EP2050957A1 - Machine à piston axial - Google Patents

Machine à piston axial Download PDF

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Publication number
EP2050957A1
EP2050957A1 EP08014003A EP08014003A EP2050957A1 EP 2050957 A1 EP2050957 A1 EP 2050957A1 EP 08014003 A EP08014003 A EP 08014003A EP 08014003 A EP08014003 A EP 08014003A EP 2050957 A1 EP2050957 A1 EP 2050957A1
Authority
EP
European Patent Office
Prior art keywords
axial piston
piston machine
rocker arm
machine according
swash 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.)
Granted
Application number
EP08014003A
Other languages
German (de)
English (en)
Other versions
EP2050957B1 (fr
Inventor
Martin Bergmann
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.)
Linde Material Handling GmbH
Original Assignee
Linde Material Handling 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 Linde Material Handling GmbH filed Critical Linde Material Handling GmbH
Publication of EP2050957A1 publication Critical patent/EP2050957A1/fr
Application granted granted Critical
Publication of EP2050957B1 publication Critical patent/EP2050957B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F04B1/124—Pistons
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • 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
    • F04B1/124—Pistons
    • F04B1/126—Piston shoe retaining means

Definitions

  • the invention relates to an axial piston machine in swash plate construction, with a cylinder drum rotatably mounted about a rotation axis, wherein the cylinder drum is provided with cylinder bores, in each of which a piston is mounted longitudinally displaceable, and the pistons are supported by a respective sliding shoe on a swash plate, wherein the sliding shoes by means of a rotationally synchronous with the cylinder drum rotating retainer, in particular a retaining plate, are in operative connection.
  • the pistons are supported on the swashplate by means of a respective sliding shoe. Between the piston and the shoe, a sliding shoe joint is arranged.
  • a tilting moment occurs on the sliding shoes due to the centrifugal forces acting on the sliding shoe, which causes the sliding shoes to tilt off the swashplate.
  • the sliding shoes are pressed in the direction of the swash plate to prevent lifting or tilting of the sliding shoes due to the Abkippmoments.
  • the retaining device can in this case be designed as a force-locking retaining device, wherein a spring device is provided, which acts on the retaining device and thus the sliding shoes in the direction of the swash plate.
  • a spring device which acts on the retaining device and thus the sliding shoes in the direction of the swash plate.
  • the spring force of the spring device is to be interpreted to the maximum speed.
  • this results in high spring forces, which cause high contact forces of the sliding shoes on the swash plate and the cylinder drum on the control surface at low speeds.
  • the high contact forces lead to increased wear of the swash plate machine.
  • the retaining device can furthermore be designed as a form-fitting retaining device, which is fastened to the housing in the axial direction. Due to the play existing in the form-locking connection of the retaining device with the housing, the sliding shoes can tilt due to the centrifugal force occurring during operation of the swash plate, whereby a leakage current is produced, which leads to a deteriorated efficiency of the swash plate machine.
  • a generic, designed as a beveled disc axial piston machine is from the DE 10 2005 047 981 A1 known.
  • the present invention has for its object to provide a hydrostatic axial piston machine of the type mentioned available, which is improved in terms of efficiency.
  • the sliding blocks are operatively connected to a torque generating means by means of which a Abkippmoment counteracting counter-torque is generated on the sliding shoes.
  • the idea according to the invention thus consists of generating on the sliding shoes by means of the torque generating device a counteracting torque which counteracts the tilting moment generated by the centrifugal forces and which partially or completely compensates for the tilting moment.
  • the spring force and thus the contact force can be reduced in the case of a non-positive restraint device acted upon by a spring device, resulting in lower frictional forces and thus an improved efficiency of the swashplate machine.
  • the wear of the swash plate machine is reduced by the reduced contact force.
  • tilting of the sliding shoes is reliably avoided by the torque generating device, as a result of which a swash plate machine according to the invention has low leakage and thus high efficiency.
  • the torque generating device is formed by rocker arms, wherein each sliding block is associated with a rocker arm, by means of which a contact force acting on the sliding shoe can be generated, which is directed opposite to the centrifugal force acting on the sliding block.
  • rocker arms can be generated in a simple manner acting on the sliding shoes and the centrifugal force counteracting contact force and thus on the sliding blocks a the centrifugal force caused by the tilting moment counteracting counter-torque.
  • the rocker arm can in this case according to a preferred embodiment of the invention in the region of a Gleitschuhhalses of the shoe with the peripheral surface of the shoe in operative connection can be brought.
  • rocker arm according to a further embodiment of the invention in the region of a Gleitschuhplatte of the shoe is engageable with the peripheral surface of the shoe in operative connection.
  • the rocker arm is designed as a two-armed lever, wherein a contact surface which can be brought into contact with the sliding shoe is formed on a region of the rocker arm provided with a first lever arm and engages the center of mass of the rocker arm on a second lever arm.
  • the rocker arm is thus actuated by the centrifugal force, whereby the contact force is proportional to the force acting on the rocker arm centrifugal force and thus proportional to the speed of the swash plate machine.
  • the mass of the rocker arm and the first lever arm and the second lever arm are designed such that the counter-torque generated by the rocker arm compensates almost or completely the tilting moment acting on the shoe.
  • rocker arm partially wraps around the sliding block and the area of the rocker arm provided with the second lever arm at least partially fills the space between two adjacent sliding blocks, a corresponding rocker arm mass can be made available without additional space requirement for the rocker arms.
  • the rocker arms can be arranged between the retaining device and the swash plate according to a preferred embodiment of the invention.
  • a bearing component in particular a cylindrical pin, is provided for supporting the rocker arm on the retaining device.
  • the rocker arms can be mounted pivotably on the retaining device in a simple manner.
  • the torque generating device formed from the rocker arms can be used in a swash plate machine with a non-positive restraint device, which is acted upon by means of a spring device in the direction of the swash plate.
  • the torque generating device formed from the rocker arms can be used in a swash plate machine with a positive retaining device, wherein the retaining device is supported on a housing of the axial piston machine.
  • FIG. 1 is a trained as a swash plate machine 1 hydrostatic axial piston machine of the prior art shown in a longitudinal section.
  • the swash plate machine 1 has a cylinder drum 3 rotatably mounted about an axis of rotation 2, which is provided with a plurality of concentrically arranged cylinder bores 4, in each of which a piston 5 is mounted longitudinally displaceable.
  • the cylinder drum 3 is in this case with a concentric with the axis of rotation 2 arranged drive shaft 6 in a rotationally fixed connection.
  • the pistons 5 are supported on a swash plate 8 by means of a respective sliding element 7 designed as a sliding element.
  • the shoe 7 is in this case connected to the piston 5 by means of a spherical Gleitschuhgelenks 9 hinged.
  • the swash plate 8 can hereby as in the FIG. 1 shown formed on a housing 10 of the swash plate machine 1, wherein the swash plate machine 1 has a fixed displacement volume.
  • Swash plate 8 adjustably form, whereby the swash plate machine 1 has a variable displacement volume.
  • the cylinder drum 3 is supported in the axial direction on a housing-fixed control surface 11, which is formed on a disc-shaped control base 12.
  • the control floor 12 is provided with kidney-shaped control slots (not shown), which form an inlet connection and an outlet connection of the swash plate machine 1.
  • the sliding blocks 7 are in operative connection with a retaining device 16 in the form of a disc-shaped retaining plate 15.
  • the retainer 16 is designed as a non-positive retention device.
  • the retaining plate 15 is in this case mounted on a spherical bearing component 17, which is supported on the cylinder barrel 3 by means of a spring device 18 formed by a spring or several springs.
  • the spring device 18 By means of the spring device 18 in this case the sliding blocks 7 are acted upon by the bearing member 17 and the retaining plate 15 in the direction of the swash plate 8.
  • FIG. 2 In the FIG. 2 is a shoe 7 of the FIG. 1 shown in an enlarged view, wherein the forces occurring during operation of the swash plate machine 1 are illustrated.
  • the tilting of the shoe 7 from the swash plate 8 is prevented by acting between the swash plate 8 and the shoe 7 and the shoe 7 and the retaining plate 15 forces F A and F B , by the diameter d of a circular Gleitschuhplatte 7 a, by means of the sliding shoe 7 is supported on the swash plate 8, are spaced and produce a moment counteracting the Abkippmoment.
  • the pressing force F A must in this case be applied by the spring plate 18 acting on the retaining plate 15.
  • the spring force of the spring device 18 must be designed for the high centrifugal forces F f occurring at maximum speed. At lower speeds, these high and unnecessary pressing forces F A lead to increased friction losses and thus a reduced efficiency of the swashplate machine 1 and to an increased wear of the swashplate machine 1.
  • FIG. 3 Here is a swash plate machine of the prior art with a positive retention device 15 in a representation according to the FIG. 2 shown.
  • the disc-shaped retaining plate 15 is in this case fastened by means of a fastening device 19, for example, formed by a Seegering arranged in a groove-shaped recess 20 of the housing 10 on the housing 10 in the axial direction.
  • the tilting moment of the sliding shoe 7 caused by the centrifugal force F f in turn counteracts the moment formed by the forces F A and F B. Due to the existing manufacturing tolerances and installation reasons game of fastener 19 but the slide 7 tilts from the swash plate 8, whereby a gap 21 between the Gleitschuhplatte 7a of the shoe 7 and the swash plate 8 is formed, through which a leakage current occurs in the housing interior, the results in a deteriorated efficiency of the swash plate machine.
  • the sliding blocks 7 When in the FIG. 4 illustrated swash plate machine according to the invention are the sliding blocks 7 with a torque generating device 25 in operative connection, which generate a counteracting from the centrifugal force F f on the sliding shoes 7 counteracting counter-torque.
  • the torque generating device 25 is arranged between the swashplate 8 and the retaining device 16 formed by the retaining plate 15 in the region of the sliding shoe plates 7a.
  • the retaining device 16 according to the FIG. 4 is designed as a non-positive retaining device, which according to the FIG. 1 by means of Spring device 18 and the spherical bearing member 17 is acted upon in the direction of the swash plate 8.
  • the retainer 15 according to the FIG. 4 form as a positive retention device, which according to the FIG. 3 is secured to the housing 3 in the axial direction.
  • the torque generating device 25 is - as from FIG. 5 can be seen, which shows a plan view of the retaining plate 15 and the sliding shoes 7 - of rocker arms 26, wherein each shoe 7 is associated with a rocker arm 26.
  • FIG. 6 is a part of the FIG. 5 shown in an enlarged view.
  • the rocker arm 7 associated with a rocker arm 26 is mounted by means of a trained example as a cylindrical pin bearing member 27 about a parallel to the rotation axis D of the retaining plate 15 pivot axis 28 pivotally mounted on the outer region of the retaining plate 15.
  • the rocker arm 26 is in this case designed as a two-armed lever, wherein a contact surface 30 is formed on a first region of the rocker arm, which is in operative connection with the peripheral surface of the shoe 7 in the region of the shoe plate 7a.
  • the contact surface 30 is in this case spaced from the pivot axis 28 about a first lever arm c.
  • the second region of the rocker arm 26 opposite this region with respect to the pivot axis 28 partially wraps around the sliding shoe 7 and at least partially fills the intermediate space with the adjacent sliding shoe 7.
  • the center of gravity S M of the rocker arm 26 is arranged in the second region and is spaced from the pivot axis 28 by a second lever arm d.
  • the second lever arm d is larger than the first lever arm c formed here.
  • FIG. 7 is one of the FIG. 2 corresponding representation of the shoe 7 of a swash plate machine 1 according to the invention with the forces acting on the shoe 7 forces.
  • the contact force F k generated by the rocker arm 26 and acting on the peripheral surface of the shoe 7 in the region of the shoe plate 7 a directed inward, and thus the centrifugal force F f acting on the shoe 7.
  • the contact force F k acting on the circumferential surface of the sliding shoe 7 in the region of the sliding shoe plate 7 a has the distance b from the center of the sliding shoe joint 9, whereby a counter-torque is generated by the contact force F k with the distance b, which is the distance from the distance a and counteracts the centrifugal force F f formed Abkippmoment the shoe 7.
  • the mass of the rocker arm 26 and the lever arms c, d of the rocker arm 26 are hereby preferably designed such that the Abkippmoment formed by the centrifugal force F f and the distance a of the force formed by the contact force F k and the distance b completely or almost completely is compensated, so that the sum of the moments about the midpoint of the shoe joint 9 is zero or almost zero, resulting in low forces F A and F B or these forces F A , F B disappear.
  • swash plate machine 1 with a positive retention device 26 is prevented by the counterpoise generated by the rocker arms 26 tilting of the sliding shoes 7 due to the game in the fastening means of the retainer 16 in the housing 10 effectively, creating a Increase in the leakage oil is effectively avoided and the swash plate machine according to the invention has a high efficiency.
  • rocker arm 26 instead of the arrangement of the rocker arm 26 between the swash plate 8 and the retaining plate 15 in the region of the Gleitschuhplatten 7 a, it is also possible to arrange the rocker arm 26 on the cylindrical drum 3 side facing the retaining plate 15. The rocker arms 26 are thus in operative connection with the contact surface 30 with the sliding shoe neck 7b of the sliding shoe 7 arranged between the sliding shoe joint 9 and the sliding shoe plate 7a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Hydraulic Motors (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
EP08014003A 2007-10-15 2008-08-05 Machine à piston axial Not-in-force EP2050957B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007049393A DE102007049393A1 (de) 2007-10-15 2007-10-15 Axialkolbenmaschine

Publications (2)

Publication Number Publication Date
EP2050957A1 true EP2050957A1 (fr) 2009-04-22
EP2050957B1 EP2050957B1 (fr) 2012-06-20

Family

ID=39811882

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08014003A Not-in-force EP2050957B1 (fr) 2007-10-15 2008-08-05 Machine à piston axial

Country Status (4)

Country Link
US (1) US8037808B2 (fr)
EP (1) EP2050957B1 (fr)
JP (1) JP5311383B2 (fr)
DE (1) DE102007049393A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2418381A1 (fr) * 2010-08-12 2012-02-15 Mpp Gbr Moteur à piston axial hydraulique réglable, notamment pour des éoliennes et doté d'un entraînement principal hydrostatique et procédé de commande
CN102575666A (zh) * 2009-10-06 2012-07-11 博格华纳扭矩输出系统公司 液压泵组件
CN102926959A (zh) * 2012-11-07 2013-02-13 三一重工股份有限公司 一种斜盘式柱塞泵或马达
WO2014206713A1 (fr) * 2013-06-25 2014-12-31 Robert Bosch Gmbh Machine à plateau oscillant comme pompe à pistons axiaux et/ou moteur à pistons axiaux
EP2930360A3 (fr) * 2014-04-08 2015-11-04 Linde Hydraulics GmbH & Co. KG Machine à piston axial dans une construction à axe oblique avec patins de guidage dans le plateau d'entraînement
CN109236597A (zh) * 2018-11-08 2019-01-18 四川航天烽火伺服控制技术有限公司 一种滑靴柱塞组件及一种柱塞泵

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012218982A1 (de) 2012-10-18 2014-06-12 Robert Bosch Gmbh Axialkolbenmaschine
US9863408B2 (en) * 2015-01-16 2018-01-09 Hamilton Sundstrand Corporation Slipper retainer for hydraulic unit
US9719499B2 (en) * 2015-01-16 2017-08-01 Hamilton Sundstrand Corporation Slipper retainer ball for hydraulic unit
KR20180083356A (ko) * 2015-11-13 2018-07-20 보그워너 스웨덴 아베 독립형 후륜 차축 구동부의 윤활 제어
CN114046231A (zh) * 2021-11-05 2022-02-15 中国航发北京航科发动机控制系统科技有限公司 一种滑靴与支撑盘的摩擦结构
WO2024157174A1 (fr) * 2023-01-25 2024-08-02 Stem Numerical Engineering Srl Machine hydraulique à pistons axial améliorée

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4872394A (en) * 1984-02-29 1989-10-10 Shimadzu Corporation Bent axis type axial piston pump or motor
US20030138331A1 (en) * 2002-01-22 2003-07-24 John Fox Metering pump with proportional output
DE102005047981A1 (de) 2005-10-06 2007-04-12 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1226418B (de) * 1962-07-12 1966-10-06 Unipat A G Einrichtung zum Andruecken der winkelbeweglichen Kolbengleitschuhe an die Schiefscheibe oder Taumelscheibe einer Axialkolbenmaschine (Pumpe oder Motor)
US3807283A (en) * 1970-05-18 1974-04-30 Cessna Aircraft Co Axial piston pump or motor
DD107116A1 (de) * 1973-10-01 1974-07-12 Manfred Mueller Hydrostatische axialkolbenmaschine
DE3928942A1 (de) * 1989-08-31 1991-03-07 Linde Ag Axialkolbenmaschine in schraegscheibenbauweise
US5862704A (en) * 1996-11-27 1999-01-26 Caterpillar Inc. Retainer mechanism for an axial piston machine
US5730042A (en) * 1996-12-04 1998-03-24 Caterpillar Inc. Retaining device for axial piston machines
DE19706263C1 (de) * 1997-02-18 1998-07-23 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit drehzahlabhängiger Anpressung der Zylindertrommel

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4872394A (en) * 1984-02-29 1989-10-10 Shimadzu Corporation Bent axis type axial piston pump or motor
US20030138331A1 (en) * 2002-01-22 2003-07-24 John Fox Metering pump with proportional output
DE102005047981A1 (de) 2005-10-06 2007-04-12 Linde Ag Axialkolbenmaschine in Schrägscheibenbauweise

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102575666A (zh) * 2009-10-06 2012-07-11 博格华纳扭矩输出系统公司 液压泵组件
CN102575666B (zh) * 2009-10-06 2014-08-13 博格华纳扭矩输出系统公司 液压泵组件
EP2418381A1 (fr) * 2010-08-12 2012-02-15 Mpp Gbr Moteur à piston axial hydraulique réglable, notamment pour des éoliennes et doté d'un entraînement principal hydrostatique et procédé de commande
CN102926959A (zh) * 2012-11-07 2013-02-13 三一重工股份有限公司 一种斜盘式柱塞泵或马达
WO2014206713A1 (fr) * 2013-06-25 2014-12-31 Robert Bosch Gmbh Machine à plateau oscillant comme pompe à pistons axiaux et/ou moteur à pistons axiaux
EP2930360A3 (fr) * 2014-04-08 2015-11-04 Linde Hydraulics GmbH & Co. KG Machine à piston axial dans une construction à axe oblique avec patins de guidage dans le plateau d'entraînement
US10001010B2 (en) 2014-04-08 2018-06-19 Linde Hydraulics Gmbh & Co. Kg Axial piston machine utilizing a bent-axis construction with slippers on the drive flange
CN109236597A (zh) * 2018-11-08 2019-01-18 四川航天烽火伺服控制技术有限公司 一种滑靴柱塞组件及一种柱塞泵

Also Published As

Publication number Publication date
JP2009097512A (ja) 2009-05-07
US20090095149A1 (en) 2009-04-16
EP2050957B1 (fr) 2012-06-20
JP5311383B2 (ja) 2013-10-09
US8037808B2 (en) 2011-10-18
DE102007049393A1 (de) 2009-04-16

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