EP0608144B1 - Axialkolbenpumpe - Google Patents

Axialkolbenpumpe Download PDF

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Publication number
EP0608144B1
EP0608144B1 EP19940300461 EP94300461A EP0608144B1 EP 0608144 B1 EP0608144 B1 EP 0608144B1 EP 19940300461 EP19940300461 EP 19940300461 EP 94300461 A EP94300461 A EP 94300461A EP 0608144 B1 EP0608144 B1 EP 0608144B1
Authority
EP
European Patent Office
Prior art keywords
swashplate
cylinder block
piston pump
pump according
valve plate
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
EP19940300461
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English (en)
French (fr)
Other versions
EP0608144A3 (de
EP0608144A2 (de
Inventor
Chang Chun Du
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.)
David Brown Hydraulics Ltd
Original Assignee
David Brown Hydraulics Ltd
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 David Brown Hydraulics Ltd filed Critical David Brown Hydraulics Ltd
Publication of EP0608144A2 publication Critical patent/EP0608144A2/de
Publication of EP0608144A3 publication Critical patent/EP0608144A3/de
Application granted granted Critical
Publication of EP0608144B1 publication Critical patent/EP0608144B1/de
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
    • F04B1/20—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 rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2021—Details or component parts characterised by the contact area between cylinder barrel and valve plate
    • F04B1/2028—Bearings
    • 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
    • F04B1/20—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 rotary cylinder block
    • F04B1/2007—Arrangements for pressing the cylinder barrel against the valve plate, e.g. by fluid pressure
    • 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
    • F04B1/20—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 rotary cylinder block
    • F04B1/2014—Details or component parts
    • F04B1/2078—Swash plates
    • F04B1/2085—Bearings for swash plates or driving axles

Definitions

  • the present invention relates to an axial piston pump of the type generally used in hydraulic systems.
  • a conventional axial piston pump comprises a rotating cylinder block which is supported on a drive shaft which is, in turn, supported on bearings, to enable the shaft and cylinder block to rotate together.
  • the block contains a plurality of pistons.
  • Each piston is fitted, by means of a universal joint, with a slipper pad.
  • the slipper pads contact and react against a load surface of a swashplate which surrounds the drive shaft.
  • the load surface is inclined at an angle to the axis of rotation of the drive shaft.
  • the swashplate is held stationary in relation to the rotating cylinder block. Therefore, the action of the slipper pads against the angled load face of the swashplate causes a reciprocating action in the pistons.
  • the reciprocation of the pistons causes oil to be drawn into the cylinder via an inlet port located in the pump housing, a kidney-shaped inlet port situated in a valve plate located between the cover and an opposed, adjacent valve face of the cylinder block.
  • the valve face of the cylinder block and the opposed face of the valve plate lie in a plane perpendicular to the rotational axis of the drive shaft.
  • the oil is discharged via slots in the valve face of the cylinder block and on through a kidney-shaped outlet port in the valve plate. This discharged oil is subsequently directed through loading pistons housed within the cover and finally on through an outlet port provided in the cover.
  • the pump design must ensure that clearance between valve plate and cylinder block face is controlled in order to minimise leakage without incurring excessive frictional losses.
  • the first method has the valve plate rigidly mounted to the pump casing with the cylinder block connected to the drive shaft by a loose fitting spline.
  • the main pumping pistons load the cylinder block hydrostatically against the valve plate.
  • the clearance in the spline allows the cylinder block to articulate, thus accommodating manufacturing tolerances and deflections arising from the loads generated within the pump. This articulation facilitates the alignment of the cylinder block valve face and the valve plate.
  • Such a conventional pump is shown in accompanying figures 7a and 7b.
  • US 2 241 701 discloses a fluid pressure energy translating device which can be used as a pump.
  • this device an axially displaceable cylinder block is urged against a static valve plate.
  • the ports in the valve plate are provided with perimeteral seals which are urged against the cylinder block. Due to the arcuate shape of the ports, these seals are arcuate also.
  • EP-A-175 206 discloses a similar arrangement.
  • the second configuration has the cylinder block rigidly mounted to the drive shaft and the valve plate is floating in the axial direction.
  • the valve plate is loaded against the cylinder block by a series of loading pistons.
  • the second arrangement affords the advantage that the low inertia valve plate can follow the cylinder block runnout with minimum vibration.
  • the higher inertia of the floating cylinder block version leads to high amplitude vibrations and consequently the valve plate clearance in adversely affected.
  • the loading pistons are used to load the valve plate onto the cylinder block in the axial direction of the shaft and are designed to prevent separation of the porting interface valve face, thereby minimising a loss of pressurized fluid into the pump casing.
  • the displacement of the pump can be varied from zero to a maximum by altering the angle of the swashplate using, for example, control pistons situated within the pump housing.
  • the control system for controlling the angle of the swashplate, requires that the friction between a rear, curved side of the swashplate and a complementary, but inversely, curved swashplate cradle (which seats the swashplate) be kept to a minimum. This can be achieved by means of a hydrostatic bearing system which is supplied with lubricating oil at a pump outlet pressure. Alternatively, a roller bearing can be used, but this feature has the disadvantages of high cost, increased noise level and limited life.
  • the valve plate provides a mechanism for transferring fluid to and from the cylinder block. It is important to maintain the design clearance between the valve plate and cylinder block in order to optimize leakage and frictional losses. If loading is excessive, it results in seizure between the static valve plate and the rotating cylinder block.
  • valve plate has been loaded against the cylinder block by four (for example) circular loading pistons (DE-B-1 653 565 illustrates a machine with circular loading pistons).
  • Each of the discrete pistons imparts a localised load onto the valve plate. This results in distortion of the valve plate, leading to undesirable variation in the clearance between the valve plate and the cylinder block and in the extreme, metal to metal contact can occur. In areas of high clearance leakage increases and the pump's efficiency is reduced. Areas of low clearance increase the risk of seizure and the pump's reliability is adversely affected at extreme operating conditions.
  • the conventional way of providing the hydrostatic low friction bearing between the rear of the swashplate and the swashplate cradle requires a feed of high pressure oil from the pump outlet port. This has conventionally been achieved by means of a series of interconnecting drillings from the outlet port at one end of the pump, via the pump casing, to the swashplate bearing which is at the opposite end of the pump to the outlet port.
  • the drilling provided in the pump casing is complicated and relatively expensive to manufacture.
  • the present invention sets out to provide an axial piston pump in which the leakage gap between the cylinder block and the valve plate is minimised but without causing seizure or excessive frictional losses.
  • the invention sets out to provide an arrangement in which distortion of the valve plate is obviated or mitigated, thereby avoiding local variations in the thickness of the oil film between the valve plate and the cylinder block.
  • an axial piston pump comprising a drive shaft (2), a cylinder block (4) fixed to, and rotatable with, the drive shaft (2), a plurality of first pistons (6a-6i) provided within the cylinder block (4), a swashplate (12) situated at one axial end of the cylinder block (4) for causing reciprocation of the pistons (6a-6i) when the said cylinder block (4) is rotated, and an axially moveable valve plate (26) situated at a second axial end of the cylinder block (4) and held stationary relative to the direction of rotation of the cylinder block (4) and urged against the said second end of the cylinder block (4) to form a hydrostatic seal between the cylinder block (4) and a bearing face (52) of the said valve plate (26) which addresses the cylinder block, wherein the valve plate (26) is urged against the cylinder block (4) by means of a second piston (60), the said second piston (60) having a load face which is axially aligned with a portion of
  • valve plate loading becomes evenly distributed, resulting in less distortion of the valve plate.
  • this reduction in distortion of the valve plate local distortions in the oil film thickness caused by using discrete pistons can be avoided, providing less leakage, minimum friction and higher reliability.
  • the valve plate distributes the loading more evenly, the valve plate is less susceptible to deformation and the thickness of the valve plate can be reduced. This means that costs can be saved.
  • the general construction of the pump according to the present invention is the same as that of the conventional pump described above.
  • the pump comprises a drive shaft 2 which is fitted with a cylinder block 4.
  • the cylinder block 4 is keyed to the said drive shaft 2 by means of a portion 7 of the drive shaft 2 which is generally square in cross-section and fits within a similarly profiled recess in the cylinder block 4.
  • the cylinder block 4 is fixed to the drive shaft 2 in such a manner that rotation of the drive shaft 2 causes the cylinder block 4 to rotate.
  • the drive shaft is supported by bearings 3 and 5 to facilitate rotation.
  • the cylinder block 4 is fitted with nine pistons 6a - 6i.
  • Each piston is reciprocally movable in a direction parallel to the axis of rotation of the cylinder block assembly.
  • a ball 8a - 8e is provided at the end of each piston and is received within a socket in a respective slipper pad 10a - 10e.
  • a swashplate 12 is provided within a swashplate cradle 14.
  • the swashplate 12 has a curved back 16, which is part-circular in profile.
  • the swashplate cradle 14 is provided with a swashplate seating surface 18 which is curved to the same degree as the rear of the swashplate 16. This allows the swashplate to swivel within the swashplate cradle 14.
  • the swashplate 12 will be positioned within the swashplate cradle 14 with its load face 20 inclined such that a normal to the load face 20 is at an angle with the rotational axis of the drive shaft 2.
  • the angle of inclination of the swashplate 12 can be adjusted by means of a pair of control pistons (not completely shown) which move an arm 24 which is received within the swashplate 12.
  • the angle of inclination of the swashplate is adjusted by means of the control pistons 22 which move the arm, thereby moving the swashplate.
  • the direction of movement of the pistons 22 is into and out of the page as seen in Figure 1.
  • the rotation of the cylinder block 4 causes the pistons 6a - 6i to reciprocate as the piston slippers 10a - 10i act against the load face of the swashplate 12.
  • a valve plate 26 is provided at the other end of the cylinder block 4.
  • the valve plate 26 is loaded against the valve face of the cylinder block by four loading pistons 30a-30d. These pistons 30a-30d serve to prevent separation of the valve plate from the cylinder block valve face, thus minimising the loss of pressurized fluid into the pump casing. Each piston is provided with a seal 31a-31d about its perimeter.
  • the valve plate is provided with a kidney-shaped inlet port 28 and two kidney-shaped outlet ports 29a and 29b.
  • a kidney-shaped recess is provided on the face 52 of the valve plate 26 which addresses the cylinder block. This recess communicates with the outlet ports 29a and 29b.
  • a spiral groove bearing 50 is provided in a peripheral region of the cylinder block facing face 52 of the valve plate 26.
  • the spiral groove bearing 50 is formed from a plurality of grooves 54, which are formed so as to spiral inwardly from the periphery of the cylinder block facing face 52 of the valve plate towards the centre of this face 52.
  • valve plate 26 Because the valve plate is held stationary relative to the rotating cylinder block during use , oil is driven into the grooves of the spiral groove bearing 50 and creates a hydrodynamic pressure. This provides a self-compensating effect and significantly reduces the risk of seizure. This arrangement enables the valve plate 26 to be loaded more heavily, thereby reducing leakage.
  • valve plate loading pistons 30a - 30d are replaced with a single kidney-shaped piston 60. This can be seen in Figure 4.
  • the piston 60 comprises six outlet apertures 62a - 62f. These are aligned with six similarly sized and shaped outlet apertures 64a - 64f provided in a single kidney-shaped outlet port 66 of the valve plate 26. During operation of the pump, oil can escape by means of the outlet apertures 64a - 64f and subsequently on out through the outlet apertures 62a - 62f in the piston 60.
  • the kidney-shaped inlet port of the valve plate 26 is identical to that of the conventional valve plate 26.
  • the kidney shaped piston 60 is fitted with a seal 61 about its perimeter; this corresponds to the seals 31a-31d of the prior art loading pistons.
  • kidney-shaped piston 60 will be used in conjunction with a spiral groove bearing 50, but it will operate successfully without the presence of such a spiral groove bearing.
  • valve plate 26 plus loading piston 60 could be manufactured as a single integral component.
  • a pair of hydrostatic bearings 70 and 72 are provided in the curved surface 16 of the swashplate 12. This can best be seen from Figure 5. These bearings are fed with oil at pump outlet pressure.
  • the high pressure oil is supplied to the hydrostatic bearings 70 and 72 from the outlet port via openings provided in the nine pumping pistons 6a - 6i, through holes in the respective slipper pads 10a - 10i and via a feed hole 80 which extends through the wearplate 13 and the swashplate 12.
  • the feed hole 80 directly feeds hydrostatic bearing 72.
  • Hydrostatic bearing 70 is fed by means of a drilling 82 (shown in Figure 1 and schematically in Figure 5) in the swashplate cradle 14. Drilling 82 connects the two bearings 70 and 72.
  • An orifice 83 is fitted in the drilling 80 to control the pressure at the bearings and limit the leakage rate.
  • feed hole 80 relative to the outset port will determine the pressure of the oil supplied to the bearings. For maximum pressure at the hydrostatic bearings 70, 72, the feed hole and outlet port would need to be aligned.
  • This arrangement reduces the complexity of machining components to provide the oil supply and thereby reduces the cost of the pump. It also provides a self-cleaning action for the control orifice 83, reduces fiction between swashplate 12 and cradle 14 and minimises leakage.
  • the invention could be incorporated in the hydraulic motor variant of the pump.
  • the fitting of two pistons permits rotation in either the clockwise or anit-clockwise direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Reciprocating Pumps (AREA)

Claims (16)

  1. Axialkolbenpumpe, die aufweist: eine Antriebswelle (2), einen Zylinderblock (4), der an der Antriebswelle (2) befestigt und mit dieser drehbar ist, eine Vielzahl von ersten Kolben (6a-6i), die innerhalb des Zylinderblockes (4) vorhanden sind, eine Taumelscheibe (12), die sich an einem axialen Ende des Zylinderblockes (4) befindet, um die Hin- und Herbewegung der Kolben (6a-6i) hervorzurufen, wenn der Zylinderblock (4) gedreht wird, und eine axial bewegliche Ventilplatte (26), die sich an einem zweiten axialen Ende des Zylinderblockes (4) befindet und relativ zur Drehungsrichtung des Zylinderblockes (4) stationär gehalten und gegen das zweite Ende des Zylinderblockes (4) gedrückt wird, um eine hydrostatische Abdichtung zwischen dem Zylinderblock (4) und einer tragenden Fläche (52) der Ventilplatte (26) zu bilden, die zum Zylinderblock gerichtet ist, wobei die Ventilplatte (26) gegen den Zylinderblock (4) mittels eines zweiten Kolbens (60) gedrückt wird, und wobei der zweite Kolben (60) eine Lastfläche aufweist, die axial mit einem Abschnitt der tragenden Fläche (52) der Ventilplatte ausgerichtet ist; dadurch gekennzeichnet, daß die Lastfläche des zweiten Kolbens (60) bogenförmig ist.
  2. Axialkolbenpumpe nach Anspruch 1, bei der der zweite Kolben (60) eine nierenförmige Lastfläche aufweist.
  3. Axialkolbenpumpe nach Anspruch 1 oder 2, bei der der zweite Kolben (60) eine Vielzahl von Austrittsöffnungen (62a-62f) aufweist; wobei jede Öffnung (62a-62f) mit einer entsprechenden gleichermaßen gestalteten Austrittsöffnung (64a-64f) in der Ventilplatte (26) ausgerichtet ist.
  4. Axialkolbenpumpe nach einem der vorhergehenden Ansprüche, bei der die Ventilplatte (26) und der zweite Kolben (60) in einem Stück hergestellt sind.
  5. Axialkolbenpumpe nach einem der vorhergehenden Ansprüche, die außerdem dadurch gekennzeichnet ist, daß zwischen der Ventilplatte (26) und dem Zylinderblock (4) ein Spiralrillenlager (50) vorhanden ist.
  6. Axialkolbenpumpe nach Anspruch 5, bei der die Rillen (54) des Spiralrillenlagers (50) in der Ventilplatte (26) vorhanden sind.
  7. Axialkolbenpumpe nach Anspruch 5, bei der die Rillen des Spiralrillenlagers (50) im Zylinderblock (4) vorhanden sind.
  8. Axialkolbenpumpe nach Anspruch 5, 6, 7, bei der das Spiralrillenlager (50) eine Vielzahl von spiralförmig gestalteten Rillen aufweist.
  9. Axialkolbenpumpe nach einem der Ansprüche 5 bis 7, bei der das Spiralrillenlager aus einer Vielzahl von geradlinigen Rillen gebildet wird.
  10. Axialkolbenpumpe nach einem der Ansprüche 5 bis 9, bei der die Rillen (54), die das Spiralrillenlager (50) bilden, sehr flach sind.
  11. Axialkolbenpumpe nach einem der vorhergehenden Ansprüche, bei der die Taumelscheibe (12) mit einer gekrümmten Rückseite versehen ist, wobei die gekrümmte Rückseite innerhalb einer gekrümmten Aussparung in einer Taumelscheibenwiege (14) sitzt, und wobei sich die Taumelscheibe (12) innerhalb der Aussparung (14) drehen kann; außerdem dadurch gekennzeichnet, daß ein hydrostatisches Lager (70, 72) zwischen der gekrümmten Rückseite der Taumelscheibe (12) und der gekrümmten Aussparung der Taumelscheibenwiege (14) gebildet wird, und daß Hochdrucköl dem hydrostatischen Lager (70, 72) über einen Kanal, der in mindestens einem der Kolben vorhanden ist, und über eine Loch (80) zugeführt wird, das im Körper der Taumelscheibe (12) vorhanden ist.
  12. Axialkolbenpumpe nach Anspruch 11, bei der ein Paar hydrostatische Lager (70, 72) zwischen der Taumelscheibenrückseite und der Taumelscheibenwiege vorhanden ist.
  13. Axialkolbenpumpe nach Anspruch 12, bei der ein erstes hydrostatisches Lager (72) direkt mittels des in der Taumelscheibe (12) vorhandenen Loches (80) versorgt wird, und das andere (70) über das erste hydrostatische Lager (72) und über einen im Körper der Taumelscheibenwiege (14) vorhandenen Kanal (82), wobei der Kanal (82) die zwei Lager (70, 72) verbindet.
  14. Axialkolbenpumpe nach einem der Ansprüche 11 bis 12, die außerdem eine Steueröffnung (83) aufweist, die im Loch (80) in der Taumelscheibe (12) für das Abstimmen des Druckes im hydrostatischen Lager oder den Lagern (70, 72) vorhanden ist.
  15. Axialkolbenpumpe nach einem der Ansprüche 11 bis 14, bei der jeder Kolben (6a-6i) ein Loch aufweist, um die Zuführung von Öl zur Taumelscheibe (12) zu gestatten.
  16. Axialkolbenpumpe nach Anspruch (15), bei der die Lastfläche der Taumelscheibe mit einer Verschleißscheibe (13) versehen ist, auf der sich die Gleitstücke (10a-10i) bewegen, die an den entsprechenden Enden der Kolben (6a-6i) vorhanden sind; wobei jedes Gleitstück (10a-10i) einen Kanal aufweist, damit das Öl aus seinem entsprechenden Kolben (6a-6i) austreten kann, und wobei die Verschleißscheibe (13) einen Kanal aufweist, der eine Verbindung mit dem Loch (80) in der Taumelscheibe (12) zeigt.
EP19940300461 1993-01-21 1994-01-21 Axialkolbenpumpe Expired - Lifetime EP0608144B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB9301163A GB2274491B (en) 1993-01-21 1993-01-21 Axial piston pump
GB9301163 1993-01-21

Publications (3)

Publication Number Publication Date
EP0608144A2 EP0608144A2 (de) 1994-07-27
EP0608144A3 EP0608144A3 (de) 1994-12-21
EP0608144B1 true EP0608144B1 (de) 1997-06-18

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ID=10729077

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19940300461 Expired - Lifetime EP0608144B1 (de) 1993-01-21 1994-01-21 Axialkolbenpumpe

Country Status (3)

Country Link
EP (1) EP0608144B1 (de)
DE (1) DE69403819D1 (de)
GB (1) GB2274491B (de)

Cited By (2)

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Publication number Priority date Publication date Assignee Title
US6186748B1 (en) * 1998-07-21 2001-02-13 Kawasaki Jukogyo Kabushiki Kaisha Axial piston pump
CN105164414A (zh) * 2013-05-22 2015-12-16 贺德克传动中心有限公司 液压泵和用于这样的液压泵的活塞

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DE19953183C2 (de) * 1999-11-04 2001-12-06 Erich Scheugenpflug Mikrodosierer
US20060120882A1 (en) * 2004-08-20 2006-06-08 Glenn Jordan Motor or pump assemblies
WO2006130837A2 (en) * 2005-06-02 2006-12-07 Kmt Waterjet Systems, Inc. High pressure rotary pump
DE102005030485A1 (de) * 2005-06-28 2007-01-04 Framatome Anp Gmbh Pumpenvorrichtung für kerntechnische Anlagen
EP1780410B1 (de) 2005-10-26 2013-04-03 Poclain Hydraulics Hydraulische Taumelscheibemaschine mit variabler Kapazität
DE102006037690A1 (de) * 2006-08-11 2008-02-14 Robert Bosch Gmbh Axialkolbenmaschine
JP5286408B2 (ja) * 2008-04-01 2013-09-11 パーデュ リサーチ ファンデーション アキシャルすべり軸受とその動力損失低減方法
DE102012214830B4 (de) * 2012-08-21 2022-06-30 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit verstellbarer Schrägscheibe oder Schenkwiege und zugehörigem Gleitlager mit hydrostatischem Druckfeld, dessen Randkonturausbildung den Leckagestrom ins Gehäuse minimiert
DE102013221623A1 (de) * 2013-10-24 2015-04-30 Robert Bosch Gmbh Axialkolbenmaschine
DE102017105610A1 (de) * 2017-03-16 2018-09-20 Volkswagen Aktiengesellschaft Axialkolbenmotor und Kreisprozessvorrichtung
CN108916037B (zh) * 2018-10-23 2019-02-19 江苏恒立液压科技有限公司 具有斜盘座定位装置的液压柱塞泵
KR102592519B1 (ko) * 2021-07-28 2023-10-24 주식회사 모트롤 씨일 커버 및 이를 포함하는 구동장치

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6186748B1 (en) * 1998-07-21 2001-02-13 Kawasaki Jukogyo Kabushiki Kaisha Axial piston pump
CN105164414A (zh) * 2013-05-22 2015-12-16 贺德克传动中心有限公司 液压泵和用于这样的液压泵的活塞
CN105164414B (zh) * 2013-05-22 2018-01-12 贺德克传动中心有限公司 液压泵和用于这样的液压泵的活塞

Also Published As

Publication number Publication date
GB9301163D0 (en) 1993-03-10
GB2274491A (en) 1994-07-27
EP0608144A3 (de) 1994-12-21
EP0608144A2 (de) 1994-07-27
GB2274491B (en) 1996-09-04
DE69403819D1 (de) 1997-07-24

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