US3498227A - Axial plunger pump - Google Patents

Axial plunger pump Download PDF

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Publication number
US3498227A
US3498227A US736169A US3498227DA US3498227A US 3498227 A US3498227 A US 3498227A US 736169 A US736169 A US 736169A US 3498227D A US3498227D A US 3498227DA US 3498227 A US3498227 A US 3498227A
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US
United States
Prior art keywords
plunger
disk
chamber
axial
housing
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
US736169A
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English (en)
Inventor
Yasuo Kita
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.)
SANJYO FACTORY SHIMADZU SEISAK
SANJYO FACTORY SHIMADZU SEISAKUSHO Ltd
Original Assignee
SANJYO FACTORY SHIMADZU SEISAK
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Publication date
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Publication of US3498227A publication Critical patent/US3498227A/en
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
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/18—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having self-acting distribution members, i.e. actuated by working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/141—Details or component parts
    • F04B1/143—Cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/14—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders
    • F04B1/16—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis having stationary cylinders having two or more sets of cylinders or pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/12—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by varying the length of stroke of the working members

Definitions

  • This invention relates to improved axial plunger pumps, more particularly to axial plunger pumps which can run at a high speed and high pressure.
  • Axial plunger pumps are known as particularly suited for a high speed and high pressure operation and attempts have been made to provide improved axial plunger pumps for various kinds of use.
  • conventional axial plunger pumps are very complicated in construction and expensive.
  • the provision of a thrust bearing which has been considered heretofore as indisensable to axial plunger pumps makes a limitation of the running speed.
  • the speed which can be obtained with conventional axial plunger pumps is relatively high but not so extremely high.
  • the life of thrust bearings which are used is short.
  • the primary object of the invention is to provide new and improved axial plunger pumps which can dispense with any thrust bearing, whereby the above mentioned disadvantages which have been inevitable with conventional axial plunger pumps can be avoided.
  • Another object of the invention is to provide new and improved axial plunger pumps which are simple in constructions and can be economically manufactured.
  • a further object of the invention is to provide a new and improved means for cotnrolling the discharge of axial plunger pumps.
  • the axial plunger pump of the type to which the invention is applied comprises a housing forming an enclosed chamber therein and having an inlet and an outlet.
  • a driven shaft is rotatably supported by the housing to rotate within the enclosed chamber defined by the housing.
  • a cylindrical barrel is mounted within the housing. This cylindrical barrel is provided with a central aperture having a diameter larger than the diameter of the driven shaft so that said driven shaft extends through the central aperture.
  • the cylindrical barrel partitions liquid tightly in the discharge side of the chamber defined by the housing from the suction side of the chamber.
  • the discharge side communicates with the outlet while the suction side communicates with the inlet.
  • the cylindrical barrel is also provided with a plurality of cylindrical apertures extending in parallel to the axial direction of the shaft and satellitically arranged with respect to the central aperture.
  • a pair of disks are fixed on the rotating shaft in such a spaced relationship that the distance between said pair of disks continuously varies
  • one disk extends in a plane normal to the axis of the rotating shaft while the other extends an inclined plane with respect to the axis of the shaft.
  • the above mentioned relationship between the two disks can also be achieved by using two differently, for example, symmetrically inclined plates. In any case, the two disks are spaced from the opposite ends of the cylinder barrel, respectively.
  • an extensible plunger assembly is inserted in each of the satellitically arranged apertures of the cylinder barrel.
  • the extensible plunger assembly comprises a pair of axially slidable plug members inserted in the cylindrical aperture to close the opposite end openings thereof in such a spaced relation as to form an extensible pump chamber therebetween and a spring inserted therebetween for urging them to be alienated from each other.
  • the outer ends of the slidable plug members engaging sealingly and slidably with the two disks at their opposed surfaces, respectively.
  • Means are provided for communicating the pump chamber in each of the satellitically arranged apertures selectively with the suction and discharge side of the chamber defined by the housing so that the liquid to be pumped, for example, oil is introduced from the suction side to the pump chamber and then discharged from the pump chamber to discharge side during the extension and retraction operation of the plunger assembly, respectively.
  • each of the pump chambers is communicated with the discharge side of the chamber defined by the housing through a check valve and means are provided for communicating the pump chamber with the suction side of a chamber defined by the housing through an opening formed in at least one of the two disks and a passageway formed in the slidable plug member engaging the disk having said opening.
  • the passageway of the slidable plug member is capable of communicating with said opening of said disk during the extension stroke of the plunger assembly.
  • the cylinder lbarrel having a plurality of pump chambers may be so mounted within the housing as to be movable in the direction of the axis of the rotating shaft.
  • a port is provided for communicating the pump chamber with the suction side of the chamber defined by the housing when the plunger assembly is in an extended position, it becomes possible to control the discharge by changing the relative position of the plunger assembly with respect to the cylinder barrel since the effective stroke of each of the plunger assemblies is changed accordingly.
  • FIGURE 1 is a longitudinally sectional view, taken along the line 11 of FIGURE 2, of an axial plunger pump showing an embodiment of the invention
  • FIGURE 2 is a vertical sectional view at the line 22 of the FIGURE 1;
  • FIGURE 3 is a vertical sectional view at the line 33 of FIGURE 1;
  • FIGURE 4 is a longitudinal sectional view of an axial.
  • FIGURE 5 is a longitudinal sectional view" of an axial plunger pump similar to FIGURE 1 showing a further embodiment of the invention.
  • an axial plunger pump including a housing or casing generally indicated as 11.
  • the housing 11 comprises a pair of members 11a and 1112 which cooperate to form an enclosed chamber 12 having an inlet 13 and an outlet 14.
  • the reference numeral 15 indicates a screw connecting the cooperating members 11a and 11b to each other and the reference numeral 16 indicates packing seal means at contact surfaces of the cooperating members 11a and 11b.
  • the member 11a has an end opening 17 for receiving a bearing 18 which in turn supports rotata bly a driven shaft 19.
  • the reference numeral 20 indicates an end cover plate having oil seal means 21 for sealingly closing the opening 17 of the member 11a.
  • the driven shaft 19 which extends into the chamber 12 is connected to a drive mechanism (not shown) at the outside of the housing 11.
  • a pair of disks 22 and 23 are fixed on said driven shaft 19 within the enclosed chamber 12.
  • the disk 22 is mounted on the shaft in a normal relation to the axial direction thereof while the disk 23 is an inclined plate so that the distance between the two disks 22 and 23 continuously varies along a circular direction.
  • the disk 22 is secured by a screw 24 to the shaft 19 and the inclined disk 23 is secured by means of a key 25 and a nut 26 to the inner end of the shaft 19.
  • a cylinder barrel 27 which is provided with a central aperture 28 having a diameter larger than the outer diameter of the shaft 19 so that the shaft 19 extends through the aperture 28.
  • the cylindrical barrel is secured by screws (only one of which is indicated as 29) to the member 11a in a sealing engagement with use of O-rings 30 so that the outlet 14 is liquid-sealed tightly by the cylinder barrel pertitioned from the chamber 12.
  • the cylinder barrel 27 is provided at its outer periphery with an annular recess 31 which communicates with the outlet 14.
  • the cylinder barrel 27 is also provided with a plurality of elongated cylindrical apertures 32 arranged in a circle around the shaft 19, in other words, satellitically with respect to the central apertures 28, and extending in directions parallel to the shaft 19.
  • the extensible plunger assembly comprises a pair of slidable plug members 41 and 42 inserted in the cylindrical apertures 32 to close the opposite end openings thereof, respectively, so as to form a pump chamber 44 therebetween in cooperation with the cylindrical apertures 32.
  • a coil spring 43 is inserted between the inner ends of the slidable plug members 41 and 42 so as to urge the slidable members 41 and 42 outwardly, respectively.
  • the outer ends of the slidable members 41 and 42 abut sealingly and slidably on the opposed surfaces 22a and 23a of the disks 22 and 23, respectively.
  • the outer end of the member 41 is in direct contact with the surface 22a while the outer end of the member 32 engages through a swivel block 45 with the surface 23a.
  • the slidable member 41 is formed with a through oil passageway 46 for introducing oil into the pump chamber 44 through a window opening 47 formed in the perpendicular disk 22.
  • the window opening 47 is of an elon gated arc form as shown in FIGURE 2 so that the passageway 46 may communicate with the chamber 12 only for a certain rotating angle of the disk 22 which corresponds to the extension stroke of the plunger assembly is in contact with the inner surface 22a of the disk 22 is provided with a central cavity 49 and an annular recess 50 so that the oil pressure which will be produced in the pump chamber 44 is supplied between the contact surfaces 48 and 22a so as to provide a static pressure bearing system.
  • the slidable member 42 is provided with an oil passageway 51 extending in its axial direction and communicating with a central port 52 which is formed in the swivel block, 45.
  • the swivel block 45 is provided with a central cavity 53 and an annular recess 54 at its end surface 55 which is always in contact with the surface 23a of the inclined disk 23.
  • the port 52 communicates the central cavity 53 with the oil passageway 51.
  • the pump chamber 44 of each of the cylindrical apertures 32 is communicated to the annular recess 31 through a check valve means 56 which allows the pressure oil to lbe discharged to the annular recess 31 and then to the outlet 14.
  • the driven shaft 19 is provided with an axial oil passageways 60 and a pluarlity of radial oil passageway 61.
  • the axial passageway 60 is opened at its one end to the chamber near the inlet 11 and communicated at its inner end with the radial passageways 61 which are in turn opened at the position near the opposite surface of the perpendicular disk 22 to the surface 22a.
  • the shaft 19 is also rotatably carried by a needle bearing 70 which is in turn supported by the cylinder barrel 27 at its central aperture 28.
  • the two disks 22 and 23 are rotated with the outer ends of the slidable members 41 and the swivel blocks 45 engaging with the slidable members 42 sliding on the opposed surfaces 22a and 23a of the disks 22 and 23, respectively, under pressure and sealing condition.
  • the distance between the two disks 22 and 23 at the position of each of the plunger assemblies 40 varies continuously. While the slidable member 41 abuts against the disk 22 perpendicular to the axis of the shaft, there is no substantial movement of the member '41, the other slidable member 42 abutting against the inclined disk is enforced to a reciprocating movement along the cylindrical aperture 32 whereby the volume of the pump chamber 44 is varied.
  • the thrust due to the pumping operation of plunger assemblies 40 is fully supported by the two disks 22 and 23-.
  • the shaft 19' can, therefore, be supported by radial bearings 18 and 70 alone and dispense with any thrust bearing.
  • FIGURE 4 Another embodiment of the invention is illustrated in 'FIGURE 4, in which the same reference numerals as used in FIGURE 1 indicate the corresponding parts, respectively.
  • a pair of inclined disks 122 and 123 are fixed on the driven shaft 19. These two disks 122 and 123 extend symmetrically inclined planes, respectively, with respect to the axisof the shaft 19 so that both the two slidable members 141 and 142 which correspond to the members 41 and 44 illustrated in FIGURE 1 are enforced to simultaneous axially reciprocating movements which cooperate to produce the expansion and contraction operation of the pump chamber 44 formed between them.
  • the engagement of the member 141 to the inclined disk 122 is carried out in the same manner as the engagement of the member 142 to the inclined disk 123.
  • the latter is thus similar to the engagement of the member 42 to the inclined disk 23 illustrated in FIGURE 1.
  • the reference numeral 145 indicates the swivel block similar to the swivel block 45 of FIGURE 1.
  • Introduction of oil from the chamber 12 into the pump chamber 44 is carried out through both the passageways 146 and 151 which can communicate through central ports 152 with window openings 147 and 148 formed in the inclined disks 122 and 1.23, respectively.
  • Each of the window openings 147 and 148 is formed in a similar manner to the window opening 47 of the disk 47 shown in FIGURE 1.
  • the structure and the operation of the other parts of the embodiment of FIGURE 4 are substantially identical with those of corresponding parts illustrated in FIGURES 1 to 3.
  • FIGURE 5 A further modified embodiment of the invention is illustrated in FIGURE 5, in which the same reference numerals as used in FIGURE 1 indicate the corresponding parts, respectively.
  • the cylinder barrel 227 is engaged within the housing 11 so as to be slidable in an axial direction with the sealing angagement between the outer periphery of the barrel 227 and the inner wall of the housing 11 being maintained.
  • the reference numeral 201 indicates a screw for driving the cylinder barrel 227.
  • the screw 201 is operable by a handle 202 outside of the housing.
  • An axial plunger pump comprising:
  • a housing forming an enclosed chamber having an inlet and an outlet, said inlet being at one end of the housing and said outlet being intermediatelly disposed on the housing;
  • a cylindrical barrel having an external centrally disposed annular recess, a central through aperture, a plurality of through apertures satellitically arrangedwith respect to the central aperture and a port extending from each of the satellitically arranged through apertures to the annular recess, said cylindrical barrel being mounted within the housing in liquid sealing relationship and located to provide alignment of the annular recess with the chamber outlet;
  • first disk fixedly mounted on the driven shaft adjacent the cylindrical barrel and in proximity to the bearing mount, said first disk being disposed perpendicularly to the driven shaft;
  • each of said plunger assemblies comprising a first and a second slidably arranged section having axial through bores and a spring located between the sections to bias the sections away from each other and into engagement with the first and second disks respectively;
  • means for effecting communication between the chamber inlet and the axial bores in each of the plunger assemblies comprising an axial through bore in the driven shaft, radially extending bores in the driven shaft extending perpendicularly from the axial passageway in the driven shaft at a location adjacent to the first disk on the side thereof remote from the plunger assemblies, and a window opening in the first disk aligned with the bores in the plungers and extending for a length of at least two plunger openings;
  • a needle bearing arranged in the central aperture of the cylindrical barrel of the end nearest the inlet to support the driven shaft.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
US736169A 1967-06-14 1968-06-11 Axial plunger pump Expired - Lifetime US3498227A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP42038001A JPS5011086B1 (de) 1967-06-14 1967-06-14

Publications (1)

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US3498227A true US3498227A (en) 1970-03-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
US736169A Expired - Lifetime US3498227A (en) 1967-06-14 1968-06-11 Axial plunger pump

Country Status (5)

Country Link
US (1) US3498227A (de)
JP (1) JPS5011086B1 (de)
DE (1) DE1703594C3 (de)
FR (1) FR1569276A (de)
GB (1) GB1236613A (de)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3628425A (en) * 1968-12-13 1971-12-21 Messrs Mitsubishi Jukogyo Kk Fluid motor-pump construction
US3734647A (en) * 1971-09-07 1973-05-22 C Sparks Compressor pump
US3772965A (en) * 1970-11-30 1973-11-20 Shimadzu Corp Axial plunger pump
US3981630A (en) * 1974-06-19 1976-09-21 Gerard Leduc Hydraulic swash plate pumps
US4007663A (en) * 1974-02-01 1977-02-15 Mitsubishi Kogyo Kabushiki Kaisha Hydraulic pump of the axial piston type
US4072444A (en) * 1975-05-30 1978-02-07 Fabrique Nationale Herstal S.A. Axial piston pumps
US4793774A (en) * 1987-09-28 1988-12-27 Allied-Signal Inc. Variable displacement high pressure pump
US5062267A (en) * 1988-12-08 1991-11-05 Hydromatik Gmbh Hydrostatic transmission containing an axial piston motor located in a recess of a valve controlled axial piston pump
US5230610A (en) * 1989-04-05 1993-07-27 Zahnradfabrik Friedrichshafen Ag Axial piston pump
US5286173A (en) * 1991-10-23 1994-02-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Coolant gas guiding mechanism in swash plate type compressor
US5354181A (en) * 1992-02-28 1994-10-11 Hydro Rene Leduc Hydraulic piston pumps equipped with suction valve
US5401144A (en) * 1992-05-13 1995-03-28 Kabushiki Kaisha Toyoda Jisoshokki Seisakusho Swash plate type refrigerant compressor
US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
US5429482A (en) * 1991-09-11 1995-07-04 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocatory piston type compressor
US5440878A (en) * 1992-08-27 1995-08-15 Vernon E. Gleasman Variable hydraulic machine
US20050172798A1 (en) * 2004-02-11 2005-08-11 George Kadlicko Rotating group of a hydraulic machine
US20060153698A1 (en) * 2002-12-25 2006-07-13 Hiroyuki Makino Rotary fluid machine
US20100050627A1 (en) * 2008-08-29 2010-03-04 Bryan Edward Nelson Hydraulic circuit with variable displacement flow divider
CN103883493A (zh) * 2014-03-20 2014-06-25 西安交通大学 一种缸体静止的轴向柱塞泵
CN103899506A (zh) * 2014-04-11 2014-07-02 西安交通大学 一种缸体与壳体一体化的端面凸轮驱动式轴向柱塞泵
US20170030341A1 (en) * 2015-07-27 2017-02-02 Caterpillar Inc. Multi-plunger cryogenic pump having intake manifold

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5291509U (de) * 1975-12-29 1977-07-08
JPS5419982U (de) * 1977-07-12 1979-02-08
DE3437949A1 (de) * 1984-10-17 1986-04-17 Ludwig 7570 Baden-Baden Mokesch Verbesserte axialkolbenpumpe
EP0234006A3 (de) * 1985-12-26 1988-01-07 Allied Corporation Hochdruckpumpe mit veränderlicher Fördermenge
DE4210767C1 (en) * 1992-04-01 1993-02-18 Hydromobil Hydraulik Handelsgesellschaft Mbh, 3200 Hildesheim, De Flange for axial-flow piston pump - has separate turning portion, rotatable w.r.t. bearing housing, overlapping with central aperture jacket region of bearing housing
DE19803533A1 (de) * 1998-01-30 1999-08-05 Itt Mfg Enterprises Inc Axialkolbenpumpe

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2286301A (en) * 1941-02-28 1942-06-16 American Bosch Corp Liquid pump
US2709339A (en) * 1953-07-06 1955-05-31 Pacific Airmotive Corp Two-stage pumping system with automatic demand responsive control
US2821932A (en) * 1954-04-28 1958-02-04 Siam Fluid pumps or engines of the piston type
US2842068A (en) * 1954-10-05 1958-07-08 Sundin Eric Olov Piston pump
FR1188441A (fr) * 1956-03-22 1959-09-22 Offray Et Cie Perfectionnements aux pompes à pistons pour fluides liquides, destinées en particulier à actionner des moyens de levage pour bennes basculantes de véhicules poids lourds, et autres applications
US2990781A (en) * 1957-11-25 1961-07-04 Gen Motors Corp Wobble plate pump
US3085514A (en) * 1960-06-07 1963-04-16 Weatherhead Co Pump cooling apparatus
US3125034A (en) * 1964-03-17 Pump with radial cylinders
US3265008A (en) * 1964-01-06 1966-08-09 Boulton Aircraft Ltd Hydraulic apparatus

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3125034A (en) * 1964-03-17 Pump with radial cylinders
US2286301A (en) * 1941-02-28 1942-06-16 American Bosch Corp Liquid pump
US2709339A (en) * 1953-07-06 1955-05-31 Pacific Airmotive Corp Two-stage pumping system with automatic demand responsive control
US2821932A (en) * 1954-04-28 1958-02-04 Siam Fluid pumps or engines of the piston type
US2842068A (en) * 1954-10-05 1958-07-08 Sundin Eric Olov Piston pump
FR1188441A (fr) * 1956-03-22 1959-09-22 Offray Et Cie Perfectionnements aux pompes à pistons pour fluides liquides, destinées en particulier à actionner des moyens de levage pour bennes basculantes de véhicules poids lourds, et autres applications
US2990781A (en) * 1957-11-25 1961-07-04 Gen Motors Corp Wobble plate pump
US3085514A (en) * 1960-06-07 1963-04-16 Weatherhead Co Pump cooling apparatus
US3265008A (en) * 1964-01-06 1966-08-09 Boulton Aircraft Ltd Hydraulic apparatus

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3628425A (en) * 1968-12-13 1971-12-21 Messrs Mitsubishi Jukogyo Kk Fluid motor-pump construction
US3772965A (en) * 1970-11-30 1973-11-20 Shimadzu Corp Axial plunger pump
US3734647A (en) * 1971-09-07 1973-05-22 C Sparks Compressor pump
US4007663A (en) * 1974-02-01 1977-02-15 Mitsubishi Kogyo Kabushiki Kaisha Hydraulic pump of the axial piston type
US3981630A (en) * 1974-06-19 1976-09-21 Gerard Leduc Hydraulic swash plate pumps
US4072444A (en) * 1975-05-30 1978-02-07 Fabrique Nationale Herstal S.A. Axial piston pumps
US4793774A (en) * 1987-09-28 1988-12-27 Allied-Signal Inc. Variable displacement high pressure pump
US5062267A (en) * 1988-12-08 1991-11-05 Hydromatik Gmbh Hydrostatic transmission containing an axial piston motor located in a recess of a valve controlled axial piston pump
US5230610A (en) * 1989-04-05 1993-07-27 Zahnradfabrik Friedrichshafen Ag Axial piston pump
US5429482A (en) * 1991-09-11 1995-07-04 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Reciprocatory piston type compressor
US5286173A (en) * 1991-10-23 1994-02-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Coolant gas guiding mechanism in swash plate type compressor
US5354181A (en) * 1992-02-28 1994-10-11 Hydro Rene Leduc Hydraulic piston pumps equipped with suction valve
US5401144A (en) * 1992-05-13 1995-03-28 Kabushiki Kaisha Toyoda Jisoshokki Seisakusho Swash plate type refrigerant compressor
US5440878A (en) * 1992-08-27 1995-08-15 Vernon E. Gleasman Variable hydraulic machine
US5417552A (en) * 1992-10-20 1995-05-23 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Swash plate type variable displacement compressor
US20060153698A1 (en) * 2002-12-25 2006-07-13 Hiroyuki Makino Rotary fluid machine
US20050172798A1 (en) * 2004-02-11 2005-08-11 George Kadlicko Rotating group of a hydraulic machine
US7402027B2 (en) * 2004-02-11 2008-07-22 Haldex Hydraulics Corporation Rotating group of a hydraulic machine
US20100050627A1 (en) * 2008-08-29 2010-03-04 Bryan Edward Nelson Hydraulic circuit with variable displacement flow divider
CN103883493A (zh) * 2014-03-20 2014-06-25 西安交通大学 一种缸体静止的轴向柱塞泵
CN103883493B (zh) * 2014-03-20 2015-12-09 西安交通大学 一种缸体静止的轴向柱塞泵
CN103899506A (zh) * 2014-04-11 2014-07-02 西安交通大学 一种缸体与壳体一体化的端面凸轮驱动式轴向柱塞泵
CN103899506B (zh) * 2014-04-11 2016-02-24 西安交通大学 一种缸体与壳体一体化的端面凸轮驱动式轴向柱塞泵
US20170030341A1 (en) * 2015-07-27 2017-02-02 Caterpillar Inc. Multi-plunger cryogenic pump having intake manifold

Also Published As

Publication number Publication date
JPS5011086B1 (de) 1975-04-26
DE1703594C3 (de) 1974-07-11
FR1569276A (de) 1969-05-30
DE1703594B2 (de) 1973-12-13
DE1703594A1 (de) 1972-03-09
GB1236613A (en) 1971-06-23

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