US3834281A - Control system for axial-piston machines and the like - Google Patents

Control system for axial-piston machines and the like Download PDF

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Publication number
US3834281A
US3834281A US00325889A US32588973A US3834281A US 3834281 A US3834281 A US 3834281A US 00325889 A US00325889 A US 00325889A US 32588973 A US32588973 A US 32588973A US 3834281 A US3834281 A US 3834281A
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United States
Prior art keywords
piston
axis
bore
working piston
cylindrical
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US00325889A
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English (en)
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W Heyl
K Bergmann
H Kern
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Linde GmbH
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Linde GmbH
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    • 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
    • F04B1/122—Details or component parts, e.g. valves, sealings or lubrication means
    • 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
    • F04B1/26—Control
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash plate

Definitions

  • the present invention relates to a motion-transfer mechanism and more particularly to a mechanism for BACKGROUND OF THE INVENTION
  • the term axial-piston machine is used generally in the art of fluid mechanics to indicate broadly a hydraulic pump or hydraulic motor having a plurality of pistons parallel to an axis of rotation of a cylinder block or drum and angularly equispaced therearound, the drum being rotated by an applied force in the case of a pump or driving a shaft in the case of a motor.
  • an axial-piston machine can operate either as a pump or as a motor, depending upon whether an external force is applied to the shaft or the shaft is to be driven by the supply of fluid from an external source.
  • the expression axial-piston machine is intended to identify machines of the general configuration described below and which can either be a pump or a motor or which can operate both as a pump or as a motor.
  • Axial-piston machines of this general type comprise a fluid-distribution surface, generally lying in a plane perpendicular to the axis of the drum or cylinder block and provided directly, or thorugh the intermediary of a valve or distribution plate, with arcuate or kidneyshaped fluid distribution ports.
  • the cylinder drum, barrel or block may be rotable with a shaft extending perpendicular to this surface and can be urged against the surface while being provided with a plurality of bores extending axially within the cylinder drum and angularly equispaced therearound, the cylinder bores communicating by axially extending passages with the kidney-shaped ports. These passages open at a face of the drum which bears against the fluid distribution or fluid collection surface.
  • the pistons which are reciprocable within these cylinder bores, extend from the cylinder drum into engagement with an inclined plate or control plate which may lie generally transverse to the axis of the drum at an angle other than 90 therewith so that, with rotation of the drum, pistons in the region of closest approach of the plate to the drum are urged inwardly and pistons as they approach the region of greatest distance from the drum move outwardly, thereby alternately contracting and expanding the chambers within each of the cylinders.
  • fluid is forced under pressure from the cylinder bores as the compartments contract and is drawn into the cylinder bores as the compartments expand.
  • fluid under pressure is forced into a contracted compartment of a machine operated as a motor, the piston is driven outwardly and the system rotates to expand the compartments.
  • an axial-piston pump may be connected to the inlet of an axial-piston motor while the outlet of the motor is connected to the input of the pump, thereby creating a relatively close fluidtransmitting system between the two.
  • the motor operates.
  • Axial-piston machines of the type with which the invention is concerned are generally of the variable-displacement type, the displacement being a function of the angle at which the control plate intersects the drum axis. By varying this angle it is possible to reduce the displacement to zero, increase the displacement or reverse the direction to flow substantially continuously and thus a transmission of this type is generally a continuously variable torquetransmission system.
  • Variation of the output of the machine can be accomplished by pivoting the control plate or disk or by pivoting the barrel or cylinder drum about a swing axis perpendicular to but coplanar with the drum axis and the shaft axis. In a position of the control plate in which it is perpendicular to the drum axis and to the shaft axis, there is zero displacement.
  • An axial-piston hydraulic machine of this type is disclosed in the com-' monly owned US. Pat. No. 3,678,804.
  • Another object of the invention is to provide an improved controlled system for an axial-piston machine whereby the disadvantages of the earlier systems set forth above can be eliminated.
  • this guide body is provided with a cylindrical guide bore transversely to the axis of the cylindrical body and intersecting same or somewhat offset therefrom.
  • the axis of the guide bore is perpendicular to the axis of the cylindrical body and receives a cylindrical pin fixed to the swinging member.
  • this pin Upon swinging movement of the latter member with axial displacement of the working piston, this pin slides axially within the guide bore and/r rotates about its axis while the cylindrical guide body rotates about its axis and forces transmit between the piston and the angularly adjustable member by surface-to-surface contact without the danger of jamming.
  • the pin When the axis of the bore in the piston (receiving the cylindrical guide body) is not parallel to the axis about which the controlled member swings (hereinafter referred to as the swinging axis), the pin will rotate in the guide body.
  • the position of the piston axis with respect to the swing axis is not of significance since the relatively movable force transmitting elements, namely, the cylindrical guide body and the cylindrical pin, can shift relatively to compensate for any relative position of the two axes.
  • the force-transmitting elements allow various orientations of the pistonand -cylinder arrangement with respect to the axis of the machine and the swing axis.
  • the axis of the pin may intersect the swing axis or may be substantially parallel thereto.
  • the guide body also may shift axially in the working piston because the axis of the pin describes a circular arc-segmental path about the swinging axis.
  • the system of the present invention permits one and the same working piston, with its associated working cylinder, to be positioned in various configurations with appropriate modification of position of the guide body. This is especially significant when the motiontransmitting mechanism is used as the control device for different axial-piston pumps.
  • the same control mechanism can be used with axial-piston pumps with adjustable control disks since the axis of the cylindrical bore is at least approximately parallel to the axis of the shaft and to the cylinder drum.
  • the pin can lie precisely in the plane of the axis of the shaft and the axis of the piston, when the latter axes are parallel, or can be offset from this plane when tis arrangement is more desirable for space considerations.
  • the axis of the pin may be swung through so that the axis of the pin lies parallel to the swing axis but the guide-body axis is swung through 90 as well.
  • the axis of the piston can thus be parallel to the axis of the motor shaft or the right angles thereto so that the axis of the piston lies in a plane to which the axis of the shaft is perpendicular.
  • This latter arrabgement has been found to be most desirable for swinging-drum axial-piston machines.
  • the bore in which the pin is threaded e.g., on a pivoting control plate, may be tilted in one way or another during manufacture, the force-transmitting assembly compensating for it.
  • FIG. 1 is an axial cross-sectional view taken generally along the line II of FIG. 2, showing an axialpiston machine provided with a motion-transmitting mechanism according to the invention;
  • FIG. 2 is a cross-sectional view taken along line II-lI of FIG. 1;
  • FIG. 3 is an enlarged perspective view of the guide body of the mechanism shown in FIG. 2;
  • FIG. 4 is a cross-sectional view through a guide body according to another embodiment of the invention.
  • FIG. 5 is a view similar to FIG. 2 of a fragment of another embodiment of the invention.
  • FIGS. 1 through 3 of the drawing we show an axial-piston machine, e.g., an axial-piston pump, which may form part of a power transmission in accordance with conventional principles discussed above.
  • an axial-piston machine e.g., an axial-piston pump
  • This pump comprises a housing 1 closed at one end by a cover plate 2 and provided with a shaft 3 journaled in self-aligning roller bearing 4 and 5.
  • the shaft 3 may be coupled at its threaded end 3a to an electric, internal combustion or other motor or engine, has a cylindrical portion 3b receiving the inner race of roller bearings 4 and a shoulder 3c abutting this inner race to form a thrust-resisting member therewith.
  • a cylindrical portion 3d receives the inner race of roller bearings 5 and a shaft has a shoulder 3e which axially abuts this inner race.
  • a central portion 3f is splined to rotatably entrain a cylindrical drum 6 in which pistons 11 are reciprocable, the pistons being angularly equispaced about the axis A of the drum.
  • Each of the pump pistons 11 is received within a cylinder bore 60 extending axially in the cylinder drum or block 6 and vented at 6b to the chamber la surrounding the cylinder drum.
  • Each piston 11 is also provided with a generally spherical head 11a which is received with two degrees of freedom in the generally spherical socket a of a shoe 10 whose surface 10b slidingly engages the annular face 9a of a swingable control disk 9.
  • a retaining ring 9b which rests upon a hub 90 of spherical outer configuration, centered upon the axis of swing B of the disk 9, retains the shoes 10 axially against the surface 9a.
  • the hub 9c is seated upon a boss 66 of the cylinder drum so that the latter is urged to the right by the spring disk 9b.
  • the shoes 10 are provided with passages 10c connecting the socket interfaces with the surface interfaces 9a, 10b to insure lubrication of the sliding parts.
  • the cylinders 6a communicate via axial passages 6d with registering passages formed in a valve plate 40 whose apertures 41 and 42 may have the kidney-shaped configuration customarily used to distribute fluid to or receive fluid from the cylindrical drum of an axial piston machine.
  • Apertures 41 and 42 communicate with passages 43 and 44 of the cover 2 and these passages terminate in ports 7 and 8 for the entry of fluid 2 and its discharge from the pump.
  • the control disk 9 (FIG. 2) has a pair of hubs 9d and 9e diametrically opposite locations along its pivot axis B and journal in roller bearings 37 and 38 of the housing.
  • a threaded boss 9f is also provided for connection to the control piston as will be apparent hereinafter. It will be evident that, when the disk 9 lies in a plane perpendicular to axis A, there is no axial displacement of the pistons 11 and rotation of the drum by a motor does not displace fluid.
  • the servomechanism comprises a cylinder housing 12 which is mounted on the top of the housing 1 and which slidably receives a working piston 13 whose axis C is here shown to lie parallel to the axis A of the cylinder drum and in the section plane of FIG. 1.
  • the piston 13 is formed with a transverse cylindrical bore 13 in which a cylindrical guide body 14 is rotatably received, this guide body having an axis D which is generally parallel to the axis B and is perpendicular to the axis C.
  • a pin 16 projects on opposite sides of the cylindrical bore 13, there are provided recesses or openings 15 in the piston 12, into which the opposite ends of a pin 16 projects.
  • the pin 16 is axially shiftable and rotatable in a bore 14a of the cylindrical guide body 14, the axis E of pin 16 lying perpendicular to the axis C (in one position as illustrated of the pin 16) and perpendicular to the axis D.
  • the axis of pin 16 is perpendicular (in the latter position) to the plane defined by the axes C and D of the working piston 13 and the cylindrical guide body 14, respectively.
  • the pin 16 is provided with a thread 17 screwed into the boss 9f of the complementarily threaded control disk 9, while the other end of the pin 16 is provided with an internal hexagonal socket 18 adapted to receive an Allen wrench.
  • the Allen wrench may be inserted in a threaded bore in cylinder 12, in
  • Cylinder 12 is closed at its right-hand end by a cylindrical housing 20 forming a seat for a pair of springs 21 of the coil compression type, the springs being seated against a plate 22.
  • the working piston 13 is provided with a threaded axially extending bore receiving a pair of counterlocking screws 24 and 25 having Allen-wrench hexagonal sockets and adapted to be rotated counter to one another to lock an adjustment of the working piston into the system.
  • the screw 25 rests against the spring seat 22 when the working piston 13 is in the position shown in FIG. 1 and the swinging control disk 9 is perpendicular to the shaft 3.
  • a spring 26 whose spring force is only about half the spring force of springs 21 bears upon the working piston 13 from the left, i.e., in the direction opposite the applied force of springs 21. Spring 26 thus biases the working piston 13 to the right so that its screw 24 rests against the spring seat 22 as long as neither the right nor the left hand effective faces of the piston 13 are under fluid pressure.
  • the piston 13 is also provided with a throughgoing axially extending control bore 27 in which a control piston 28 is longitudinally shiftable.
  • the piston 28, constituting a valve member is, in turn, selectively shiftable by a control pin 30 which extends into a lostmotion slot 28a of this valve member and is controlled by mechanical means not illustrated in the drawing, e.g., by a transmission-ratio or reversing lever.
  • the piston 13 is provided with a bore 29 communicating with an annular chamber 27a surrounding the valve portion 28b of this valve member which is also formed with an axially extending bore 28c for servo-operation of the main piston 13. Hydraulic fluid can be admitted to the cylinder 12 through a port not structurally illustrated in the drawing to supply the actuating fluid for the control piston.
  • the connecting bore or passage 31 terminates at the transverse bore 13' receiving the guide body 14 and to permit the control fluid to pass this body, it is formed with a sectoralrecess or groove 32 which communicates with bore 31 and the axial bore 27.
  • the control fluid from pilot valve 28 can flow through the recess 32 and passage 31 into the working chamber closed by plate 32.
  • a threaded plate 33 in cylinder housing can be removed, when necessary, to provide an axial aperture through which the second screws 24 and can be adjusted with Allen wrenches, thereby adjusting the position of the working piston 13 in the neutral position of the system as illustrated.
  • the control disk 9 When the working piston 13 is shifted in cylinder 12, the control disk 9 is swung about its axis B by the cylindrical pin which is rotatable and axially shiftable within the cylindrical guide body 14.
  • the pin 16 thus describes a circular arc about the common axis of the bearings 37 and 38 at its end 17 threaded into the control disk 9.
  • the pin 16 and the cylindrical guide body 14 swing about the axis D, the pin being slightly canted from its position as illustrated in FIG. 1. Should the thread 17 in the boss 9f be slightly inclined as a result of a manufacturing error, this will mean that the pin 16 will be slightly inclined to the section plane ll-II illustrated in FIG. 1 and the guide body 14 slightly rotated angularly about its axis D.
  • the com pensation may be effected by adjusting the position of the piston 13 as previously described. Should the thread 17 of the boss 9f be manufactured with a slight deviation out of the plane of the drawing in FIG. 1, a slight rotation of the piston 13 is all that is required to compensate.
  • FIG. 4 we show an arrangement in which the cylindrical guide body 14 receives the pin 116 with an offset between the axis D' of guide body 114 and E of the axis of pin 116.
  • the pin 16 can be rotated through 90 from its position as illustrated with a corresponding rotation of the guide body 14.
  • FIG. 5 This has been shown in which the cylindrical body 14 received the pin 16 which engages a lug 9f of the control disk 9.
  • a similar modification can provide an arrangement in which the swinging axis of the control disk 9 is approximately parallel to the axis of the working piston and the axis of the bore-receiving pin 16 is approximately perpendicular to the plane of the swing axis and parallel to the axis of the working piston.
  • a motion-transmitting mechanism for an axial piston machine comprising:
  • a linearly shiftable working piston formed with a first cylindrical bore
  • a cylindrical guide body rotatably received in said cylindrical bore and snugly surrounded by said piston, said body being provided with a second cylindrical bore having an axis transverse to the axis of said first cylindrical bore and said body;
  • a cylindrical pin rotatably received in said second cylindrical bore and shiftable therein while being snugly surrounded by said body, said pin having an end projecting from said body along the axis of said second cylindrical bore;
  • said axial-piston machine comprising a cylindrical drum rotatable about an axis perpendicular to said swing axis and provided with a plurality of axially reciprocable pump pistons, and a control disk acting upon ends of said pump pistons, one of said drum and said control disks constituting said controlled member, said pin threadedly engaging said control member;
  • a pilot piston controllable to feed fluid selectively to opposite sides of said working piston for driving same in opposite direction, said first bore lying between said opposite sides, said working piston being formed with a passage leading from said pilot piston to one side of said working piston, said passage communicating with said first bore, said guide body being formed with a recess at least along an arc of its circumference and communicating with said passage.
  • said axial-piston machine comprises a housing receiving said drum and said disk, said mechanism further comprising means forming a cylinder for said piston in said housing substantially parallel to the axis of said drum and laterally offset therefrom, said piston being received in said cylinder and defining at opposite ends of said piston working chambers pressurizable to shift said working piston in opposite directions, said working piston being formed with an axially extending bore communicating with a source of control fluid and a pilot piston received within said axially extending bore of said working piston from controlling fluid flow to said chambers; and a control pin extending laterally into said working piston and engaging said pilot piston for shifting the latter and thereby inducing said working piston to follow the motion of said pilot piston.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
US00325889A 1972-01-31 1973-01-22 Control system for axial-piston machines and the like Expired - Lifetime US3834281A (en)

Applications Claiming Priority (1)

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DE2204466A DE2204466A1 (de) 1972-01-31 1972-01-31 Bewegungsuebertragungsmechanik

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US (1) US3834281A (it)
JP (1) JPS4887256A (it)
DE (1) DE2204466A1 (it)
FR (1) FR2155737A5 (it)
GB (1) GB1378723A (it)
IT (1) IT978501B (it)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3933083A (en) * 1974-10-21 1976-01-20 General Signal Corporation Variable displacement cylindrical pump
US3949649A (en) * 1973-04-14 1976-04-13 Robert Bosch G.M.B.H. Adjusting apparatus for hydraulic pumps or motors
US3965682A (en) * 1973-07-20 1976-06-29 Friedrich Kocks Gmbh Hydraulic installation, more particularly for driving warping retaining winches on bulk cargo ships
US4014628A (en) * 1975-05-15 1977-03-29 Caterpillar Tractor Co. Supercharged three-section pump
US4167895A (en) * 1978-06-26 1979-09-18 The Oilgear Company Axial pump with displacement control device
US4896585A (en) * 1987-05-05 1990-01-30 Linde Aktiengesellschaft Adjustable axial piston machine
US5046401A (en) * 1989-08-10 1991-09-10 Sanden Corporation Wobble plate compressor with a rotation prevention mechanism
EP0922858A3 (de) * 1997-12-12 2000-04-05 Brueninghaus Hydromatik Gmbh Hydrostatische Maschine mit einer drehbar gelagerten Zylindertrommel und einer einstellbaren Schwenkscheibe
US6358025B1 (en) * 1998-02-13 2002-03-19 Parker Hannifin Ab Hydraulic rotating axial piston engine
US6358018B1 (en) * 1999-02-12 2002-03-19 Parker Hannifin Ab Hydraulic rotating axial piston engine
US20030112077A1 (en) * 2001-12-17 2003-06-19 Stmicroelectronics S.A. Amplifier with a MOS output stage
US6715997B2 (en) 2001-04-30 2004-04-06 Sauer-Danfoss Inc. Housing for a rotary hydraulic unit with a servo piston
US20080155980A1 (en) * 2006-12-28 2008-07-03 Koji Sakata Hydrostatic Stepless Transmission
CN104641110A (zh) * 2012-08-17 2015-05-20 罗伯特·博世有限公司 致动器装置和轴向活塞机
CN104685155A (zh) * 2012-08-17 2015-06-03 罗伯特·博世有限公司 致动器装置和轴向活塞机
US20150337814A1 (en) * 2014-05-22 2015-11-26 Robert Bosch Gmbh Adjustment Device for a Hydrostatic Piston Machine, and Hydrostatic Axial Piston Machine
EP3211229A1 (de) * 2016-02-24 2017-08-30 Liebherr Machines Bulle SA Axialkolbenmaschine, insbesondere axialkolbenpumpe
CN114165403A (zh) * 2020-02-13 2022-03-11 罗伯特·博世有限公司 采用斜盘结构的流体静力的轴向活塞机

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4269574A (en) * 1978-04-03 1981-05-26 Bobier Wilfred S Fluid device
DE4002017A1 (de) * 1990-01-24 1991-07-25 Linde Ag Verstellbare axialkolbenmaschine in schraegscheibenbauweise
DE4020325C2 (de) * 1990-06-26 1995-01-05 Hydrokraft Gmbh Regeleinrichtung für verstellbare Hydropumpen

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US1918985A (en) * 1923-04-28 1933-07-18 Waterbury Tool Co Fluid controlled mechanism
US2265314A (en) * 1936-07-15 1941-12-09 Waterbury Tool Co Power transmission
US2303955A (en) * 1936-03-28 1942-12-01 Edwin L Rose Power transmission
US2574335A (en) * 1948-02-21 1951-11-06 Ledue Rene Fluid-pressure motor device for control systems
US2732808A (en) * 1956-01-31 Fluid pump and control
US2945449A (en) * 1954-06-03 1960-07-19 Bendix Aviat Corp Hydraulic control pump
US3620130A (en) * 1969-06-30 1971-11-16 Borg Warner Hydrostatic transmission mechanism
US3736073A (en) * 1971-12-29 1973-05-29 Lucas Industries Ltd Pump control mechanism

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Publication number Priority date Publication date Assignee Title
US2732808A (en) * 1956-01-31 Fluid pump and control
US1918985A (en) * 1923-04-28 1933-07-18 Waterbury Tool Co Fluid controlled mechanism
US2303955A (en) * 1936-03-28 1942-12-01 Edwin L Rose Power transmission
US2265314A (en) * 1936-07-15 1941-12-09 Waterbury Tool Co Power transmission
US2574335A (en) * 1948-02-21 1951-11-06 Ledue Rene Fluid-pressure motor device for control systems
US2945449A (en) * 1954-06-03 1960-07-19 Bendix Aviat Corp Hydraulic control pump
US3620130A (en) * 1969-06-30 1971-11-16 Borg Warner Hydrostatic transmission mechanism
US3736073A (en) * 1971-12-29 1973-05-29 Lucas Industries Ltd Pump control mechanism

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3949649A (en) * 1973-04-14 1976-04-13 Robert Bosch G.M.B.H. Adjusting apparatus for hydraulic pumps or motors
US3965682A (en) * 1973-07-20 1976-06-29 Friedrich Kocks Gmbh Hydraulic installation, more particularly for driving warping retaining winches on bulk cargo ships
US3933083A (en) * 1974-10-21 1976-01-20 General Signal Corporation Variable displacement cylindrical pump
US4014628A (en) * 1975-05-15 1977-03-29 Caterpillar Tractor Co. Supercharged three-section pump
US4167895A (en) * 1978-06-26 1979-09-18 The Oilgear Company Axial pump with displacement control device
US4896585A (en) * 1987-05-05 1990-01-30 Linde Aktiengesellschaft Adjustable axial piston machine
US5046401A (en) * 1989-08-10 1991-09-10 Sanden Corporation Wobble plate compressor with a rotation prevention mechanism
EP0922858A3 (de) * 1997-12-12 2000-04-05 Brueninghaus Hydromatik Gmbh Hydrostatische Maschine mit einer drehbar gelagerten Zylindertrommel und einer einstellbaren Schwenkscheibe
US6358025B1 (en) * 1998-02-13 2002-03-19 Parker Hannifin Ab Hydraulic rotating axial piston engine
US6358018B1 (en) * 1999-02-12 2002-03-19 Parker Hannifin Ab Hydraulic rotating axial piston engine
US6715997B2 (en) 2001-04-30 2004-04-06 Sauer-Danfoss Inc. Housing for a rotary hydraulic unit with a servo piston
US20030112077A1 (en) * 2001-12-17 2003-06-19 Stmicroelectronics S.A. Amplifier with a MOS output stage
US20080155980A1 (en) * 2006-12-28 2008-07-03 Koji Sakata Hydrostatic Stepless Transmission
CN104641110A (zh) * 2012-08-17 2015-05-20 罗伯特·博世有限公司 致动器装置和轴向活塞机
CN104685155A (zh) * 2012-08-17 2015-06-03 罗伯特·博世有限公司 致动器装置和轴向活塞机
US20150337814A1 (en) * 2014-05-22 2015-11-26 Robert Bosch Gmbh Adjustment Device for a Hydrostatic Piston Machine, and Hydrostatic Axial Piston Machine
US10054112B2 (en) * 2014-05-22 2018-08-21 Robert Bosch Gmbh Adjustment device for a hydrostatic piston machine, and hydrostatic axial piston machine
EP3211229A1 (de) * 2016-02-24 2017-08-30 Liebherr Machines Bulle SA Axialkolbenmaschine, insbesondere axialkolbenpumpe
CN114165403A (zh) * 2020-02-13 2022-03-11 罗伯特·博世有限公司 采用斜盘结构的流体静力的轴向活塞机
US11598322B2 (en) * 2020-02-13 2023-03-07 Robert Bosch Gmbh Hydrostatic axial piston machine of swash plate construction
CN114165403B (zh) * 2020-02-13 2026-04-17 罗伯特·博世有限公司 采用斜盘结构的流体静力的轴向活塞机

Also Published As

Publication number Publication date
JPS4887256A (it) 1973-11-16
FR2155737A5 (it) 1973-05-18
GB1378723A (en) 1974-12-27
DE2204466A1 (de) 1973-08-09
IT978501B (it) 1974-09-20

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