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US3748063A - Pressure loaded gear pump - Google Patents

Pressure loaded gear pump Download PDF

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Publication number
US3748063A
US3748063A US00132682A US3748063DA US3748063A US 3748063 A US3748063 A US 3748063A US 00132682 A US00132682 A US 00132682A US 3748063D A US3748063D A US 3748063DA US 3748063 A US3748063 A US 3748063A
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United States
Prior art keywords
pressure
chamber
sealing
cavity
faces
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Expired - Lifetime
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US00132682A
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English (en)
Inventor
R Putnam
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Eaton Corp
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Cessna Aircraft Co
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Assigned to EATON CORPORATION, EATON CENTER, CLEVELAND, OH 44114-2584, AN OH CORP. reassignment EATON CORPORATION, EATON CENTER, CLEVELAND, OH 44114-2584, AN OH CORP. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CESSNA AIRCRAFT COMPANY, THE
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • Patent 11 1 ifiinssunstolmsp GEAR PUMP,
  • A seal pack in the-chamber seals against the land memberjandf'one of the parallel seal plate and housing faces'to separate the chamber from the inlet and shaft'openings'Theseal pack, in-itself, further defines zones of pressure on'the seal plate maintained at pressures different from .that in' the chamber. 4'
  • This invention relates to positive displacement hydraulic gear devices of the type incorporating pressure loaded side sealing plates. More particularly, the invention relates to improved sealing means contained wholly within the gear cavity effecting fluid sealing of the transverse gear faces.
  • Devices of the class described generally incorporate a movable sealing plate arranged such that one side is pressed upon the transverse gear faces to seal same.
  • One or more pressure chambers, fed with fluid from the device, on the opposite side of the plate urge the plate toward the gears.
  • Such chambers and the means required to seal the chambers have generally produced complicated and expensive design of the sealing plate, the housing and other components.
  • prior art designs contemplate grooves in either the seal plate or the housing to carry the sealing means delimiting and defining theradial limits of the pressure chamber.
  • the present invention proposes improved sealing means providing pressure loaded sealing of the gear side faces distinctly simpler and more economical than prior art. Yet, the invention also creates precise side loading and optimal pump efficiency. It is particularly characterized by a lack of grooves in the seal plate and housings for delimiting the pressure chamber. Instead, the device of the present invention utilizes sealing meansfreely positioned within the-pressure chamber.
  • the inventioncontemplate s a flat sealing plate mov ably disposed within the gear cavity with one side adjacent the gear side faces and the'outer face spaced from The chamber covers an area of the sealing plate face so as to create sufficient force to urge the plate into'light sealing engagement with the lateral faces of the gears.
  • a three-element seal pack disposed within the pressure chamber, seals against one 'ofthe parallel faces and at right angles against the land to isolate the pressure chamber from the lower pressure inlet'and shaft areas. Theseal pack itself defines a fluid zone within the main pressure chamber which is isolated therefrom and maintained at a pressure somewhat less thatthat of the main pressure chamber.
  • the invention thus provides a pressure loading chamber of desireddesign with separate pressure zones without introducing complicated design of the seal plate or housing.
  • the invention therefore, generally contemplates improved side sealing means for hydraulic gear devices simple and economical in design.
  • the invention has a primary objective of providing a sealing plate for engagement with the gears in a rotary fluid machine having a pressure loaded rear surface spaced from a parallel housing surface with land means projecting axially therebetween to define a pressure loading chamber and to surround areasof pressure different from that of the loading chamber. Sealing means positioned at right angles against the land and one of the parallel faces isolate and seal the pressure loading chamber from the areas maintained at different pressure.
  • a further object is to provide improved sealing means for devices constructed in accordance with the preceding objective.
  • Yet another object is to provide such sealing means which define a zone wholly confined within the sealing means hydraulically isolated from the main pressure loading chamber and maintained at a pressure different from that of the main chamber.
  • FIG. 1 is a transverse section of a gear ing the present invention
  • FIG. 2 is a view taken along line 2-2 of FIG. 1;
  • FIG. 3 is a viewtaken along line 3-3 of FIG. 1 showing the seal plate face 43 which engages the sides of the gears;
  • FIG. 4 is a view taken'along line 44 of FIG. 1 show- DESCRIPTION or THE PREFERRED EMBODIMENT
  • the gear device in FIG. 1, designated generally by the numeral 20, has a housing including end plates 21 and 22 and a body 23 sandwiched between and secured to the plates 21, 22.
  • Agearcavity 24 within the body shown in'FIG. 2, accepts a pair of intermeshing gears 25, 26 whose teeth'tips closely fit the cavity wall 27.
  • Each gear is affixed'to a shaft 28, 29 that is mounted for rotation within b'ushings30 provided in shaft bores in the end plates.
  • a fluid inlet 31 and outlet 32 open into opposite sides of cavity 24 and communicate with external ports in the housing for delivery and discharge of fluid.
  • gear 25 drives gear 26, and fluid drawn in through inlet 31 .is trapped in the intertooth gear spaces and transported around the cavity wall 27 to high pressure outlet 32. While traveling around the periphery of the gear'cavity from inlet to outlet, pressure of the intertooth spaces gradually increases, this pressure increase with rotation generally being referred to as the pump pressure gradient.
  • the pressure gradient zone of the pump denotes those portions subject to pressure which are intermediate inlet and outlet pressure.
  • the gear transverse faces 34 lightly press and seal against end plate 21, and an axially movable seal plate 36 disposed within the gear cavity 24 between gear faces 35 and flat face 45 of end plate 22 seals transverse face 35. Fluid pressure between the seal plate and end plate urges seal plate 36 and the gears leftwardly in FIG. 1 to effect sealing of the transverse gear faces.
  • Recesses 42 positioned a short are distance fromrelief 37, direct fairly low pressure fluid to the bushings as they pick up fluid at a lower pressure point in the pump pressure gradient zone.
  • pressure at a certain location in the pressure gradient zone such as at depression 42, varies markedly with changes in different operating parameters such as speed of gear rotation and outlet pressure.
  • Pressure in the bearing openings accordingly may vary from near inlet pressure to outlet pressure with changes in the operating parameters.
  • Bearing pressure may be controlled .if desired by, for instance, including a pressure relief valve in'the bearing pressure area.
  • FIG. 4' illustrates seal plate face 44 and the upstanding land member 46 formed integrally :with seal plate 36 upon'face 44 and extending axially thereof toward end plate face 45.
  • 'Land 46 surrounds each shaft opening 39, 40 and has a portion 47 substantially surrounding the inlet by extending between the shaft openings and from each opening 39, 40 laterally to the cavity wall 27.
  • a seal receiving groove 70 in portion 47 extends around inlet 31 and opens at the cavity wall 27 on opposite sides of the inlet.
  • the sealing plate has through oblong slots 48 permitting communication of fluid in the intertooth pockets with face 44 as the pockets passslots 48.
  • the outward edge 49 of land 46 forms, along with a portion of cavity wall 27, the periphery of a fluid chamber 50 laterally bounded by the parallel spaced faces 44 and 45 of the sealing plate and end plate.
  • a portion of chamber 50 is occupied by a seal pack assembly 51 which will be described in greater detail below.
  • Pressure fluid is communicated to chamber 50 via the seal plate peripheral relief 38.
  • Chamber 50 extends from gear cavity wall 27 radially inwardly past the gear root circle at the bottom of the gear teeth pockets, and extends circumferentially around the gears from the outlet to points adjacent the inlet and includes areas of surface 44 opposite areas of face 43 exposed to pressured less than outlet pressure.
  • Outlet pressure in chamber 50 will therefore overbalance the lower pressures adjacent the inlet and inside the gear root circle to push plate 36 against the gears.
  • the plate 36 is overbalanced and pressed into sealing engagement at those areas where sealing is most required, in the pressure gradient zone and aroundthe shaft openings 39 and 40.
  • FIG. 5 illustrates the three, generally 3-shaped elements 52, 53, 54 comprising the seal pack, that, as seen in FIGS. 1 and 6,assemble upon seal plate face 44.
  • Thin protector gasket 52 of nylon or other extrusionresistant material, is of a U-shaped cross-section with its bottom face 55 lying directly upon seal plate face 44 and its legs 56, 57 extending axially toward end plate face 45. At its ends, gasket 52 has a continuous'inner wall 58 surrounding a through opening in the gasket.
  • the elastomer o-ring 53 is an endless pliable element of generally circular cross-section which is doubled and positioned within the protector gasket 52 in the same characteristic 3 form. O-ring 53 loops around gasket inner wall 58 at each endand creates a double strand running the remainder of the length of the protector gasket. FIGS. 6 and 7 clearly show how the o-ring fits within gasket 52 at inner wall 58 and at other positions. Elastomers of a variety of cross-sections may be utilized; the o-ring is chosen in the present embodiment due to its availability and economy. Alternately, the elastomer can be integrally formed as a single element with eyelets at either end looping walls 58.
  • the third seal element is a generally U-shaped backup gasket 54 made of relatively rigid fibrous material and generally conforming in' size and shape to the portion of seal flat face 44 forming the lateral face of pressure chamber 50.
  • the protector gasket legs 56, 57 fit within depending back-up gasket legs 59, 60 to enclose arectangular space containing elastomer 53.
  • Upper'surface 61 of back-up gasket 54 sealingly engages end plate face 45, and side face 62 seals against wall 49 of land 46.
  • Gasket-54 thus provides two right angle faces 61, 62 which effectively seal chamber 50 from the lower pressure inlet and shaft openings.
  • back-up gasket 54 has an island projection 63 snugly protruding inside protector gasket wall 58. In this area, the outer back-up gasket leg 59 is deleted and protector gasket wall 56 engages gear cavity wall 27.
  • the protector gasket inner wall 58 and back-up gasket island 63 cooperate to form a separate pressure chamber 64 within but isolated from the pressure chamber 50.
  • Slot opening 48 feeds intermediate pressure fluid from the pressure gradient area of the gear cavity to chamber 64 which is accordingly maintained subject to the intermediate pressure.
  • Chamber 64 communicates through bore 65 with recess 66 in the face 61 of gasket 54'.
  • Recess 66 is substantially equal to chamber 64 in area to assure a pressure balance across island 63 and prevent the accumulation of higher discharge pressure in recess 66 which would, under certain conditions, increase the pressure in chamber 64 to discharge pressure.
  • chamber 64 By forming chamber 64 entirely by and within the seal pack elements, design of seal plate 36 and end plate face 45 are simplified, thereby reducing costs while increasing unit reliability and life. Assembly procedures are also considerably simplified.
  • prior art pumps normally create an intermediate pressure chamber by an island such as 63 integrallyformed upon eitherthe seal plate or end plate and a complex groove system surrounding the island and carrying fluid seals.
  • back-up gasket 54 serves primarily to seal at, right angles against edge 49 of land 46 and the end plate face 45.
  • Protector gasket 52 assists in sealing but serves primarily to prevent extrusion of .flowing of the soft o-ring 53'from its proper position.
  • High prescertain circumstances it has been found advantageous to induce lateral compressing of the left strand of o-ring 53 in FIG. 7 between body 23 and island 58, and in other applications it may be desirable to include lateral v compressment of the elastomer.
  • an intermediate chamber 64 is optional, being dependent upon the overall size of the pump. Without such chamber the design and elements of the seal pack may be varied considerably, subject to the primary requirement that the seal pack effect right angle sealing against the end plate face and the support wall to isolate pressure chamber 50 from the inletand the shaft openings.
  • seal pack 51 is such that it can be freely positioned in the pressure chamber 50 and need not be confined within a groove in the seal plate 36 or end plate 22. Pressure in chamber 50 urges the seal pack against land edge 49 and end plate face and holds the seal pack in proper sealing position. Fluid flow patterns set up in chamber will not move or wash out" the seal pack due to the relatively rigid nature of the outer sides of the seal pack, especially leg 59 of gasket 54 which is laterally unsupported over an extensive area and particularly unsupported at peripheral relief 38. In contrast, prior art designs incorporate the sealing means in a groove to give the required lateral support. Being freely positioned in pressure chamber 50 also distinctly simplifies assembly of the seal pack into the unit.
  • Sealing groove 70 in the inlet portion 47 of support 46 accepts an o-ring 71, L-shaped back-up gasket 72 and protector gasket 73, illustrated in cross-section in FIG. 8.
  • the back-up gasket 72 along with o-ring 7l effect the primary sealing against end plate face 45 and the wall 74 of groove 70 adjacent the inlet 31. This seals against fluid leakage from the higher pressure shaft openings to inlet 31 and prevents loss of bearing lubrication fluid.
  • Protector gasket 73 like gasket 52, prevents extrusion of o-ring 71.
  • Trough 67 shown in dotted lines in FIG. 4, is not sealed from the intermediate chambers 64 and normally carries chamber 64 pressure by communicating therewith between walls 58 and islands 63.
  • This trough, along with chamber 64 at intermediate pressure adds with the higher discharge pressure across the remainder of face 44 to produce a precise force slightly and uniformly overbalancing the gear cavity forces to urge the seal plate into light, but sealing contact with gear faces.
  • the o-ring also initially compresses axially to provide slight preloading to hold gaskets 52 and 54 against faces 44 and 45.
  • an axially pressure loaded gear pump having a housing enclosing an internal gear cavity having fluid inlet and outlet means opening intoopposite sides of the cavity; a pair of intermeshing gears having transverse gear faces disposed in the cavity and affixed to axially extending shafts rotatively mounted in the housing; an axially movable seal plate disposed entirely within said cavity having one ,side in sealing engagement with the transverse gear faces and an opposite flat face disposed parallel and spaced from a transverse end face of the gear cavity to define a space therebetween,
  • said plate having bores accepting the shafts, wherein the improvement comprises:
  • a land member integral with said seal plate extending axially between said parallel faces and occupying only that portion of said space between the parallel faces surrounding the inlet and shaft bores, said land member and the wall of said cavity defining a pressure chamber of substantially uniform axial width in the remainder of said space;
  • first relatively rigid U-shaped gasket member in said chamber having a base and a pair of axially extending legs depending from the base, pressure in said chamber urging one of said legs and said base respectively into sealing engagement with said land member and said gear cavity end face to seal said chamber from said inlet and said shaft bores, said one leg of the gasket being laterally supported by said land member while the other leg of said gasket is laterally unsupported against said pressure in the chamber;
  • an axially pressure loaded gear pump having an axially movable side sealing plate wholly contained within the rotor cavity of the pump housing, the rear face of said sealing plate and the adjacent housing end wall comprising the transverse faces of a fluid pressure chamber therebetween of substantially uniform axial width, said sealing plate and housing defining inner and outer axially extending radial walls of said chamber; improved means for sealing said chamber,.comprising:
  • first and second gaskets disposed wholly within said chamber and cooperating with each other to define an enclosed space therebetween, said first gasket having adjacent right angle faces urged by chamber pressure into sealing engagement with one of said chamber transverse faces and said inner wall of said chamber;
  • said second gasket having a base urged by chamber pressure into sealing engagement with the other of said chamber transverse faces;
  • a resilient elastomer positioned in said space and compressed between said gaskets so as to urge same initially against said chamber transverse faces.
  • a hydraulic gear device having a housing enclosing an internal gear cavity having spaced apart end walls, fluid inlet and outlet means opening into opposite sides of the cavity; a pair of intermeshing gears disposed in said cavity between said end walls and closely fitting the cavity confines and presenting a transverse side spaced from an adjacent one of said end walls of the cavity; axially extending shafts in the housing rotatively supporting each gear whereby upon rotation said gears carry fluid from the inlet to the outlet; wherein the improvement comprises:
  • a unitary fluid sealing plate movably disposed within said gear cavity intermediate said transverse side of the gears and said adjacent end wall, said sealing plate having one side in sealing engagement with said transverse side of the gears and an opposing face arranged parallel and spaced from said adjacent end wall defining a space therebetween;
  • a land member disposed within said space and extensive through only that portion of said space which surrounds said shaft openings and the inlet, said land member engaging the edge of said gear cavity adjacent the inlet, whereby said land member and said gear cavity edge define a pressure chamber of substantially uniform axial width in the remaining portion of said space between said adjacent end wall and said opposing face of the sealing plate;
  • sealing means movably disposed wholly within said pressure chamber and conforming generally in shape to the edge of the land member;
  • said sealing means including a first U-shaped gasket with a pair of parallel legs extending perpendicularly and axially from a bottom face which is adjacent said adjacent end wall, said chamber pressure urging said bottom face axially against said adjacent end wall and urging one of said perpendicular axial legs transversely against said edge of the land member.
  • the device of claim 1 further including a groove in said land member, and second sealing means in said groove preventing fluid flow across said land member between said shaft openings and the inlet.
  • sealing means further includes resilient means contained within said U-shaped first gasket and axially compressed between said sealing plate and adjacent end wall.
  • said sealing means includes a second U-shaped gasket having a bottom face lying upon said sealing plate and having parallel legs axially extending within said first gasket legs, said first and second gaskets forming therebetween a rectangular trough containing said resilient means.
  • said resilient means comprise an endless elastomer o-ring located in said trough and surrounded by said gaskets.
  • an axially pressure loaded gear pump having a pair of intermeshing gears journalled upon axially extending shafts and located within a housing pumping cavity, a fiat sealing plate in the housing cavity with one face in sealing engagement with the transverse gear faces and an opposite face parallel to and spaced from a transverse end face of the housing cavity, and a rigid land member on said sealing plate extending axially in said space between the sealing plate and housing end plate to define a pressure loading chamber of substantially uniform axial width in said spacefed with outlet pressure fluid; improved means for sealing said chamber comprising:
  • first U-shaped gasket having a back face with leg members depending at generally right angles thereto, said gasket disposed in said chamber having said back face and a leg member urged by pressure in said chamber into sealing engagement at right angles with said land member and said end plate;
  • a resilient elastomer member located inside said gaskets in said rectangular space, said elastomer being compressed axially to initially preload said first and second gaskets against said end plate and sealing plate faces respectively.
  • said resilient elastomer is an endless elastomer o-ring arranged to form a double strand in said rectangular space.
  • said second gasket is provided with interior walls extending into said rectangular space defining openings in said bottom face registering with corresponding conduits in said seal plate which communicate with pressure developed in the gear cavity intermediate inlet and outlet pressure, said first gasket having an island portion at each end adapted to be received within said interior walls to define intermediate pressure zones between each of said islands and the sealing plate, said o-ring sealing against said interior walls to separate said zones from the pressure chamber, I
  • An axially pressure loaded positive displacement gear pump comprising:
  • a housing enclosing an internal gear cavity and having spaced apart transverse end faces
  • said gear peripheries closely fitting the wall of said cavity such that the gears receive low pressure fluid fromthe inlet anddeliver higher pressure fluid at L the outlet, said gears having transverse faces spaced from an adjacent end face of said housing;
  • a sealing plate movably disposed in said cavity with one side in sealing engagement with the transverse gears faces and an opposite flat face parallel and spaced from said adjacent housing end face to define a space therebetween, said plate having openings accepting said shafts;
  • a single land member integrally formed upon one of said parallel housing and sealing plate faces extend ing axially in said space toward the other of said parallel faces, said land member extensive through only that portion of the space between said parallel faces adjacent the inlet and shaft opening s, said land member and gear cavity wall defining a pressure loading chamber of substantially uniform axial width in the remainder of said space between said parallel faces that is separated from the shaft openings and inlet by said land member;
  • a sealing member in said pressure loading chamber partially encircling said gears and having adjacent right angle faces urged into sealing engagement with said land member and said other of said parallel faces by pressure in said chamber to seal same from the inlet and shaft openings, said sealing member having a groove opening toward the sealing plate;
  • elastomer means positioned in said zone for sealing said zone from said pressure loading chamber.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Gasket Seals (AREA)
US00132682A 1971-04-09 1971-04-09 Pressure loaded gear pump Expired - Lifetime US3748063A (en)

Applications Claiming Priority (1)

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US13268271A 1971-04-09 1971-04-09

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US3748063A true US3748063A (en) 1973-07-24

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US00132682A Expired - Lifetime US3748063A (en) 1971-04-09 1971-04-09 Pressure loaded gear pump

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US (1) US3748063A (ko)
JP (1) JPS5141923B1 (ko)
CA (1) CA945006A (ko)
DE (1) DE2217076A1 (ko)
FR (1) FR2135957A5 (ko)
GB (1) GB1390631A (ko)
SE (1) SE376275B (ko)

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3822682A (en) * 1972-06-30 1974-07-09 Textron Inc Rotary valve engine
FR2434264A1 (fr) * 1978-08-24 1980-03-21 Commercial Shearing Pompe ou moteur rotatif a engrenage et a plaques de butee
US4281974A (en) * 1978-09-19 1981-08-04 Kayabakogyokabushikikaisha Seal mechanism in gear pumps or motors
US4309158A (en) * 1978-11-03 1982-01-05 Robert Bosch Gmbh Gear positive displacement machine with U-shaped supporting element for sealing member
US4368013A (en) * 1979-06-19 1983-01-11 Dowty Hydraulic Units Limited Gear motor with fluid pressure groove and recess to facilitate starting
US4422836A (en) * 1981-09-01 1983-12-27 Usher Meyman Rotary machine with peripherally contacting rotors and end face sealing plate
US4449898A (en) * 1982-06-07 1984-05-22 Vickers, Incorporated Power transmission
US4636155A (en) * 1984-06-29 1987-01-13 Commercial Shearing, Inc. Hydraulic seal having U-shaped gasket and a plurality of plastically deformable posts
US4768935A (en) * 1985-10-08 1988-09-06 Atos Oleodinamica S.P.A. Volumetric blade pump for fluid-hydraulic actuation
US5004412A (en) * 1988-04-08 1991-04-02 Sauer-Sundstrand S.P.A. Gear machine for use as a pump or motor
US5076770A (en) * 1990-04-13 1991-12-31 Allied-Signal Inc. Gear pump having improved low temperature operation
WO1992014931A1 (en) * 1991-02-22 1992-09-03 Lubrication Research, Inc. Pump with variable clearance compensator end plate
US5676532A (en) * 1996-04-08 1997-10-14 Cheng; Lu Chi Adjustable one-way rotary liquid pumping device
US6390793B1 (en) * 2001-02-13 2002-05-21 Haldex Barnes Corporation Rotary gear pump with fluid inlet size compensation
US20140030132A1 (en) * 2012-07-24 2014-01-30 Denso Corporation Gear pump device
DE10104621B4 (de) * 2001-02-02 2014-07-24 Robert Bosch Gmbh Axialfeldabdichtung einer Zahnradmaschine
US20140294648A1 (en) * 2011-05-12 2014-10-02 Paul Krampe Apparatus for Sealing a Pump Chamber of a Rotary Lobe Pump, and a Rotary Lobe Pump Having Said Apparatus
DE102016005335A1 (de) 2016-04-30 2017-11-02 Audi Ag Armatur
EP3964689A1 (en) * 2020-09-08 2022-03-09 Eaton Intelligent Power Limited Gear pump with self-lubricating bearings

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2215103A5 (ko) * 1973-01-23 1974-08-19 Hydroperfect Int
JPS6139070A (ja) * 1984-07-31 1986-02-25 Casio Comput Co Ltd 複合機

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US2824522A (en) * 1950-05-19 1958-02-25 Borg Warner Pump, pressure loaded with offset loading
US3171358A (en) * 1963-06-03 1965-03-02 Lear Siegler Inc Gear type pump
US3174435A (en) * 1962-08-16 1965-03-23 Clark Equipment Co Pump or motor
US3348492A (en) * 1966-12-05 1967-10-24 Borg Warner Reversible wear plate pump
US3363578A (en) * 1966-12-21 1968-01-16 Clark Equipment Co Gear pump and thrust plate therefor
US3371615A (en) * 1967-01-16 1968-03-05 Borg Warner Pressure loaded pump
US3539282A (en) * 1968-04-13 1970-11-10 Bosch Gmbh Robert Gear pump or motor

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2824522A (en) * 1950-05-19 1958-02-25 Borg Warner Pump, pressure loaded with offset loading
US3174435A (en) * 1962-08-16 1965-03-23 Clark Equipment Co Pump or motor
US3171358A (en) * 1963-06-03 1965-03-02 Lear Siegler Inc Gear type pump
US3348492A (en) * 1966-12-05 1967-10-24 Borg Warner Reversible wear plate pump
US3363578A (en) * 1966-12-21 1968-01-16 Clark Equipment Co Gear pump and thrust plate therefor
US3371615A (en) * 1967-01-16 1968-03-05 Borg Warner Pressure loaded pump
US3539282A (en) * 1968-04-13 1970-11-10 Bosch Gmbh Robert Gear pump or motor

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3822682A (en) * 1972-06-30 1974-07-09 Textron Inc Rotary valve engine
FR2434264A1 (fr) * 1978-08-24 1980-03-21 Commercial Shearing Pompe ou moteur rotatif a engrenage et a plaques de butee
US4242066A (en) * 1978-08-24 1980-12-30 Commercial Shearing, Inc. Rotary pumps and motors and thrust plates therefor
US4281974A (en) * 1978-09-19 1981-08-04 Kayabakogyokabushikikaisha Seal mechanism in gear pumps or motors
US4309158A (en) * 1978-11-03 1982-01-05 Robert Bosch Gmbh Gear positive displacement machine with U-shaped supporting element for sealing member
US4368013A (en) * 1979-06-19 1983-01-11 Dowty Hydraulic Units Limited Gear motor with fluid pressure groove and recess to facilitate starting
US4422836A (en) * 1981-09-01 1983-12-27 Usher Meyman Rotary machine with peripherally contacting rotors and end face sealing plate
US4449898A (en) * 1982-06-07 1984-05-22 Vickers, Incorporated Power transmission
US4636155A (en) * 1984-06-29 1987-01-13 Commercial Shearing, Inc. Hydraulic seal having U-shaped gasket and a plurality of plastically deformable posts
AU576808B2 (en) * 1984-06-29 1988-09-08 Commercial Shearing Inc. Hydraulic seal
US4768935A (en) * 1985-10-08 1988-09-06 Atos Oleodinamica S.P.A. Volumetric blade pump for fluid-hydraulic actuation
US5004412A (en) * 1988-04-08 1991-04-02 Sauer-Sundstrand S.P.A. Gear machine for use as a pump or motor
US5076770A (en) * 1990-04-13 1991-12-31 Allied-Signal Inc. Gear pump having improved low temperature operation
WO1992014931A1 (en) * 1991-02-22 1992-09-03 Lubrication Research, Inc. Pump with variable clearance compensator end plate
US5676532A (en) * 1996-04-08 1997-10-14 Cheng; Lu Chi Adjustable one-way rotary liquid pumping device
DE10104621B4 (de) * 2001-02-02 2014-07-24 Robert Bosch Gmbh Axialfeldabdichtung einer Zahnradmaschine
US6390793B1 (en) * 2001-02-13 2002-05-21 Haldex Barnes Corporation Rotary gear pump with fluid inlet size compensation
US20140294648A1 (en) * 2011-05-12 2014-10-02 Paul Krampe Apparatus for Sealing a Pump Chamber of a Rotary Lobe Pump, and a Rotary Lobe Pump Having Said Apparatus
US9212659B2 (en) * 2011-05-12 2015-12-15 Hugo Vogelsang Maschinenbau Gmbh Apparatus for sealing a pump chamber of a rotary lobe pump, and a rotary lobe pump having said apparatus
US20140030132A1 (en) * 2012-07-24 2014-01-30 Denso Corporation Gear pump device
US9046102B2 (en) * 2012-07-24 2015-06-02 Advics Co., Ltd. Gear pump device with seal mechanism
DE102013214276B4 (de) * 2012-07-24 2016-11-24 Advics Co., Ltd. Zahnradpumpenvorrichtung
DE102016005335A1 (de) 2016-04-30 2017-11-02 Audi Ag Armatur
EP3964689A1 (en) * 2020-09-08 2022-03-09 Eaton Intelligent Power Limited Gear pump with self-lubricating bearings
US11703050B2 (en) 2020-09-08 2023-07-18 Eaton Intelligent Power Limited Gear pump with self-lubricating bearings

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JPS5141923B1 (ko) 1976-11-12
DE2217076A1 (de) 1972-10-26
SE376275B (ko) 1975-05-12
CA945006A (en) 1974-04-09
FR2135957A5 (ko) 1972-12-22
GB1390631A (en) 1975-04-16

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Owner name: EATON CORPORATION, EATON CENTER, CLEVELAND, OH 441

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CESSNA AIRCRAFT COMPANY, THE;REEL/FRAME:004991/0073

Effective date: 19880930