
AUTOMATICALLY REVERSIBLE GEAR PUMP 3 Sheets-Sheet s Filed Sept. 12, 1966 United States Patent O M 3,343,494 AUTOMATICALLY REVERSIBLE GEAR PUMP Robert W. Erikson and Nils Einar Swedberg, Rockford,
Ill., assignors to Snndstrand Corporation, a corporation of Illinois Filed Sept. 12, 1956, Ser. No. 589,150 7 Claims. (Cl. 10S-126) This application is a continuation-in-part of our copending application Ser. No. 455,217, iiled May 12, 1965, now abandoned.
This invention relates generally to hydraulic pumps for delivering uid under pressure and more particularly to a new and improved gear pump.
In compressor units a small pump is conventionally provided for supplying lubricating fluid to the various bearings in the compressor. These lubricating pumps are connected in some manner to be driven by the compressor drive shaft. This drive shaft is usually driven by a three phase electric motor. In the installation of such compressors the direction of rotation of the three phase motor and hence the compressor drive shaft, depends upon how the installing electrician connects the motor to the available source. lt has been found difcult for the electrician to connect the motor so that the compressor drive shaft and the lubricating :pump rotate in the same direction in all installations. For this reason automatically reversible lubricating pumps have been provided for pumping liuid out the same outlet passage regardless of the direction of rotation of the pump input shaft.
It is a primary object of the present invention to provide a new and improved gear type pump which maintains a unidirectional output ilow regardless of the direction of rotation of input shaft.
Another object of the present invention is to provide a new and improved reversible gear type pump of the type having a rotating outer gear driven by an input shaft and an inner gear meshing with the outer gear and eccentrically mounted with respect to the outer gear so that the expanding gear teeth spaces receive inlet fluid and the contracting gear spaces compress and discharge fluid from the pump. An indexible port plate is provided adjacent the relatively rotating outer and inner gears. As the pump begins rotation in one direction torque is transmitted to the port plate, which carries the inner gear, so that the port plate indexes to a position where high pressure fluid ows through a port therein to a stationary outlet passage in a member adjacent the port plate. If the input shaft begins rotation in the opposite direction, torque is transmitted to the port plate, rotating it approximately 180 degrees from the position noted above so that high pressure fluid flows to the stationary outlet recess even though the drive shaft rotates in the opposite direction.
It is a further object of the present invention to provide a new and improved gear pump of the type described above in which the indexing torque is applied to the port plate partly by the engagement therewith by the rotating outer ring gear, and partly by a drive sleeve connected to the ring gear and frictionally engaging a portion of the periphery of the port plate. The cooperation of the frictional engagement of the outer gear and the cylindrical drive sleeve with the port plate assures the proper indexing of the plate. Stops are provided for limiting the indexing movement of the valve plate t-o approximately 180 degrees so that the ports therein and the pinion carried thereby reverse if the direction of rotation of the input shaft reverses.
A still further object of the present invention is to provide a new and improved gear pump of the type described above in which the inlet and outlet ports are axially disposed. In this manner the pump may be constructed so Patented Sept. 26, 1967 ICC that it fits on the compressor shaft as a unit with all parts aligned with respect to the input shaft. This has a decided advantage over radial porting gear pumps in that it is unnecessary to accurately align the port plate with respect to the surrounding housing member which in a radial pump would conventionally include the stationary inlet and outlet ports.
Another object of the present invention is to provide a new and improved gear pump of the type described in which the outer ring gear is separate from the input shaft so that the pumping elements may be connected to the input shaft as a unit. The cylindrical drive sleeve mentioned above, which is connected to the ring gear, projects axially therefrom so that it may be tted over one end of the drive shaft and xed thereto and in this manner the input shaft drives the outer ring gear through the sleeve. This provides a unitary and simplified gear pump which may be fitted over and aligned with respect to the drive shaft without concern for the Vaccurate alignment of the pumping elements with respect to other portions ofthe device.
A further `object of the present invention is to provide a new and improved gear pump of the type described above in which the input shaft is vertically disposed to increase the frictional force between the outer ring gear and the port plate to provide the necessary indexing force on the plate.
A still further object of the present invention is to provide a new and improved gear pump of the type described above particularly adapted for horizontal installations which includes a resilient spring means for biasing the port plate into engagement with the .ring gear so that the ring gear exerts a suicient frictional force on the port plate to assure proper indexing thereof.
Another object of the present invention is to provide a new and improved gear pump of the type described suitable for use with outer .and inner gears of either the well known crescent type or the gear rotor type in which no crescent is utilized.
A further object of the present invention is to provide an improved gear pump of the type described above with novel means for relieving excessive uid pressure.
Other and further objects of the present invention will be readily apparent from the following detailed description taken in connection with accompanying drawings, in which:
FIG. 1 is a longitudinal section of a gear pump embodying the present invention on a vertical compressor shaft Within a reservoir in the compressor;
FIG. 2 is a cross-section, taken generally along line 2 2 of FIG. 1, showing eccentrically mounted gears and a crescent in the space between the gears;
FlG. 3 is a cross-section taken generally along line 3 3 yof FIG. 1 illustrating one face of the port plate;
FIG. 4 is a cross-section taken generally along line 4 4 of FIG. 1 showing one face of the cover plate;
FIG. 5 is a Ifragmentary view taken generally along line 5 5 in FIG. 1 showing the other side of the port plate;
FIG. 6 is a longitudinal section of another form of the present invention particularly suited for use with horizontal compressor shafts;
FIG. 7 is an elevational view, partly in cross-section, of still another form of the invention with gear rotor type gears;
FIG. 8 is a longitudinal section of another form of the present invention;
FIG. 9 is a cross-section taken generally along line 9 9 in FIG. 8 showing one side of the cover plate; and FIG. 10 is a cross-section taken generally along line 10 10 of FIG. 8 showing the gear assembly.
VWhile illustrative embodiments of the present invention are shown and described in detail herein it should be understood that the present invention'is susceptible of embodiment in many different forms and that the embodiments'illustrated are to be consideredan exemplifica- Vtion of the principles of the invention and are not intended to` limit the invention thereto. The scope of the invention will be pointed. out in the appended claims.
Referring to the drawings and particularly to FIG. l, a vertically disposed shaft 10 is the main drive shaft for a compressor, the details of which form no part of the present invention and are therefore not shown. Suffice it to state that the shaft 10 may be driven by a suitable three phaser electric motor. A reservoir is located within thev compressor housing 11 and holds a suitable supply of lubricating uid for the various bearings in the compressor.
The present hydraulic gear pump generally designated by the numeral 14 is mounted on the outboard end of the compressor shaft 10. Shaft 10 drives the pump 14 which draws fluid from withinrthe reservoir 11 and pumps fluid through a'central passage 15 in shaft 10 to the various bearing locations. A generally cylindrical housing member 17 has a mounting ange 18 thereon adapted to be xed to a stationary portion of the compressor by suitable fastening means (not shown). A bore 20 is provided in the upper end of the housing 17 for a bearing 21 which surrounds vthe outboard end of the input shaft 10. The outboard end of the housing 17 has a bore 22 therein larger than and aligned with the bore 20.
A generally cylindrical cover plate or member 25 closes the housing 17, and defines stationary inlet and outlet ports for the gear pump, as shown in FIGS.V 1 and 4. Suit-V able threaded fasteners 26 fix the cover plate 25 to the housing 17. As shown more clearly in FIG. 4 an inlet port 27 extends through the cover member 25 and is in constant communication with fluid in the reservoir 11. A generally T-shaped outlet recess 28 is formed in the inside surface 29 of the cover member 25. Recess 28 includes a central leg 30 symmetrical about the center of the cover member and a radially projecting leg 31. As will appear more clearly hereinafter fluid flows from the reservoir through inlet port 27 to the pump and from the pump through outletrecess 2.8 regardless of the direction of rotation of input shaft 10. A stop pin 33 is iixed Within the cover member 25 and extends inwardly towards the shaft 10 a short distance as shown in FIGS. 1, 4 and 5.
A generally cylindrical indexible port plate 35 is provided for maintaining the high pressure outlet of the pump 14 in communication with outlet recess 28. AS shown in solid lines in FIG. 3, two generally arcuate ports 37 and 38 are provided in the inwardly facing surface of the port plate 35. Ports 37 and 38 may be either outletl or inlet ports depending upon the direction of rotation of input shaft 10. Diametrically opposed passages 39 and 40 communicate with the ports 37 and 38, respectively, and extend through to the outward face of the port plate 35. Passages 39 and 40 are spaced from the center of the port plate 35 a distance to communicate with either inlet port 27 or the leg 31 of the outlet recess 28 in the cover member 25.
As shown more clearly in FIG. the port plate 35 has an outwardly facing peripheral recess 42 extending approximately 180 degrees plus the Width of the stop pin 33. The recess 42 slidably receives the stop pin 33 so that, as shown in FIG. 5, the pin 33 will prevent counterclockwise movement of the port plate 35k beyond the position shown. Upon clockwisel rotation of the port plate 35, pin 33 will prevent rotation of the port plate beyond the positionrwhere the passages 39 and 40 are reversed as shown in broken lines in FIG. 3.
A hollow shaft 44 is xed within and extends through the port plate 35 projecting therefrom to the outboard end of the input shaft 10. The interior of the hollow shaft 44 continuously communicates with the elongated leg 30 of the outlet recess 28 and the passage 15 in the drive shaft 10. Note that the axis of shaft 44 is spaced fromV the axis of the input shaft 10 so that depending upon the indexed position of the port plate 35, the interior'of shaft 44 will be aligned with either the upper or the lowerend of the recess leg 30 in the cover member 25.
An outer ring ygear 46 is provided with inwardly di- Y rected spaced teeth 47. Gear 46 is symmetrical about the axis of rotation of input shaft 10 and is driven thereby by a cylindrical drive sleeve 49 surrounding and engaging the outboard end of the input'shaft 10,'the periphery of the outer ring gear 46, and a portion of the indexible port plate 35. Sleeve 49 is pinned to the input Vshaft 10 and fixed by suitable means to the ring gear 46 so that the outer gear is driven continuously by shaft 10. Sleeve 49 slidably engages the periphery of the port plate 35 to support the same and to assist in indexing the port plate. Ring gear 46 has a radial surface 51 which frictionally engages the inward face of the port plate 35 to also assist in indexing the port plate. It should be understood that the indexing of the port plate 35 occurs only during pump starting and that during normal running operation the port plate 35 remains stationary `and the ring gear 46 and the drive sleeve 49 rotate with respect to the port plate 35.
The bore 22 in the housing is spaced from the sleeve 49 so that it does not retard rotation of the sleeve or the indexing of the port plate 35.
An internal pinion or gear 53 is rotatably mounted on the hollow shaft 44 and has outwardly extending teeth 54 meshing with the teeth 47 on the outer gear 46 asY shown in FIGS. l and 2. As the pinion or roller gear 53 Y tion in this type of pump of sealing -the low pressure area 0r spaces from the high pressure area. As shown in FIG. 2 and assuming that ring gear 46 is rotating in a clock- Wise direction, low pressure fluid will be drawn in from port 37 in the valve plate and carried by the spaces be tween the gears which in association with the crescent 56 define chambers, to the contracting area of the gears adjacent the port 38 where the fluid is compressed and discharged through the port. If an excessive nid pressure is developed in the contracting lluidV chambers between the gears 46 and 53, the hydraulic force acting. between the port plate 35 and cover member 25 will lift the port plate slightly (the play in shaft 10 permits the upward movement) from sealing engagement with the cover plate 25 permitting nid to escape into the low pressure bore 22, thus relieving the excessive pressure. Fluidy leakage may also occur due to separation between the gears and the port plate or the gears and the input shaft, and in these instances the high and low pressure chambers between the gears are short circuited.
One of the advantages of the present device is that the pump 14 may be mounted on the outboard end of' the compressor shaft 10 without maintaining an accurate alignment between the port plate 35 or the gears withY the stationary cover member 2,5 which defines the stationary outlet port. More particularly, the indexible port i plate 35 andthe gears 46 and 53 may be fitted as an aligned unit onV the end of the compressor shaft simply by fitting the drive sleeve 49 over the shaft and fixing it thereto. Thisserves to align not only the ring gear 46 with respect to the shaft, but also the port plate 35 so that during indexing thereof it rotates about the axis of shaft 10. Small misalignmentsv between the port plate 35V S and the inlet and outlet ports in the cover member 25 do not adversely affect the operation of the pump.
While the operation of the present device as shown in FIGS. 1 to 5 is believed clear from the description above, it may be helpful to review the automatic reversal on clockwise and counterclockwise rotation of the input shaft 10. Assume iirst that the input shaft 10 begins rotation in a clockwise direction as viewed in FIG. 3. The vertically disposed shaft 10 through the sleeve 49 begins rotating the outer ring gear 46. At the same time the frictional engagement of sleeve 49 with the periphery of the port plate 35 and the frictional engagement of radial surface 51 of ring gear 46 with the radial surface of port plate 35 serve to index the port plate in a clockwise direction until the end of recess 42 engages the pin 33, which serves to stop the port plate in the position shown in FIGS. l, 3 and 5. It should be noted that the weight of the vertical shaft 10 on the ring gear 46 provides frictional force between the face 51 and the valve plate to aid proper indexing and to prevent axial separation between the port plate and the cover, the port plate and the gears, and the gears and the input shaft, in the embodiment shown in FIGS. l to 5. In this position, port 7 and passage 39 communicate with inlet port 27 and the diverging or expanding spaces between the gears 46 and 53. High pressure uid from the converging spaces, which are approximately diametrically opposed to the diverging spaces as shown in FIG. 2, pass through port 38, outlet passage 40 and into the outlet recess 28. High pressure fluid in the outlet recess 28 flows through the hollow shaft 44 and into the axial passage 15 in the compressor shaft 10 to the various bearing locations for lubrication thereof.
On the other hand assume that during installation the -motor driving the compressor shaft 10 is connected to rotate the shaft in a counterclockwise direction as viewed in FIG. 3. Also assume that the various pump parts are initially in the positions shown in FIGS. 1 to 5 at rest. Shaft 10 through the drive sleeve 49 lbegins rotating the outer gear 46 about the axis of shaft 10. At the same time the outer gear 46 and the sleeve 49 frictioually engage the valve plate 35 and rotate it in a counterclockwise direction until the stop 33 abuts the opposite end of the recess 42, thereby stopping the valve plate 35. The valve plate then assumes the position shown in dotted lines in FIG. 3. Note that during this indexing movement of the valve plate that the pinion shaft 44 and the crescent 56 also index 180 degrees, as they are fixed to the port plate 35. Fluid then enters the pump through inlet port 27 in the cover plate 25 but now ows to the expanding gear spaces through port 38 in the valve plate which is then aligned with the inlet port 27. High pressure fluid owing from the gears passes through port 37 in the valve plate and into the recess 28, the leg portion 31 of which is then aligned with passage 39. High pressure fluid in recess 28 flows through the hollow shaft 44 and passage 15 in shaft 10 in the same manner as in the clockwise operation described above.
In this manner the present device maintains a unidirectional output through a stationary outlet passage by effectively indexing the gears and port plate so that the high pressure and low pressure ports in the valve plate always communicate respectively with the outlet and the inlet ports in a stationary port member regardless of the direction of rotation of the pump input shaft.
In some installations it is desirable to provide a gear pump of the type described adapted to be driven by a horizontally oriented compressor drive shaft. Such a pump is shown in FIG. 6 incorporating the principles of the present invention. The parts in FIG. 6 which are the same as the parts in FIGS. l to are designated with like reference numerals. A pump housing 18 is provided similar in construction to the housing 17 except that it has an axial extension 60 with a counterbore 22 therein. A radial inlet passage 62 extends through the housing 6 18 and is adapted to carry low pressure fluid to the pump 14. In place of the stationary cover member 25 in the FIGS. l to 5 embodiment, a non-rotatable, axially slidable valve member is provided in bore 22'. A stop pin 33', fixed within the valve member 25', slides within the recess 42 in the indexible valve plate 35 in the same manner as in the pump 14. The stop pin 33 performs the additional function of preventing rotation of the valve member 25' without retarding its axial movement. For this purpose pin 33 slides within an axial groove 61 in the bottom of bore 22.
The cover plate 63 encloses the pump and is fixed to the open end of housing member 18' by suitable threaded fasteners 65. A tapered compression spring 66 engages the inside surface of the cover 63 and is seated at its other end in a central recess in valve member 25. In this manner the valve member 25 is continuously urged into engagement with the face of the indexible port plate 35. If the pump 14' develops an excessive fluid pressure, the force of hydraulic uid acting against valve member 25 will move it slightly axially against the force of compression spring 66 permitting iiuid leakage between the valve member and the face of the port plate 35, thus relieving the excessive pressure. Fluid leakage may also occur due to separation between the port plate and the gears or between the gears and the input shaft, and in these instances the high and low pressure chambers are short circuited.
The operation of the FIG. 6 embodiment is the same as that of the FIGS. l to 5 embodiment, except that the frictional indexing force of gear face 51 on the indexible port plate 35 and the sealing engagement between the parts is produced as a result of the biasing effect of spring 66. In this manner the present device is usable as well in horizontal installations.
In some installations it may =be desirable to eliminate the inner gear support shaft 44 in both the FIGS. 1 and 6 embodiments, particularly when the pump application requires low discharge pressures. In such a case, the inner gear 53 would be supported and float between the outer gear 46 and the crescent 56. Discharge fluid from the pump would ow through a central bore in the inner gear and a complementary bore in the port plate 35, rather than through hollow shaft 44.
It should be understood that the principles of the present invention are applicable not only to crescent-type gear pumps such as shown in FIGS. 1 to 6, but also to gear rotor pumps of the type in which the inner and outer gear teeth are in sliding contact over the non-meshing arc of the gears. The outer and inner gear elements 70 and 71 respectively of such a gear rotor are shown in FIG. 7. In a gear rotor as opposed to a crescent pump, the gear teeth are elongated and shaped so that the engagement between the outer and inner gear teeth provide the neces- Sary sealing between the low and high pressure sides of the pump. No crescent is necessary in this type of pump. When used in the present pumping device, the outer gear member 70 would be driven by the cylindrical drive sleeve 49 in the same manner as outer ring gear 46. The inner gear 71 would be rotatably mounted on pinion shaft 44 in the same manner as inner gear 53. The operation of the gear rotor pump would be substantially the same as that described above.
The hydraulic unit shown in FIGS. 8 to 10 is generally Y similar in construction and operation to those described above except for the provision of a separate resiliently brilased sealing plate between the gears and the compressor s aft.
The pump 114 is seen to include a housing member 118 forming part of the housing of an associated compressor having a sleeve bearing 121 supporting the outboard end of compressor shaft 110. Shaft has a suitable center bore 115 which serves as the outlet passage for the pump in either direction of rotation. The housing member 118 has a central recess 122 for receiving the pumpingy elements and an inlet passage 162 communicating with the recess. A cover member 125 is fixed to the recessed end of the housing 118, andy has formed therein a chamber-'127 kcommunicating with recess 122 and inlet passage 162. Chamber 1 27 extends radially and communicates with an arcuatel inlet portY 127A also formed in the cover 125. Opposite the port 127A (which is a low pressure port) is an arcuate port 128 which is a high pressure port in the cover 125.k Port 128 continuously communicates with a radial passage or recess 131 which communicates continuously withthe outlet passage 115 in the shaft 110.
Fixed to the end of shaft 110k are pumping elements,
similar to that shownV in the FIG. 7 embodiment includ-. ing sleeve 149, outer gear 70, inner gear 71, port plate 135 andy hollow shaft 144. Pin 133'is mounted in cover plate 125 and limits indexing movement of the port plate, 135 in a manner similar to that described above with the other embodiments.
In the FIGS. 8 to l() embodiment, the outer gear is somewhat lar-ger than the outer diameter of shaft 110 so that a suitable annular adapter 149A is provided fixed to shaft 110 and sleeve 149 by radially extending key pins 150.
This embodiment is also somewhat different from the others in that the gear elements are spaced from the end of compressor shaft 11,0 and a sealing p late 160 is located therebetween with one face thereof sealingly engaging the gears 70 and 71. Shaft 110 has a counterbore 162 in the end thereof receiving a coiled compression spring 163 which biases a hollow piston 164 against the sealing plate 16,0, thus urging the plate against the gears and maintaining sealing engagement between the parts. If an excessive iuid pressure develops in the outlet of the pump, i.e. passage 131 and hollow shaft 144, fluid pressure acting against .piston 144 and plate 160 will urge the sealing plate away from the gears against the force of spring 163 permitting uid to leak between the plate and the gears and into the low pressure recess 122 through slot 166 in shaft 110 and also between high and low pressure liuidl chambers.
The operation of the embodiment of FIGS. 8 to 10 is substantially the same as that described above with reference to FIGS. l to 7'.
It should be understood that the present invention is not limited to use with a compressor and finds applicability in many types of rotating machinery.
We claim:
1. In a gear pump, the combination comprising: an input Shaft rotatable uabout an axis, an outer ring gear adjacent one end of said input shaft and driven thereby, an indexible port plate slidably engaging said outer ring gear and having two generally arcuate ports extending axially therethrough, said port plate having an arcuate recess in the periphery thereof extending substantially 180 degrees, a hollow shaft mounted in said port plate and extending within said ring gear, said hollow shaft having an axis spaced from said input shaft axis, an inner pinion gear mounted for rotation'on said hollow shaftV and meshing with said outer ring gear, a passage in said input shaft communicating with the interior of said hollow shaft adapted to convey uid fromy the pump, a relatively stationary cover member engaging one side of said port plate, a projection on said cover member extending into said port plate recess for limiting the indexing movement thereof whereby when the input shaft rotates the port plate,V the hollow shaft and inner gear rotate approximately 180 .degrees to reverse the location of the arcuate ports, -an
outlet recess in said cover member in continuous communication with the interior of said hollow shaft, said outlet recess extending radially in said cover member to selectively communicate with said arcuate ports in said port plate, an inlet passage in said cover member located to selectively communicate with the arcuate ports in said Vport plate, whereby inlet uid enters through said inlet passage and passes through one of said arcuate ports, and high vpressure outlet liuid passes through one of saidy arcuate ports, into said outlet recess, through said hollow shaft and out said input shaft passage regardless of they direction of rotation of said inputvshaft.
2. A combination as defined in claim 1, wherein said Y outer ring gear is separatefrom said in-put shaft and llasV an outer Ydiameter substantially equalV to the input shaft diameter, a cylindrical sleeve surrounding a portion ofsaid input shaft and said outer ring gear, said sleeveVY being -xed to said input shaft and said gear t-o transfer Y torque therebetween, said sleeve extending around a portion of said port plate and supporting said plate for rotation about the axis of said input shaft, said sleeve slidable Vand frictionally engaging Vsaid port plate so that the sleeve indexes said port plate,y a housing surrounding said gears and port plate, said cover member being fixed to said k housing member, the inner surface of said housing being spaced from said sleeve Iand port plate so that the port plate may be readily indexed.
3. In a gear pump, the combination comprising: an input shaft adapted to be rotated about an axis, an outer gear driven by said inputY shaft, an inner gear meshing with said outer gear and rotatable about an axis spaced from said input shaft axis, anV indexible port plate adjacent said gears having ports therein adapted to convey uid to and from, said gears, said inner gear axis being fixed with respect to said` port plate, a relativel stationary port member having inlet and outlet ports therein adapted to selectively communicate with said indexible ports to maint-ain a unidirectional pump output irrespective of the direction of rotation of said input shaft, means separate from said stationary port member for supporting said port plate for rotation about the input shaft axis to assure the propel alignment therebetween, said outer ring gear being separate from said input shaft, and mean-s for connecting and aligning said outer ring to said shaft whereby the port plate, the inner gear, and the outer gear may be connected as a unit and aligned with respect to the input shaft.
4. A combination as defined in claim 3, and further including means for relieving excessive pressure in said outlet port.
`5. A combination as defined in claim 4 wherein said means for relieving excessive pressure in said outlet port includes a resiliently biased sealing plate between the end of said input shaft and said gears.
6. Ina gear pump the combination comprising: an outer gear member, .sleeve means su-rronnding and xed to said outer gear member and extending axially therefrom, means for rotatably fixing said sleeve means around an input shaft so that the gear pump is aligned therewith, an indexible plate adjacent said outer gear, said sleeve means extending axially from said outer gear around said indexible plate for radially supporting the same, said sleeve fric-. tionally engaging said plate, an inner gear meshing with said outer gear and mounted for rotation about an axis spaced from the axis of said outer gear, means for maintaining the axis for rotation of said inner gear stationary with respect to said indexibleV plate, said inner and outer gears defining upon relative rotation therebetween expanding and contracting fluid chambers, inlet port means for conveying liuid to the expanding fluid chambers, outlet port means for conveying liuid from the contracting fluid chambers, and -means'forlimiting the indexing movement of said Vindexible plateV so that the contracting iiuidchambers communicate with said output port means regardless of the direction of rotation of'said outer gear member.V
7. In a Vgear, pump, the combination comprising: an input shaft adapted to be rotated about an axis, an outer gear driven by said input shaft, an inner gear meshing with said outer gear and rotatable about an axis spaced from said input shaft axis, :an yindexible port plate adjacent said gears having ports therein adapted to convey iiuid to and from said gears, said inner gear axis being fixed with respect Ito said port plate, a relatively stationary port member having inlet and outlet Iports therein adapted to selectively communicate with said indexible ports to maintain a unidirectional pump `output irrespective of the direction of rotate of said input shaft, means separate from said stationary port Imember -or supporting said port plate for rotation about the input shaft axis to assure the proper alignment therebetween, said means for supporting said port plate :and said means for connecting the outer gear to the input shaft including a cylindrical sleeve surrounding a portion of said input shaft and fixed with respect thereto, said sleeve extending around said outer gear and xed with respect thereto, and said sleeve further extending :around a portion of said port plate and frietionally engaging the lperiphery thereof.
References Cited UNITED 2/1939 3/1939 12/1940 12/1949 ll/l954 10/1957 9/1959 1/1965 9/1965 STATES PATENTS Kempton et al 103-117 Neeson 10B-126 Neeson 103-117 Wentling 103-126 Seavey 103--117 Hoekstra.
Gerteis.
Phelps et al. 103-126 Garrison et al 103-126 DONLEY T. STOCKING, Primary Examiner.
l5 W. I. GOODLIN, Assistant Examiner.
Pf3-1050 UNITED STATES PATENT OFFICE CERTIFICATE 0F CORRECTION Patent No. 3 343 494 Dated September 26 1967 IUVEDLOS) Pobert Erikson and Nils Einar Swedberg It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:
In claim 3, column 8, line 28, cancel "relativel" and substitute therefor relatively line 35 cancel "ring"; line 37, cancel'ring and insert gear In the Assignment, please cancel "Sundstrand Corporation, an Illinois corporation" and insert the correct assignee as Sundstrand Corporation, a Delaware corporation SIGNED AND SEALED MAR 2 4.1970
(SEAL) Attest:

Claims (1)

1. IN A GEAR PUMP, THE COMBINATION COMPRISING: AN INPUT SHAFT ROTATABLE ABOUT AN AXIS, AN OUTER RING GEAR ADJACENT ONE END OF SAID INPUT SHAFT AND DRIVEN THEREBY, AN INDEXIBLE PORT PLATE SLIDABLY ENGAGING SAID OUTER RING GEAR AND HAVING TWO GENERALLY ARCUATE PORTS EXTENDING AXIALLY THERETHROUGH, SAID PORT PLATE HAVING AN ARCUATE RECESS IN THE PERIPHERY THEREOF EXTENDING SUBSTANTIALLY 180 DEGREES, A HOLLOW SHAFT MOUNTED IN SAID PORT AND EXTENDING WITHIN SAID RING GEAR, SAID HOLLOW SHAFT HAVING AN AXIS SPACED FROM SAID INPUT SHAFT AXIS, AN INNER PINION GEAR MOUNTED FOR ROTATION ON SAID HOLLOW SHAFT AND MESHING WITH SAID OUTER RING GEAR, A PASSAGE IN SAID INPUT SHAFT COMMUNICATING WITH THE INTERIOR OF SAID HOLLOW SHAFT ADAPTED TO CONVEY FLUID FROM THE PUMP, A RELATIVELY STATIONARY COVER MEMBER ENGAGING ONE SIDE OF SAID PORT PLATE, A PROJECTION ON SAID COVER MEMBER EXTENDING INTO SAID PORT PLATE RECESS FOR LIMITING THE INDEXING MOVEMENT THEREOF WHEREBY WHEN THE INPUT SHAFT ROTATES THE PORT PLATE,
US589150A 1966-09-12 1966-09-12 Automatically reversible gear pump Expired - Lifetime US3343494A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US589150A US3343494A (en) 1966-09-12 1966-09-12 Automatically reversible gear pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US589150A US3343494A (en) 1966-09-12 1966-09-12 Automatically reversible gear pump

Publications (1)

Publication Number Publication Date
US3343494A true US3343494A (en) 1967-09-26

Family

ID=24356814

Family Applications (1)

Application Number Title Priority Date Filing Date
US589150A Expired - Lifetime US3343494A (en) 1966-09-12 1966-09-12 Automatically reversible gear pump

Country Status (1)

Country Link
US (1) US3343494A (en)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1921942A1 (en) * 1968-04-29 1969-11-20 Tuthill Pump Co Cam pump
US3491697A (en) * 1966-11-29 1970-01-27 Danfoss As Hydraulic fuel oil pump or the like
US3796523A (en) * 1972-12-13 1974-03-12 Novelty Tool Co Inc Reversible gear pump
DE2926443A1 (en) * 1978-09-25 1980-04-03 Copeland Corp Reversible radial vane oil pump for compressor - has friction operated valve disc to maintain direction of flow when rotation reverses
US4331420A (en) * 1978-09-25 1982-05-25 Copeland Corporation Reversible unidirectional flow pump with frictionally engaged axial valve plate
US4331421A (en) * 1979-05-31 1982-05-25 Jones Othel L Reversible unidirectional flow pump with axial frictionally engaged recessed valve plate
US4526518A (en) * 1981-07-23 1985-07-02 Facet Enterprises, Inc. Fuel pump with magnetic drive
US4540347A (en) * 1981-12-24 1985-09-10 Concentric Pumps Limited Gerotor pump
US5340284A (en) * 1992-03-20 1994-08-23 Lucas Industries Public Limited Company Two stage fuel pump with pressure passage in the first stage rotor
US6196814B1 (en) * 1998-06-22 2001-03-06 Tecumseh Products Company Positive displacement pump rotatable in opposite directions
WO2002023044A1 (en) * 2000-09-16 2002-03-21 Zf Friedrichshafen Ag Hydraulic pump
WO2008138655A1 (en) * 2007-05-11 2008-11-20 Robert Bosch Gmbh Hydraulic system having a reversible gear pump
US10337512B2 (en) * 2014-08-25 2019-07-02 Carrier Corporation Gear pump with dual pressure relief
US11022116B2 (en) * 2018-01-19 2021-06-01 Lg Electronics Inc. Lubricant supply device and a compressor using the same

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2148561A (en) * 1937-01-13 1939-02-28 Tuthill Pump Co Pump structure
US2151482A (en) * 1937-06-26 1939-03-21 Chrysler Corp Pump
US2225228A (en) * 1937-05-29 1940-12-17 Chrysler Corp Compressor lubrication
US2490391A (en) * 1946-04-10 1949-12-06 Chrysler Corp Reversible internal gear pump
US2694367A (en) * 1950-11-01 1954-11-16 Paragon Gear Works Inc Rotary pump
US2808780A (en) * 1952-10-07 1957-10-08 Philips Corp Rotary pump
US2905094A (en) * 1955-06-01 1959-09-22 Carrier Corp Automatically reversible positive displacement internal gear rotary pump
US3165066A (en) * 1962-07-11 1965-01-12 Copeland Refrigeration Corp Unidirectional flow rotary pump
US3208392A (en) * 1962-10-15 1965-09-28 Copeland Refrigeration Corp Reversible gear pump with unidire ctional flow

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2148561A (en) * 1937-01-13 1939-02-28 Tuthill Pump Co Pump structure
US2225228A (en) * 1937-05-29 1940-12-17 Chrysler Corp Compressor lubrication
US2151482A (en) * 1937-06-26 1939-03-21 Chrysler Corp Pump
US2490391A (en) * 1946-04-10 1949-12-06 Chrysler Corp Reversible internal gear pump
US2694367A (en) * 1950-11-01 1954-11-16 Paragon Gear Works Inc Rotary pump
US2808780A (en) * 1952-10-07 1957-10-08 Philips Corp Rotary pump
US2905094A (en) * 1955-06-01 1959-09-22 Carrier Corp Automatically reversible positive displacement internal gear rotary pump
US3165066A (en) * 1962-07-11 1965-01-12 Copeland Refrigeration Corp Unidirectional flow rotary pump
US3208392A (en) * 1962-10-15 1965-09-28 Copeland Refrigeration Corp Reversible gear pump with unidire ctional flow

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3491697A (en) * 1966-11-29 1970-01-27 Danfoss As Hydraulic fuel oil pump or the like
DE1921942A1 (en) * 1968-04-29 1969-11-20 Tuthill Pump Co Cam pump
US3796523A (en) * 1972-12-13 1974-03-12 Novelty Tool Co Inc Reversible gear pump
DE2926443A1 (en) * 1978-09-25 1980-04-03 Copeland Corp Reversible radial vane oil pump for compressor - has friction operated valve disc to maintain direction of flow when rotation reverses
US4331420A (en) * 1978-09-25 1982-05-25 Copeland Corporation Reversible unidirectional flow pump with frictionally engaged axial valve plate
US4331421A (en) * 1979-05-31 1982-05-25 Jones Othel L Reversible unidirectional flow pump with axial frictionally engaged recessed valve plate
US4526518A (en) * 1981-07-23 1985-07-02 Facet Enterprises, Inc. Fuel pump with magnetic drive
US4540347A (en) * 1981-12-24 1985-09-10 Concentric Pumps Limited Gerotor pump
US5340284A (en) * 1992-03-20 1994-08-23 Lucas Industries Public Limited Company Two stage fuel pump with pressure passage in the first stage rotor
US6196814B1 (en) * 1998-06-22 2001-03-06 Tecumseh Products Company Positive displacement pump rotatable in opposite directions
WO2002023044A1 (en) * 2000-09-16 2002-03-21 Zf Friedrichshafen Ag Hydraulic pump
WO2008138655A1 (en) * 2007-05-11 2008-11-20 Robert Bosch Gmbh Hydraulic system having a reversible gear pump
US10337512B2 (en) * 2014-08-25 2019-07-02 Carrier Corporation Gear pump with dual pressure relief
US11022116B2 (en) * 2018-01-19 2021-06-01 Lg Electronics Inc. Lubricant supply device and a compressor using the same

Similar Documents

Publication Publication Date Title
US3343494A (en) Automatically reversible gear pump
US1927799A (en) Rotary pump
US2309683A (en) Pumping unit
US2490115A (en) Variable displacement rotary pump
US2255785A (en) Fluid pressure device
US2405061A (en) Pump structure
US2527673A (en) Internal helical gear pump
US3515496A (en) Variable capacity positive displacement pump
US2544144A (en) Oil burner pump
US2053919A (en) Rotary pump
US3216362A (en) Flexible ring pump drive device
US3289601A (en) Fluid displacement device usable as a hydraulic motor or pump
US2148561A (en) Pump structure
US3211365A (en) Compressor structure
US2107152A (en) Reversible fuel pump
US2266191A (en) Variable displacement pump
US2338065A (en) Gear pump
US2233709A (en) Fuel supply unit for oil burners
US1964330A (en) rotary pump
US3165066A (en) Unidirectional flow rotary pump
US2915982A (en) Rotary pump
US2076664A (en) Pump
US2052419A (en) Variable delivery gear pump
US3076413A (en) High pressure aircraft gear pump
US2346761A (en) Hydraulic gear pump