EP0608144A2 - Pompe à pistons axiaux - Google Patents

Pompe à pistons axiaux Download PDF

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Publication number
EP0608144A2
EP0608144A2 EP94300461A EP94300461A EP0608144A2 EP 0608144 A2 EP0608144 A2 EP 0608144A2 EP 94300461 A EP94300461 A EP 94300461A EP 94300461 A EP94300461 A EP 94300461A EP 0608144 A2 EP0608144 A2 EP 0608144A2
Authority
EP
European Patent Office
Prior art keywords
cylinder block
swashplate
valve plate
piston pump
pistons
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.)
Granted
Application number
EP94300461A
Other languages
German (de)
English (en)
Other versions
EP0608144A3 (fr
EP0608144B1 (fr
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
Hamworthy 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, Hamworthy Hydraulics Ltd filed Critical David Brown Hydraulics Ltd
Publication of EP0608144A2 publication Critical patent/EP0608144A2/fr
Publication of EP0608144A3 publication Critical patent/EP0608144A3/fr
Application granted granted Critical
Publication of EP0608144B1 publication Critical patent/EP0608144B1/fr
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.
  • 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.
  • 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.
  • 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.
  • the invention sets out to provide an arrangement in which oil can be supplied to a hydrostatic bearing provided between the swashplate and the swashplate cradle, but without requiring a complicated drilling of the pump casing.
  • an axial piston pump comprising a drive shaft, a cylinder block rotatable with the drive shaft, a plurality of pistons provided within the cylinder block, a swashplate situated at one axial end of the cylinder block for causing reciprocation of the pistons when the said cylinder block is rotated, and a valve plate situated at a second axial end of the cylinder block; wherein eitherone of the cylinder block orvalve plate is urged against the other to form a hydrostatic seal between the cylinder block and a face of the said valve plate; characterised in that a spiral groove bearing is provided between the valve plate and the cylinder block.
  • the cylinder block is fixed relative to the axial direction of the drive shaft and the valve plate is urged against the cylinder block.
  • valve plate can be fixed in the axial direction of the drive shaft and the cylinder block urged against it.
  • the spiral groove bearing will be provided in the valve plate. It can be formed by a plurality of spirally orientated grooves. Alternatively, the grooves can be straight. If preferred, the spiral groove bearing can be provided in the cylinder block.
  • the grooves of the spiral groove bearing can be very shallow.
  • an axial piston pump comprising a drive shaft, a cylinder block rotatable with the drive shaft, a plurality of first pistons provided within the cylinder block, a swashplate situated at one axial end of the cylinder block for causing reciprocation of the pistons when the said cylinder block is rotated, a valve plate situated at a second axial end of the cylinder block and held stationary relative to the direction of rotation of the cylinder block and urged against the said second end of the cylinder block to form a hydrostatic seal between the cylinder block and a face of the said valve plate, wherein the valve plate is urged against the cylinder block by means of a second piston.
  • the second piston has an arcuate load face.
  • the piston will be kidney-shaped.
  • an axial piston pump comprising a drive shaft, a cylinder block rotatable with the drive shaft, a plurality of pistons provided within the cylinder block, a swashplate situated at one axial end of the cylinder block for causing reciprocation of the pistons when the cylinder block is rotated; the said swashplate being provided with a curved back, the curved back being seated within a curved recess in a swashplate cradle the said swashplate being capable of swivelling within the said recess; characterised in that a hydrostatic bearing is formed between the said curved back of the swash plate and the curved recess of the swashplate cradle, and high pressure oil is supplied to the said hydrostatic bearing via a passage provided in at least one of the said pistons and via a hole provided in the body of the said swashplate.
  • a pair of hydrostatic bearings are provided between the swashplate back and the swashplate cradle.
  • One of these may be fed directly by means of the said drilling in the swashplate and the other is fed via the first bearing and via a drilling provided in the body of the swashplate cradle, which links the two bearings together.
  • a control orifice can be provided in the feed drilling in the swash plate to modulate the pressure at the hydrostatic bearings and minimise the leakage.
  • Each of the pistons can comprise a hole for allowing oil to be fed to the swashplate.
  • the load surface of the swashplate is provided with a wear plate, upon which slippers, provided at the respective ends of the pistons, move.
  • the slippers each comprise a drilling to allow oil to escape from their respective piston and the wearplate comprises a drilling which communicates with the drilling in the swashplate.
  • 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 block4 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 swash plate 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.
  • Avalve 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 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. Because 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.
  • 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 limitthe leakage rate.
  • feed hole 80 relative to the outlet 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 third aspect can be combined in a single pump along with one or more of the first and second aspect of the invention. Alternatively, the third aspect of the invention can be employed separately.
  • the first and third aspect of the invention can be used in a floating cylinder block pump described earlier. All three aspects of the invention could be incorporated in the hydraulic motor variant of the pump.
  • arcuate loading piston principle to motors it wi be necessary to provide two loading pistons, one adjacent to the supply port (equivalent to the pump's high pressure outlet port) and the second adjacent to the return port (equivalent to the pump's low pressure inlet port).
  • 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)
EP19940300461 1993-01-21 1994-01-21 Pompe à pistons axiaux Expired - Lifetime EP0608144B1 (fr)

Applications Claiming Priority (2)

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

Publications (3)

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

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ID=10729077

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19940300461 Expired - Lifetime EP0608144B1 (fr) 1993-01-21 1994-01-21 Pompe à pistons axiaux

Country Status (3)

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

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006023923A1 (fr) * 2004-08-20 2006-03-02 R. Sanderson Management, Inc. Dispositif hydraulique
WO2006130837A2 (fr) * 2005-06-02 2006-12-07 Kmt Waterjet Systems, Inc. Pompe rotative haute pression
DE102005030485A1 (de) * 2005-06-28 2007-01-04 Framatome Anp Gmbh Pumpenvorrichtung für kerntechnische Anlagen
EP1780410A1 (fr) * 2005-10-26 2007-05-02 Poclain Hydraulics Machine hydraulique à déplacement variable avec plateau en biais
WO2008017557A1 (fr) * 2006-08-11 2008-02-14 Robert Bosch Gmbh Machine à pistons axiaux
WO2014029588A1 (fr) * 2012-08-21 2014-02-27 Robert Bosch Gmbh Machine hydrostatique à piston axial à plateau oblique ou patin oscillant réglable, et patin oscillant
WO2014187547A1 (fr) * 2013-05-22 2014-11-27 Hydac Drive Center Gmbh Pompe hydraulique et piston pour une pompe hydraulique de ce type
WO2015058896A1 (fr) * 2013-10-24 2015-04-30 Robert Bosch Gmbh Machine à pistons axiaux
KR20230017955A (ko) * 2021-07-28 2023-02-07 주식회사 모트롤 씨일 커버 및 이를 포함하는 구동장치

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3154329B2 (ja) * 1998-07-21 2001-04-09 川崎重工業株式会社 アキシャルピストンポンプ
DE19953183C2 (de) * 1999-11-04 2001-12-06 Erich Scheugenpflug Mikrodosierer
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
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

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GB1026343A (en) * 1962-02-19 1966-04-20 Lucas Industries Ltd Hydraulic pumps and motors
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FR2124739A5 (fr) * 1971-01-12 1972-09-22 Bosch
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EP0175206A1 (fr) * 1984-09-05 1986-03-26 Hitachi, Ltd. Machine à fluide
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EP0241898A2 (fr) * 1986-04-15 1987-10-21 The Oilgear Company Lubrification du plateau oscillant pour dispositif de déplacement de fluide à pistons axiaux
US4903577A (en) * 1987-07-22 1990-02-27 Linde Aktiengesellschaft Adjustable axial piston machine with a swash plate design
DE4125391A1 (de) * 1990-08-01 1992-02-06 Toyoda Automatic Loom Works Axialkolbenpumpe mit einer festen steuerscheibe fuer die hin- und herbewegung von kolben

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CH448748A (de) * 1966-03-26 1967-12-15 Thoma Jean Ulrich Dipl Phys Et Einrichtung zum Abstützen des Zylinderblockes auf dem Verteiler einer Axialkolbenmaschine
DE1653565B1 (de) * 1967-06-16 1969-12-04 Und Eisengiesserei A Beien Mas Steuereinrichtung an einer hydrostatischen Axialkolbenmaschine
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US2241701A (en) * 1937-05-26 1941-05-13 Waterbury Tool Co Power transmission
DE1528471A1 (de) * 1962-01-26 1970-01-29 Lely Nv C Van Der Schiefscheiben-Axialkolbenmaschine
GB1026343A (en) * 1962-02-19 1966-04-20 Lucas Industries Ltd Hydraulic pumps and motors
US3495542A (en) * 1967-07-13 1970-02-17 Linde Ag Pressure axial-piston machine with rotating drum under axial force generated by fluid
US3487788A (en) * 1969-02-25 1970-01-06 Jean Thoma Hydraulic unit
FR2124739A5 (fr) * 1971-01-12 1972-09-22 Bosch
GB2134188A (en) * 1983-01-27 1984-08-08 Linde Ag An adjustable axial piston machine of the inclined swash plate type
EP0175206A1 (fr) * 1984-09-05 1986-03-26 Hitachi, Ltd. Machine à fluide
JPS61144423A (ja) * 1984-12-15 1986-07-02 Mitsubishi Heavy Ind Ltd スパイラルグル−ブスラスト軸受
US4624175A (en) * 1985-08-28 1986-11-25 Wahlmark Gunnar A Quiet hydraulic apparatus
EP0241898A2 (fr) * 1986-04-15 1987-10-21 The Oilgear Company Lubrification du plateau oscillant pour dispositif de déplacement de fluide à pistons axiaux
US4903577A (en) * 1987-07-22 1990-02-27 Linde Aktiengesellschaft Adjustable axial piston machine with a swash plate design
DE4125391A1 (de) * 1990-08-01 1992-02-06 Toyoda Automatic Loom Works Axialkolbenpumpe mit einer festen steuerscheibe fuer die hin- und herbewegung von kolben

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Title
PATENT ABSTRACTS OF JAPAN vol. 10, no. 342 (M-536) (2398) 19 November 1986 & JP-A-61 144 423 (MITSUBISHI) 2 July 1986 *

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006023923A1 (fr) * 2004-08-20 2006-03-02 R. Sanderson Management, Inc. Dispositif hydraulique
WO2006130837A2 (fr) * 2005-06-02 2006-12-07 Kmt Waterjet Systems, Inc. Pompe rotative haute pression
WO2006130837A3 (fr) * 2005-06-02 2007-02-01 Kmt Waterjet Systems Inc Pompe rotative haute pression
DE102005030485A1 (de) * 2005-06-28 2007-01-04 Framatome Anp Gmbh Pumpenvorrichtung für kerntechnische Anlagen
EP1780410A1 (fr) * 2005-10-26 2007-05-02 Poclain Hydraulics Machine hydraulique à déplacement variable avec plateau en biais
US7591215B2 (en) 2005-10-26 2009-09-22 Poclain Hydraulics Variable displacement hydraulic machine having a swash plate
WO2008017557A1 (fr) * 2006-08-11 2008-02-14 Robert Bosch Gmbh Machine à pistons axiaux
US8276503B2 (en) 2006-08-11 2012-10-02 Robert Bosch Gmbh Axial piston machine
WO2014029588A1 (fr) * 2012-08-21 2014-02-27 Robert Bosch Gmbh Machine hydrostatique à piston axial à plateau oblique ou patin oscillant réglable, et patin oscillant
WO2014187547A1 (fr) * 2013-05-22 2014-11-27 Hydac Drive Center Gmbh Pompe hydraulique et piston pour une pompe hydraulique de ce type
AU2014270773B2 (en) * 2013-05-22 2017-12-21 Hydac Drive Center Gmbh Hydraulic pump and piston for such a hydraulic pump
US9849482B2 (en) 2013-05-22 2017-12-26 Hydac Drive Center Gmbh Hydraulic pump and piston for such a hydraulic pump
WO2015058896A1 (fr) * 2013-10-24 2015-04-30 Robert Bosch Gmbh Machine à pistons axiaux
DE102013221623A1 (de) 2013-10-24 2015-04-30 Robert Bosch Gmbh Axialkolbenmaschine
CN105683561A (zh) * 2013-10-24 2016-06-15 罗伯特·博世有限公司 轴向活塞机
CN105683561B (zh) * 2013-10-24 2018-09-21 罗伯特·博世有限公司 轴向活塞机
KR20230017955A (ko) * 2021-07-28 2023-02-07 주식회사 모트롤 씨일 커버 및 이를 포함하는 구동장치

Also Published As

Publication number Publication date
GB9301163D0 (en) 1993-03-10
EP0608144A3 (fr) 1994-12-21
GB2274491A (en) 1994-07-27
DE69403819D1 (de) 1997-07-24
GB2274491B (en) 1996-09-04
EP0608144B1 (fr) 1997-06-18

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