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EP0163995A1 - Machine hydrostatique à pistons axiaux avec plateau oblique inclinable - Google Patents

Machine hydrostatique à pistons axiaux avec plateau oblique inclinable Download PDF

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Publication number
EP0163995A1
EP0163995A1 EP85105926A EP85105926A EP0163995A1 EP 0163995 A1 EP0163995 A1 EP 0163995A1 EP 85105926 A EP85105926 A EP 85105926A EP 85105926 A EP85105926 A EP 85105926A EP 0163995 A1 EP0163995 A1 EP 0163995A1
Authority
EP
European Patent Office
Prior art keywords
swash plate
actuator
piston machine
piston
housing
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.)
Withdrawn
Application number
EP85105926A
Other languages
German (de)
English (en)
Inventor
Heinz Berthold
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.)
Brueninghaus Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik 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
Priority claimed from DE19843428591 external-priority patent/DE3428591A1/de
Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0163995A1 publication Critical patent/EP0163995A1/fr
Withdrawn legal-status Critical Current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
    • F04B1/26—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 invention relates to an axial piston machine according to the preamble of claim 1.
  • the actuator is formed by a hydraulic actuating piston which is arranged on the side of the swash plate facing the piston and which, with respect to the cylinder drum axis, engages on the side of the swash plate to the side to which its pivot axis is also offset with respect to the cylinder drum axis.
  • the actuating piston is located radially next to the cylinder drum and is mounted in a cylinder which projects radially inwards from the housing of the axial piston machine.
  • the swash plate has a radially outwardly projecting shoulder on which the actuating piston engages.
  • a radially large design and, on the other hand, difficult assembly and disassembly of the swash plate and the adjusting piston are specified.
  • the large design is due to the fact that the actuating piston is arranged radially next to the cylinder drum.
  • the assembly or disassembly is difficult because the cylinder receiving the actuating piston is structurally due to a considerable degree in the protrudes into the free interior of the housing and thus not only makes it difficult to insert or remove the swash plate in or out of the housing, but also obscures the connection point at which the actuating piston is connected to the swash plate for the purpose of loading.
  • Another disadvantage of the known design is that this connection only has to be made after the swash plate has been inserted into the housing, which is difficult in view of the existing arrangement and the limited space.
  • the invention is based on the object of designing an axial piston machine of the type described at the outset such that, while ensuring a simple structural design and simple assembly or disassembly of the swash plate and the actuator, a defined limitation of the adjustment movement of the swash plate in the direction of the zero position or minimum flow rate is reached. This object is achieved by the features contained in claim 1.
  • the actuator is arranged on the side of the swash plate facing away from the piston, where it is in a position which does not hinder the dismantling or dismantling of the swash plate.
  • the swash plate can be removed and installed without the need for removal or adjustment of the actuator.
  • a simplification of the construction is given by the fact that the actuator can be arranged in the position according to the invention considerably easier than is the case with the known embodiment. This is particularly important with regard to the guide surfaces for the actuator, which in the embodiment according to the invention run transversely instead of longitudinally to the predetermined housing wall.
  • the design according to the invention Swiveling movement of the swash plate in the direction of zero position or minimum delivery rate not only clearly limited by a stop in a simple manner, but the swash plate is also fixed in the stop position between the actuator and the stop.
  • the configuration according to the invention leads to a space-saving design.
  • the housing need not be dimensioned larger than is necessary to accommodate the cylinder drum.
  • the axial enlargement of the housing, which is caused by the mounting of the actuator in the end wall of the housing according to the invention, is insignificant.
  • claims 2 and 3 lead to simple and practical configurations.
  • the embodiment according to claim 3 facilitates assembly and disassembly, because the stop can be brought into the working position after assembly of the swash plate.
  • adjustable stops can be realized, e.g. characterized in that the screw or a rotatable cam have eccentric stop surfaces or the screw has a conical stop section or the screw is arranged obliquely, so that an axial adjustment of the screw relative to the axial piston machine is possible.
  • the embodiment according to claim 4 enables a simple configuration of the adjusting device comprising the actuator and is intended for cases in which only two delivery quantity settings are desired. In such a case, there is no need to lock the adjuster link in its intermediate positions.
  • the swash plate is always loaded with a torque which acts against the actuator.
  • an actuator can be used which is only effective on one side, e.g. a one-way hydraulic piston.
  • a mechanical connection in the usual sense between the swash plate and the actuator, but the latter only has to press against the surface of the swash plate. The restoring movement of the actuator is forced by the torque described above.
  • the axial piston machine generally designated 1 in FIG. 1, has a two-part housing consisting of a cup-shaped housing part 2 and a housing cover 3, in which a drive shaft 5 extending along the central axis 4 is mounted in roller bearings 6, 7.
  • a cylinder drum 9 is mounted on the drive shaft 5 on a multi-key section designated 8, which cylinder cylinder 9 has a plurality of cylinder bores 11, in which pistons 12 are accommodated, evenly distributed over a pitch circle.
  • the pistons 12 have ball heads 13 which grip sliding shoes 14 which bear against the sliding surface 15 of a swash plate 16.
  • a retraction plate 17 which in the present exemplary embodiment is mounted on a spherical head-shaped carrier piece 18 with a recess in the form of a spherical segment.
  • the carrier piece 18 is longitudinal slidably mounted on the drive shaft 5 and is urged towards the swash plate 16 by means of an indicated compression spring 19, which is supported on the cylinder drum 9.
  • the swash plate 16 is mounted about a swivel axis 21 in a swivel bearing which is formed by two supports, generally designated 22, lying one behind the other along the swivel axis 21, consisting of two balls 23 which are located in spherical recesses 24 in the cup-shaped housing part 2 and in spherical recesses 25 store in swash plate 16.
  • the surfaces of the balls 23 facing the pistons and the spherical surfaces of the recesses 25 in the swash plate 16 thus form the bearing surfaces 26, 27 on the housing side and on the swash plate side.
  • the swash plate 16 is adjusted by means of a hydraulic piston 28, which is displaceably guided parallel to the drive shaft 5 in the flange part of the cup-shaped housing part 2 and can be hydraulically extended in the direction of the arrow 29. In the position shown, the swash plate 16 is in its maximum piston stroke position. By extending the hydraulic piston 28, the swash plate 16 can be adjusted about the pivot axis 21 until it abuts a stop 31 which is formed by a threaded screw which is screwed into the housing 2 at the side. In the stop position, the axial piston machine is set to a minimum piston stroke. In order to enable the skewed position shown, the swash plate 16 is chamfered on its side facing the supports 22. This inclined surface is designated 32.
  • the supports 22 and the piston 28 represent three support points (see FIG. 2) that define a support plane E, which in the position shown in FIG. 1 is directed approximately at right angles to the drive shaft 5.
  • the Balls 23 are secured against rotation about the pivot axis 21 by pins 33 engaging in them and in the housing part 2.
  • the spherical recesses 25 in the swash plate 16 are incorporated in spherical bearing shells 34 which rest with a collar 35 on the side of the swash plate 16 facing the supports 22.
  • the supports 22 are connected by lines 36 to the oil-carrying system of the axial piston machine 1 and are thus oil-lubricated.
  • compression spring 19 it is the purpose of the compression spring 19 to hold the swash plate 16 in contact with the supports 22.
  • compression springs which could be arranged in the cylinder bores 11 and act on the pistons 12 in the direction of the swash plate 16.
  • the cylinder drum 9 is rotated by the drive shaft 5.
  • the cylinder bores 11 alternately come into connection with control openings 37 in the form of kidneys in a control plate 38, one of which is connected to a supply line and the other to a discharge line for the hydraulic medium.
  • the direction of flow of the hydraulic medium is marked with arrow 39 for pump operation and with arrow 40 for motor operation.
  • the seal between the cylinder drum 9 and the control plate 38 is ensured by a compression spring 41, which is supported on the drive shaft 5 and acts on the cylinder drum 9 against the control plate 38.
  • the compression spring 41 engages an inner ring 42.
  • An advantageous embodiment also consists, at the same time, of the swash plate 16, indirectly or directly, by means of the compression spring 41 against the To support bearing 22. As a result, the pressure sensor 19 would cease to exist.
  • the compression spring 41 can act against the carrier piece 18.
  • the pivot axis 21 is located at a distance a from the line of action of the piston force 44 resulting from the forces of the active pistons 12.
  • the pivot axis 21 is offset toward the resultant piston force 44 on the side facing away from the piston 28.
  • the distance a is approximately 16 mm.
  • the resulting piston force 44 is generated by the pistons 12 located on the pressure side 43. Because of the distance a, the swash plate 16 is loaded with a torque in the counterclockwise direction. This ensures that the swash plate 16 bears against the piston 28 which acts as an actuator.
  • a support 22 can be designed as a so-called floating bearing, which is shown in FIG. 2.
  • the ball 23 on the right in FIG. 2 is received in a preferably round longitudinal groove 45 which extends towards the left ball 23.
  • the right ball 23 is thus kept movable along the pivot axis 21, so that small dimensional tolerances at distance b are harmless.
  • the assembly or disassembly of the swash plate is very simple because it can be inserted into the housing part 2 from the open side both individually and already mounted on the drive shaft 5 and can also be removed in the opposite direction.
  • a preferred embodiment of the axial piston machine 1 consists in adjusting its displacement volume in only one stage. That is, to limit the possibility of setting to minimum and maximum swallowing volume.
  • a switching valve not shown, is used to move the piston 28 either into its right stroke end position, in which the swash plate 16 rests against the stop 31 (minimum swallowing volume), or into its left stroke end position, in which it rests on a stop surface 47 on the housing (maximum Swallowing volume).
  • the flange part of the housing 2, designated 51 is designed in the sense of a cylinder, generally designated 52, which has a cylinder bore 53 and a working space 54.
  • the working space 54 is connected through a connection bore 55 to a hydraulic control line, not shown, which can be connected to the connection bore 55.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
EP85105926A 1984-05-23 1985-05-14 Machine hydrostatique à pistons axiaux avec plateau oblique inclinable Withdrawn EP0163995A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3419266 1984-05-23
DE3419266 1984-05-23
DE3428591 1984-08-02
DE19843428591 DE3428591A1 (de) 1984-08-02 1984-08-02 Hydrostatische axialkolbenmaschine

Publications (1)

Publication Number Publication Date
EP0163995A1 true EP0163995A1 (fr) 1985-12-11

Family

ID=25821481

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85105926A Withdrawn EP0163995A1 (fr) 1984-05-23 1985-05-14 Machine hydrostatique à pistons axiaux avec plateau oblique inclinable

Country Status (2)

Country Link
US (1) US4581980A (fr)
EP (1) EP0163995A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3733083A1 (de) * 1987-09-30 1989-04-13 Linde Ag Verstellbare axialkolbenmaschine in schraegscheibenbauweise
EP0661478A1 (fr) * 1993-12-30 1995-07-05 KOREA INSTITUTE OF MACHINERY & METALS Mécanisme de changement de vitesse pour moteur hydraulique à plateau oblique
DE4440452A1 (de) * 1994-03-02 1995-09-07 Kubota Kk Zwischen einer hohen und einer niedrigen Geschwindigkeit schaltbarer Taumelscheiben-Hydraulikmotor

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6149175A (ja) * 1984-08-16 1986-03-11 Kayaba Ind Co Ltd 可変容量型油圧ポンプまたはモ−タの制御装置
DE3519783A1 (de) * 1985-06-03 1986-12-04 Danfoss A/S, Nordborg Axialkolbenmaschine
DE3519822A1 (de) * 1985-06-03 1986-12-04 Danfoss A/S, Nordborg Einstellbare axialkolbenmaschine
US4945817A (en) * 1989-10-24 1990-08-07 General Motors Corporation Axial piston device
JP2559632B2 (ja) * 1989-11-22 1996-12-04 株式会社小松製作所 斜板式ピストンポンプ・モータの斜板角度変更装置
DE3942189C1 (fr) * 1989-12-20 1991-09-05 Hydromatik Gmbh, 7915 Elchingen, De
JP2626292B2 (ja) * 1991-03-30 1997-07-02 株式会社豊田自動織機製作所 容量可変型斜板式圧縮機
US5364232A (en) * 1992-03-03 1994-11-15 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
US5304042A (en) * 1992-04-10 1994-04-19 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Variable displacement compressor
JPH0763157A (ja) * 1993-08-26 1995-03-07 Kanzaki Kokyukoki Mfg Co Ltd 可変容量型アキシャルピストン機械
JP3874308B2 (ja) * 1994-10-18 2007-01-31 株式会社小松製作所 斜板式ピストンポンプ・モータの斜板角度変更装置
US5515768A (en) * 1995-02-28 1996-05-14 Caterpillar Inc. Slipper holddown device for an axial piston pump
US5794515A (en) * 1997-04-03 1998-08-18 Bethke; Donald G. Swashplate control system for an axial piston pump
JP2000088023A (ja) * 1998-09-10 2000-03-28 Toyota Autom Loom Works Ltd バネ端の位置決め構造及びその位置決め構造を備えた圧縮機
DE10035630C1 (de) * 2000-07-21 2002-03-14 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit einer Rückzugeinrichtung
JP4107967B2 (ja) 2001-04-05 2008-06-25 ザ オイルギア カンパニー 軸方向ピストンポンプ用サドル軸受ライナー
EP1395753B1 (fr) * 2001-05-26 2006-08-23 Robert Bosch Gmbh Pompe haute pression pour un systeme de carburant d'un moteur a combustion interne
DE102007048316B4 (de) * 2007-10-09 2010-05-27 Danfoss A/S Hydraulische Axialkolbenmaschine
KR101967505B1 (ko) * 2012-12-26 2019-04-09 나부테스코 가부시키가이샤 경사판식 유압 모터 또는 경사판식 유압 펌프
DE102014215024A1 (de) 2013-09-06 2015-03-12 Robert Bosch Gmbh Im Hubvolumen verstellbare hydrostatische Axialkolbenmaschine, inbesondere im Hubvolumen verstellbarer hydrostatischer Axialkobenmotor
DE102017206901A1 (de) 2017-04-25 2018-10-25 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE637140A (fr) *
GB588451A (en) * 1945-01-02 1947-05-22 Lapointe Machine Tool Co Improvements in or relating to revolving cylinder reciprocating pumps
GB752021A (en) * 1953-06-25 1956-07-04 Nils Einar Olzon Improvements in or relating to piston pumps
GB866661A (en) * 1958-12-05 1961-04-26 Bendix Corp Axial piston swash type pump
GB954715A (en) * 1962-03-22 1964-04-08 Lucas Industries Ltd Hydraulic pumps
GB1055286A (en) * 1963-09-10 1967-01-18 Lucas Industries Ltd Hydraulic pumps and motors

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2379546A (en) * 1937-06-09 1945-07-03 Ex Cell O Corp Hydraulic transmission
GB500299A (en) * 1937-08-16 1939-02-07 Joseph Yoxall Improved revolving-cylinder fluid pump or motor
DE1055959B (de) * 1957-08-31 1959-04-23 Bosch Gmbh Robert Pumpe mit hin- und hergehenden Pumpenkolben
US3412447A (en) * 1966-03-31 1968-11-26 Lucas Industries Ltd Mounting carbon inserts in a metal body

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
BE637140A (fr) *
GB588451A (en) * 1945-01-02 1947-05-22 Lapointe Machine Tool Co Improvements in or relating to revolving cylinder reciprocating pumps
GB752021A (en) * 1953-06-25 1956-07-04 Nils Einar Olzon Improvements in or relating to piston pumps
GB866661A (en) * 1958-12-05 1961-04-26 Bendix Corp Axial piston swash type pump
GB954715A (en) * 1962-03-22 1964-04-08 Lucas Industries Ltd Hydraulic pumps
GB1055286A (en) * 1963-09-10 1967-01-18 Lucas Industries Ltd Hydraulic pumps and motors

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3733083A1 (de) * 1987-09-30 1989-04-13 Linde Ag Verstellbare axialkolbenmaschine in schraegscheibenbauweise
EP0661478A1 (fr) * 1993-12-30 1995-07-05 KOREA INSTITUTE OF MACHINERY & METALS Mécanisme de changement de vitesse pour moteur hydraulique à plateau oblique
DE4440452A1 (de) * 1994-03-02 1995-09-07 Kubota Kk Zwischen einer hohen und einer niedrigen Geschwindigkeit schaltbarer Taumelscheiben-Hydraulikmotor
FR2716939A1 (fr) * 1994-03-02 1995-09-08 Kubota Kk Moteur hydraulique à plateau oscillant.
US5649468A (en) * 1994-03-02 1997-07-22 Kubota Corporation Swash plate type hydraulic motor having offset swash plate pivot axis

Also Published As

Publication number Publication date
US4581980A (en) 1986-04-15

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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Inventor name: BERTHOLD, HEINZ