EP0162238B1 - Machine à pistons axiaux, en particulier pompe du type à plateau incliné - Google Patents

Machine à pistons axiaux, en particulier pompe du type à plateau incliné Download PDF

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Publication number
EP0162238B1
EP0162238B1 EP85103801A EP85103801A EP0162238B1 EP 0162238 B1 EP0162238 B1 EP 0162238B1 EP 85103801 A EP85103801 A EP 85103801A EP 85103801 A EP85103801 A EP 85103801A EP 0162238 B1 EP0162238 B1 EP 0162238B1
Authority
EP
European Patent Office
Prior art keywords
control surface
cylinder
loading
axial piston
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.)
Expired
Application number
EP85103801A
Other languages
German (de)
English (en)
Other versions
EP0162238A1 (fr
Inventor
Ludwig Wagenseil
Manfred Lotter
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.)
Hydromatik GmbH
Original Assignee
Hydromatik GmbH
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 Hydromatik GmbH filed Critical Hydromatik GmbH
Publication of EP0162238A1 publication Critical patent/EP0162238A1/fr
Application granted granted Critical
Publication of EP0162238B1 publication Critical patent/EP0162238B1/fr
Expired 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
    • F04B1/2007—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
    • F04B1/2042—Valves
    • 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
    • F04B1/2064—Housings
    • F04B1/2071—Bearings for cylinder barrels

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • GB-A-311 938 An axial piston machine of the type described at the outset is described and shown in GB-A-311 938.
  • the cylinder rests with a flat end face on a flat control surface, the piston bores opening on the end face without narrowing in cross section.
  • load cylinders are arranged on the circumference of the cylinder, which are connected to the piston bores and can thus be acted upon by the working pressure and act on the cylinder against the control surface.
  • the cylinder is mounted on the drive shaft of a swash plate axial piston machine in the sense of a so-called kinematic guide.
  • each loading cylinder is connected by a connecting channel to a piston bore located in its vicinity.
  • the cylinder is supported by a roller bearing, which prevents an automatic gap adjustment.
  • the invention has for its object to design an axial piston machine of the type mentioned in such a way that axially and radially balanced guidance of the cylinder is possible with maximum utilization of the piston powers.
  • a spherical control surface leads to a radial force component, but the radial force component is harmless in the embodiment according to the invention because it acts in a transverse plane of the axial piston machine, in which the cylinder is supported radially and thus cannot exert a tilting moment on the cylinder.
  • the cylinder is freed of significant damaging forces both axially and radially. This leads to an optimal contact of the cylinder on the spherical control surface, whereby an effective oil film can form between the control surface and the cylinder due to the balance of the control surface force and the load force, whereby friction and wear are minimized.
  • both the loading force and the control surface force can consist of several partial forces, e.g. B. the frictional forces acting in the displacement of the pistons in both axial directions also influence both the control surface force and the loading force.
  • the cylinder by a central spring force, for. B. in the form of a compression spring, constantly applied against the pressure surface, as is the case with the prior art according to DE-OS 22 50 510.
  • the partial force generated by the spring is part of the loading force.
  • the embodiment according to claim 2 is advantageous for two reasons. On the one hand, due to the piston path tapering conically to the control surface, there is a smaller radius for the control openings in the control surface. As a result, due to a relatively small pressure field and the shorter lever arm, the partial forces of the control surface force caused are lower, which enables smaller loading cylinders. On the other hand, space is gained for the loading cylinders due to this configuration.
  • a load cylinder is assigned to each piston, wherein there is a line connection between the associated piston bores and load cylinders.
  • the embodiment according to claim 7 leads to an adaptation of the balancing force generated by the loading cylinder to the actual pressure profile in the piston chambers, which is due to structural and natural law conditions relative to the cylinder in the circumferential direction, so to speak, out of phase.
  • the axial piston machine which can be operated as a pump and as a motor, consists of a housing generally designated 2, a drive shaft 4, which is rotatably mounted therein about an axis of rotation 3, a so-called swash plate 5, on which by means of sliding shoes 6 and a pressure plate 7, pistons 8 are held distributed on a pitch circle, a cylinder 9 rotatable by the drive shaft 4 about the axis of rotation 3, in which the pistons 8 are displaceably guided in axially extending piston bores 11 and a control plate 12 immovably attached to the housing 2 , whose spherically convexly curved control surface 13 has kidney-shaped control openings 14 which, during the rotation of the cylinder 9, come into or out of overlap with the piston bores 11 and thus control the pumping operation or motor operation of the axial piston machine 1 in the sense of valves.
  • the pistons 8 are driven by the swash plate 5, on which the pistons 8 are only held axially. That is, while the cylinder 9 is rotating, the sliding shoes 6 slide circumferentially on the swash plate 5, whereby the axial movement of the pistons 8 is generated.
  • the end face of the cylinder 9 facing the control surface 13 is spherically concave in accordance with the curvature of the control surface 13 and lies sealingly against the control surface 13.
  • the cylinder 9 has a bore 15 in which it is penetrated by the drive shaft 4 with play, which is supported in the region of its ends by means of roller bearings 16 and 17.
  • the cylinder 9 is supported only on its end facing away from the control surface 13 by a radially effective support bearing 18 on the drive shaft 4.
  • a rotary driving connection 19 in the form of a keyway connection which is effective in the circumferential direction.
  • the cylinder 9 is biased by one or more compression springs 21 against the control surface 13, which act against the end face of the cylinder 9 facing away from the control surface 13 and are supported on a spherical bearing part 22 which, on the one hand, engages around the cylinder 9 with a cylindrical bore and on whose outer spherical surface slidably slides the pressure plate 7.
  • the support bearing 18 is arranged in the area of a plane denoted by A, which is also the central swivel plane of the swash plate 5.
  • a control surface force which acts perpendicular to the control surface 13 and attempts to lift the cylinder 9 from the control surface 13 acts on the cylinder 9, and an axially directed, resulting load force, generally designated F ER , which Cylinder 9 acted against the control surface 13.
  • the control surface force F s results essentially as the sum of the partial pressures over the entire pressure field and possible gap pressures which are able to build up between the control surface 13 and the end face 23 of the cylinder 9 sliding thereon and which attempt to lift the cylinder 9 off the control surface 13 .
  • several partial forces have an influence, e.g. B.
  • the resulting loading force F ER likewise comprises several partial forces and in particular a loading force F E with which loading cylinders 24 distributed over the circumference act on the cylinder 9 in the direction of the control surface 13.
  • the resulting loading force F ER also generally includes piston forces denoted by F K , which, as in the explanation of the control surface force Fs, will not be discussed further.
  • the force, not specified, generated by the compression springs 21 also influences the resulting loading force F ER .
  • the pistons of the loading cylinder 24 are designated 25 and the associated work spaces 26.
  • a load cylinder 24 is assigned to each piston 8, the piston bores 11 being connected to the associated working spaces 26 of the load cylinders 24 by radial channels 27.
  • the loading pistons 25 are supported on the housing 2 by means of a slide ring 28. They are pierced at 31 for the purpose of automatic lubrication of the sliding surface 29. While the slide ring 28 is fixedly attached to the housing 2, the loading pistons 25 take part in the rotary movement of the cylinder 9.
  • the cylinder 9 has a flange 32 for receiving the loading cylinders 24.
  • Both the control surface force F s and the loading force F E generated by the loading cylinders 24 are pulsating forces. This results from the pressure build-up or drop in the piston bores 11.
  • control surface force F s Since the control surface force F s is not directed parallel to the axis of rotation 3, its control surface force component F SK directed parallel to the axis of rotation 3 is lower.
  • the forces acting in opposite directions on the cylinder 9 are in equilibrium. If one takes into account that the control surface force component F SK has a smaller distance a from the axis of rotation 3 than the resulting load force F ER , the distance of which from the axis of rotation 3 is denoted by b, then the result is a relatively smaller size in comparison with the control surface force component F SK Load force F ER to create a balance of forces. In order to achieve this balance of forces, the working surfaces (diameter d) of the loading cylinder 24 are designed accordingly.
  • a radially directed force component F R results which radially loads the cylinder 9.
  • the radius R of the control surface 13 is dimensioned so large that the lines of force of the control surface force F s and the resulting loading force F ER intersect at a point S which lies on the transverse plane A in which the cylinder 9 is supported radially. Due to this configuration, the radial force component F R is unable to exert a tilting moment on the cylinder 9.
  • the embodiment of the second exemplary embodiment according to FIG. 2 differs from the first exemplary embodiment only in that the axes of the pistons 8 converge in the direction of the control surface 13. As a result, the pistons 8 are rotated on a path which tapers conically towards the control surface 13. In such an embodiment, the size of the pressure field is compared to the first embodiment
  • the loading force F ER is directed somewhat obliquely in contrast to the first embodiment.
  • the same force relationships as in the first exemplary embodiment result in the second exemplary embodiment.
  • the third exemplary embodiment according to FIG. 3 differs from the second exemplary embodiment essentially in that no compression springs are provided which act on the cylinder 9 in the direction of the control surface 13 and which are designated 21 in FIG. 1. Instead, corresponding springs 21 are provided in the load cylinders, where they both cause the pistons 24 to lift up in the unpressurized state and also cause the cylinder 9 to effectively rest against the spherical control surface. A certain investment power is not harmful if it is low.
  • FIG. 4 and 5 show a cross-section rotated by 90 ° alternately through the axial piston machine according to FIG. 1 along the line IV-IV or in the plane of the connecting channels 27. It should be taken into account that FIG. 5 is a relative to the Fig. 4 shows a modified embodiment as a fourth embodiment.
  • the control surface 13 is indicated by dashed lines.
  • the kidney shape of the control openings 14, also shown with dashed lines, is clearly recognizable.
  • the fourth exemplary embodiment according to FIG. 5 differs from the first exemplary embodiment according to FIG. 4 in that the pressure field 33 of the control surface 13 indicated with cross hatching is rotated by a certain angle w against the dead center axis 34.
  • the loading cylinders 24 are prematurely rotated in the same circumferential direction (see direction of rotation 35) by an angle w 1 .
  • the loading force F E also has a leading effect in adaptation to the pressure build-up or reduction in the piston chambers 11.

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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)
  • Hydraulic Motors (AREA)

Claims (7)

1. Machine à pistons axiaux (1) du type à plateau incliné, en particulier, pompe à pistons axiaux,
- avec un barillet ou cylindre (9) rotatif autour d'un axe de rotation, dans lequel plusieurs pistons (8) répartis sur un cercle divisé sont guidés, et par plateau incliné (5), de manière coulissante dans des alésages à pistons (11) s'étendant à peu près le long de l'axe de rotation (3),
- les alésages à pistons (11) débouchant dans la face frontale (23) du barillet (9) opposée au plateau incliné (5),
- la face frontale (23) reposant contre une surface de distribution (13) dans laquelle sont ménagées des ouvertures de distribution (14) postionnées sur le cercle de répartition des pistons, ces ouvertures venant à être, dans des positions déterminées de la rotation du barillet (9), recouvertes par les embouchures des alésages à pistons (11),
- dans laquelle les alésages à pistons (11) débouchent sans rétrécissement de section dans la face frontale (23),
- et où des cylindres de charge ou de compensation (24) sont répartis périphériquement qui, lors du fonctionnement de la machine à pistons axiaux (1), sollicitent le barillet (9) contre la surface de distribution (13) pour compenser l'apparition d'une force (FgK) de la surface de distribution tendant à soulever le barillet (9) en l'écartant de la surface de distribution (13), les chambres de travail de ces cylindres (24) étant respectivement reliées chacune à un alésage à piston (11) par un canal de jonction (27),
- et dans laquelle le barillet (9) est soutenu radialement contre l'arbre par un palier d'appui (18),
caractérisée en ce que :
- la face frontale (23) présente une courbure sphérique concave et la surface de distribution (13) présente une courbure sphérique convexe concordante,
- le rayon (R) de la surface de distribution (13) a une grandeur telle que le point de rencontre (S) de la force (Fs) de la surface de distribution dirigée perpendiculairement à la surface de distribution (13) et de la force de compensation (FER) se trouve dans un plan (A) perpendiculaire à l'axe de rotation (3), ce plan étant dans la région du palier d'appui (18) du barillet (9), et en ce que
- ledit plan (A) et le plan médian (B) d'oscillation du plateau incliné se recoupent sur l'axe de rotation (3).
2. Machine à pistons axiaux selon la revendication 1, caractérisée en ce que les axes des pistons (8) et des alésages (11) contenant ces pistons convergent en cône en direction de la surface de distribution (13).
3. Machine à pistons axiaux selon la revendication 1 ou 2, caractérisée en ce que, dans au moins quelques uns des cylindres de compensation (24) sont disposés des ressorts (21) répartis uniformément sur la périphérie, et qui sollicitent le barillet (9) en direction de la surface de distribution (13).
4. Machine à pistons axiaux selon une des revendications 1 à 3, caractérisée en ce que les pistons de charge (25) des cylindres de compensation (24) sont en appui contre le carter (2) par l'intermédiaire d'une glissière annulaire (28).
5. Machine à pistons axiaux selon la revendication 4, caractérisée en ce que les pistons de charge (25) sont perforés axialement de part en part.
6. Machine à pistons axiaux selon une des revendications 1 à 5, caractérisée en ce qu'un cylindre de compensation (24) est associé à chaque piston (8).
7. Machine à pistons axiaux selon une des revendications 1 à 6, caractérisée en ce que les cylindres de compensation (24) sont décalés d'un angle (W,) dans le sens de rotation (35) par rapport aux pistons (8) et aux alésages à pistons (11).
EP85103801A 1984-04-06 1985-03-29 Machine à pistons axiaux, en particulier pompe du type à plateau incliné Expired EP0162238B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3413059 1984-04-06
DE3413059A DE3413059C1 (de) 1984-04-06 1984-04-06 Axialkolbenmaschine,insbesondere -pumpe der Schraegscheiben- oder Schraegachsenbauart

Publications (2)

Publication Number Publication Date
EP0162238A1 EP0162238A1 (fr) 1985-11-27
EP0162238B1 true EP0162238B1 (fr) 1988-11-02

Family

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Family Applications (1)

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EP85103801A Expired EP0162238B1 (fr) 1984-04-06 1985-03-29 Machine à pistons axiaux, en particulier pompe du type à plateau incliné

Country Status (4)

Country Link
US (1) US4602554A (fr)
EP (1) EP0162238B1 (fr)
JP (1) JPS60230570A (fr)
DE (2) DE3413059C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19706263C1 (de) * 1997-02-18 1998-07-23 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit drehzahlabhängiger Anpressung der Zylindertrommel

Families Citing this family (29)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4771676A (en) * 1986-05-19 1988-09-20 Toshiba Kikai Kabushiki Kaisha Hydraulic transmission device
JPS6351172U (fr) * 1986-09-19 1988-04-06
US5033358A (en) * 1988-01-04 1991-07-23 Hans Molly Axial piston type motor
JPH0733820B2 (ja) * 1988-09-12 1995-04-12 川崎重工業株式会社 斜板式ピストンポンプモータ
DE4035748A1 (de) * 1989-11-09 1991-05-16 Vickers Systems Gmbh Axialkolbenpumpe fuer hohe drehzahlen
DE4237506C2 (de) * 1992-11-06 1995-04-06 Danfoss As Axialkolbenmaschine
US5490444A (en) 1994-10-03 1996-02-13 Dynex/Rivett, Inc. Piston pump with improved hold-down mechanism
US5647266A (en) 1994-10-03 1997-07-15 Dynex/Rivett, Inc. Hold-down mechanism for hydraulic pump
US7874914B2 (en) 1996-12-30 2011-01-25 Igt System and method for communicating game session information
DE19838897C2 (de) * 1998-08-27 2002-12-05 Lutz Mueller Axialkolbenmaschine
US7011469B2 (en) * 2001-02-07 2006-03-14 R. Sanderson Management, Inc. Piston joint
US7331271B2 (en) * 2001-02-08 2008-02-19 R. Sanderson Management, Inc. Variable stroke/clearance mechanism
DE10251552C5 (de) * 2002-11-05 2010-07-15 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine und Steuerplatte für eine Axialkolbenmaschine
CN1328511C (zh) * 2004-07-17 2007-07-25 兰州理工大学 水介质用轴向柱塞泵
US20060120882A1 (en) * 2004-08-20 2006-06-08 Glenn Jordan Motor or pump assemblies
DE102005021029A1 (de) * 2005-05-06 2006-11-09 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise mit Lagerung des Zylinderblocks auf einem Tragzapfen
DE102007006868A1 (de) 2007-02-12 2008-08-14 Robert Bosch Gmbh Axialkolbenmaschine
DE102009039829A1 (de) 2009-09-02 2011-03-03 Linde Material Handling Gmbh Hydrostatische Axialkolbenpumpe, insbesondere Schrägscheibenpumpe
DE102012222593A1 (de) 2012-12-10 2014-06-12 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise
US9856851B2 (en) * 2013-03-29 2018-01-02 Kyb Corporation Opposed swash plate type fluid pressure rotating machine
DE102013208454A1 (de) 2013-05-08 2014-11-13 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine mit einer Zylindertrommel mit schräg zu deren Axialrichtung gelagerten Arbeitskolben und einem ebenen Steuerspiegel
CA2913062C (fr) * 2013-05-22 2020-06-02 Hydac Drive Center Gmbh Pompe a pistons axiaux de type a plateau inclinable
CN103967802B (zh) * 2014-05-06 2016-06-29 华中科技大学 一种内部集成前置泵的柱塞式液压电机泵
DE102014212208A1 (de) * 2014-06-25 2015-12-31 Robert Bosch Gmbh Schrägscheibenmaschine
FR3026793B1 (fr) * 2014-10-02 2019-07-12 PSA Automobiles Machine hydraulique comprenant des bossages de fixation allonges pour reduire le bruit
JP6612610B2 (ja) 2015-12-17 2019-11-27 ナブテスコ株式会社 流体圧ポンプおよび流体圧システム
CN105736274B (zh) * 2016-02-24 2017-07-14 湖北仁创科技有限公司 一种带限压溢流装置的水液压轴向柱塞泵
DE102018205446A1 (de) * 2018-04-11 2019-10-17 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine
CN114001005B (zh) * 2021-11-02 2023-06-23 河南科技大学 一种液压柱塞泵

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB311938A (en) * 1928-05-15 1929-05-23 John Robson Improvements in or connected with hydraulic pumps, motors, hydraulic transmission gears and the like
DE910239C (de) * 1939-11-05 1954-04-29 Hans Thoma Dr Ing Hydraulisches Getriebe mit rotierender Zylindertrommel
CH257509A (de) * 1944-10-30 1948-10-15 Von Roll Ag Axialkolbengetriebe mit gewölbtem, die Steuerschlitze aufweisendem Auflagekörper für die rotierende Zylindertrommel.
DE941343C (de) * 1953-03-25 1956-04-05 Ingrid Moser Steuerung fuer Fluessigkeitspumpen und -getriebe
US3075472A (en) * 1957-03-08 1963-01-29 Air Equipement Variable-flow pumps of the drum piston type
US3046906A (en) * 1957-05-31 1962-07-31 New York Air Brake Co Means for counteracting centrifugal force moments in rotary cylinder barrel engines
DE1200135B (de) * 1959-12-12 1965-09-02 Bosch Gmbh Robert Axialkolbenpumpe mit gekruemmtem Steuerspiegel
FR1469527A (fr) * 1965-12-03 1967-02-17 Messier Fa Pompe ou moteur hydraulique à barillet tournant
FR1487397A (fr) * 1966-05-23 1967-07-07 Citroen Sa Andre Groupe pour transmission hydrostatique de puissance mécanique
US3657970A (en) * 1969-06-09 1972-04-25 Toyoda Chuo Kenkyusho Kk Hydraulic pump or motor having a rotary cylinder barrel
FR2110573A5 (fr) * 1970-10-22 1972-06-02 Citroen Sa
DE2238582A1 (de) * 1972-08-04 1974-02-21 Linde Ag Axialkolbenmaschine
DE2250510A1 (de) * 1972-10-14 1974-04-18 Bosch Gmbh Robert Axialkolbenmaschine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19706263C1 (de) * 1997-02-18 1998-07-23 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit drehzahlabhängiger Anpressung der Zylindertrommel
US6244160B1 (en) 1997-02-18 2001-06-12 Brueninghaus Hydromatik Gmbh Axial piston machine with RMP-dependent pressure acting against the cylinder drum

Also Published As

Publication number Publication date
DE3566016D1 (en) 1988-12-08
US4602554A (en) 1986-07-29
JPS60230570A (ja) 1985-11-16
EP0162238A1 (fr) 1985-11-27
DE3413059C1 (de) 1985-07-11

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