EP0953111A1 - Machine a pistons axiaux comportant un element d'amortissement pour le disque incline ou oscillant - Google Patents

Machine a pistons axiaux comportant un element d'amortissement pour le disque incline ou oscillant

Info

Publication number
EP0953111A1
EP0953111A1 EP97910399A EP97910399A EP0953111A1 EP 0953111 A1 EP0953111 A1 EP 0953111A1 EP 97910399 A EP97910399 A EP 97910399A EP 97910399 A EP97910399 A EP 97910399A EP 0953111 A1 EP0953111 A1 EP 0953111A1
Authority
EP
European Patent Office
Prior art keywords
swash plate
damping
axial piston
piston machine
cylinder
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
EP97910399A
Other languages
German (de)
English (en)
Other versions
EP0953111B1 (fr
Inventor
Rainer Stölzer
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 Hydromatik GmbH
Original Assignee
Brueninghaus 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0953111A1 publication Critical patent/EP0953111A1/fr
Application granted granted Critical
Publication of EP0953111B1 publication Critical patent/EP0953111B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
    • F03C1/0678—Control
    • F03C1/0686—Control by changing the inclination of the swash plate

Definitions

  • the invention relates to an axial piston machine according to the preamble of claim 1.
  • Such an axial piston machine is e.g. known from DE 34 28 591 AI.
  • a plurality of cylinder bores in which pistons are movably guided are formed in a rotating cylinder block in a known manner.
  • the pistons are supported by sliding shoes on a non-rotating swash plate.
  • the inclination of the swash plate, which determines the displacement volume of the axial piston machine can be adjusted by means of a hydraulic adjusting piston, in that the swash plate can be swiveled around a swivel axis within a certain angular range.
  • the invention is based on the knowledge that the swiveling back of the swashplate or swashplate can be controlled by providing a damping element engaging the swashplate or swashplate.
  • the damping piston is movably arranged in a damping cylinder which is connected to a pressure fluid reservoir via a throttle element and a check valve arranged parallel to the throttle element.
  • the check valve ensures an unthrottled inflow of the pressure fluid from the pressure fluid reservoir into the damping cylinder and prevents an unthrottled outflow of the pressure fluid from the damping cylinder bypassing the throttle element.
  • the return spring can act on the damping piston in such a way that this pressure fluid draws in from the pressure fluid reservoir via the check valve and possibly the throttle element as soon as the damping piston is freely movable in the direction of increasing the volume of the damping cylinder. This ensures that the damping cylinder is instantly refilled with pressurized fluid and thus immediately follows the swiveling movement of the swashplate or swashplate.
  • the pressure medium reservoir can be a leakage fluid collection chamber in the vicinity of the damping element, wherein the leakage fluid collection chamber is usually formed by the housing interior of the axial piston machine.
  • the swash plate or swash plate can be a first according to claim 5
  • the axial piston machine can also be designed according to claim 6 in a swash plate design, wherein the
  • Claim 9 can be arranged in a stationary counterpart opposite the swash plate.
  • the return spring holds the damping piston on the
  • the swash plate can also have a first and a second stop surface on the side facing away from the piston, each of which form a stop for the first and the second swivel position of the swash plate.
  • FIG. 1 shows a partial axial section through a first embodiment of the axial piston machine further developed according to the invention in a first swivel position of the swash plate;
  • Fig. 2 shows the first embodiment shown in Fig. 1 of the axial piston machine according to the invention in a second pivot position
  • Fig. 3 is a schematic representation of the operation of the damping element
  • FIG. 4A shows the force distribution on the embodiment of the axial piston machine further developed according to the invention shown in FIG. 1;
  • FIG. 4B shows a side view of the illustration according to FIG. 4A
  • 4C is a plan view of the representation corresponding to FIG. 4A;
  • Fig. 5 is a partial, axial section through a second embodiment of the axial piston machine according to the invention in a second
  • FIG. 6 shows the second exemplary embodiment of the axial piston machine which is further developed according to the invention in a second swivel position of the swash plate.
  • FIGS. 1 and 2 show an axial longitudinal section through an axial piston machine 1 which is only partially shown and which is further developed according to the invention.
  • the axial piston machine 1 shown by way of example in FIGS. 1 and 2 is constructed in a swash plate construction and comprises a cylinder block 2, in which several cylinder bores 3, 4 arranged uniformly distributed in a pitch circle. Pistons 5, 6 are arranged movably in the cylinder bores 3, 4. The cylinder bores 3, 4 are connected via connection channels 7, 8 to the kidney-shaped control openings 9, 10 of a stationary control disk 11.
  • the cylinder block 2 rotates about the cylinder block axis 12, so that the cylinder bores 3, 4 are cyclically connected to a low-pressure line, not shown, connected to the control opening 9 and to a high-pressure line, not shown, connected to the control opening 10.
  • the pistons 5, 6 are formed at the ends facing away from the control disk 11 to spherical heads 13, 14, which are mounted in spherical bearings 15, 16 by the pistons 5, 6 associated slide shoes 17, 18.
  • the pistons 5, 6 are designed as hollow pistons and each have one
  • the piston recesses 19, 20 are via connecting channels 21, 22 of the pistons 5, 6 and further via connecting channels 23, 24 of the
  • Sliding shoes 17, 18 for hydrostatic relief connected to pressure pockets provided on the sliding shoes 17, 18.
  • the pistons 5, 6 are supported on the sliding shoes 17, 18 on a sliding surface 26 of the swash plate 25.
  • the swash plate 25 is pivotally mounted about a pivot axis 27 and has a first stop surface 28 and a second stop surface 29 on the side facing away from the pistons 5, 6. If the swash plate, as shown in FIG. 1, bears against a stationary counterpart 30 on its first stop surface 28, the swash plate or its sliding surface 26 is inclined at a first, relatively large angle of inclination with respect to the cylinder block axis 12.
  • the swash plate as shown in Fig. 2, however, on its second stop surface 29 on the stationary counterpart
  • the swash plate or its sliding surface 26 is inclined with respect to the cylinder block axis 12 with a second inclination angle with respect to the cylinder block axis 12, which angle is smaller than the first angle of inclination.
  • the inclination of the swash plate 25 is therefore in the exemplary embodiment between two discrete pivot positions by means of a pivot device which is only indicated schematically
  • the pivot device 31 can be swung back and forth.
  • the pivot device 31 can e.g. comprise a hydraulically actuated actuating piston which non-positively engages the swash plate 25.
  • the damping piston 40 of a damping element also acts on the swash plate 25.
  • the damping element 41 is integrated in the swash plate 25.
  • the damping piston 40 is movably arranged in a damping cylinder 42 provided in the swash plate 25 in the exemplary embodiment in FIGS. 1 and 2.
  • the damping cylinder 42 is designed as a blind bore which opens out on the second stop surface 29 of the swash plate 25.
  • the damping piston 40 is also by means of a in the damping cylinder 42 arranged return spring 43 on the stationary
  • the stationary counterpart 30 can e.g. act as a housing end plate.
  • the damping cylinder 42 is connected via a check valve 44 and an inlet channel 45 to the housing interior 46 surrounding the swash plate 25 and the cylinder block 2, which serves as a leakage fluid collecting space and is accordingly filled with leakage fluid.
  • the damping cylinder 42 is additionally connected to the housing interior 46 of the axial piston machine 1 via a throttle element 47.
  • the throttle element 47 is designed in the illustrated embodiment as a bore with a relatively small cross section.
  • the inlet channel 45 and the check valve 44 are thus arranged parallel to the throttle element 47.
  • the damping element 41 according to the invention works as follows:
  • the check valve 44 closes the inlet channel 45 and the pressure fluid located in the damping cylinder 42 can only flow out of the damping cylinder 42 via the throttle element 47.
  • the desired damping is achieved and it is prevented that the swiveling movement of the swash plate 25 occurs abruptly and the stop surface 29 strikes the stationary counterpart 30 hard. The latter would to a relatively quick wear of the swash plate 25 and the stationary
  • Swinging movement is subjected to a shock load, which is undesirable.
  • the damping element 41 provided according to the invention, the pivoting process is therefore slightly delayed and a continuous, non-abrupt pivoting movement of the swash plate 25 is achieved. Furthermore, the damping element 41 according to the invention in the second swivel position shown in FIG. 1 and during the swiveling from the first swivel position shown in FIG. 1 to the second swivel position shown in FIG. 2 ensures a certain support of the one in FIG. 1 above the swivel axis 27 Section of the swash plate 25, so that the loads to which the swash plate 25 is exposed are advantageously reduced by the development according to the invention.
  • FIG. 3 illustrates the mode of operation of the damping element 41 according to the invention on the basis of a hydraulic equivalent circuit diagram. Elements already described are labeled with the same reference numerals in order to facilitate the assignment.
  • the suction of the pressure fluid takes place from a pressure fluid reservoir 48, which e.g. the housing interior 46 can be via the inlet channel 45 and the check valve 44 arranged between the inlet channel 45 and the damping cylinder 42.
  • the throttle element 47 is arranged parallel to the check valve 44 and the inlet channel 45, which means that the check valve 44 is closed for a throttled outflow of the pressure fluid from the pressure fluid cylinder 42 into the pressure fluid reservoir 48.
  • FIGS. 4A to 4C illustrate the distribution of forces on the axial piston machine 1 further developed according to the invention in accordance with the exemplary embodiment already explained with reference to FIGS. 1 and 2.
  • 4A shows a representation corresponding to FIG. 1
  • FIG. 4B shows a side view looking towards the side of the swash plate 25 facing away from the pistons 5
  • FIG. 4C shows a top view of the arrangement shown in FIG. 4A.
  • FIG. 5 and 6 show an axial longitudinal section through a second exemplary embodiment of an axial piston machine 1 which has been further developed according to the invention. Elements already described are provided with the same reference numerals, so that a repeated description in this regard is unnecessary.
  • FIGS. 5 and 6 differs from the embodiment shown in FIGS. 1 and 2 in that the damping element 41 according to the invention is not in the swash plate 25, but on the stationary counterpart 30 opposite the swash plate 25, for example in a housing end plate is arranged.
  • the damping element 41 essentially has the structure already described with reference to FIG. 1.
  • the damping piston 40 is movably arranged in the damping cylinder 42 and is acted upon by the return spring 43 so that the Damping piston 40 on the swash plate 25, preferably on the second
  • Stop surface 29 is present.
  • the suction of the pressure fluid from the housing interior 46 takes place via the inlet channel 49 and the check valve 44 opened in the suction phase.
  • the pressure fluid is pressed out of the damping cylinder 42 via the throttle element 47, which is also designed as a small-diameter bore in this exemplary embodiment, and the adjoining outlet channel 48, which results in the intended damping of the movement of the swash plate 25 and the support of the swash plate 25 during pivoting.
  • the invention is not restricted to the exemplary embodiments shown. As mentioned at the beginning, the present invention can also be used in the case of axial piston machines in a swashplate design.
  • the damping arrangement can also be arranged at any other point, provided that it is ensured that the damping piston 40 engages in a suitable manner on the swash plate 25 or the swash plate.
  • additional damping elements can be provided in the area of the first stop surface 28 in order to ensure sufficient damping for the other pivoting direction.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une machine à piston axial (1) comportant un bloc-cylindres (2) dans lequel sont prévus deux alésages de cylindres (3, 4), dans lesquels sont guidés de manière mobile des pistons (5, 6) qui s'appuient sur un disque incliné ou oscillant (25) afin d'effectuer un mouvement de levée, ainsi qu'un dispositif de pivotement (31) servant à modifier l'inclinaison du disque incliné ou oscillant (25) par pivotement autour d'un axe de pivotement (27). Selon l'invention, il est prévu un élément d'amortissement (41) qui comprend un piston d'amortissement (40) qui agit sur le disque incliné ou oscillant (25) et est monté mobile dans un cylindre d'amortissement (42) qui est relié quant à lui à un réservoir de fluide sous pression (48) par l'intermédiaire d'un élément d'étranglement (47) et un clapet antiretour (44) monté parallèlement à l'élément d'étranglement (47). Le clapet antiretour (44) permet au fluide sous pression d'être acheminé sans étranglement du réservoir (48) le contenant jusque dans le cylindre d'amortissement (42) et évite que ledit fluide sous pression de s'écoule avec étranglement hors du cylindre d'amortissement (42), par contournement de l'élément d'étranglement (47). Ce système permet d'obtenir un mouvement pivotant amorti du disque incliné ou oscillant (25).
EP97910399A 1996-11-05 1997-10-01 Machine a pistons axiaux comportant un element d'amortissement pour le disque incline ou oscillant Expired - Lifetime EP0953111B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19645580A DE19645580C1 (de) 1996-11-05 1996-11-05 Axialkolbenmaschine mit Dämpfungselement für die Schräg- oder Taumelscheibe
DE19645580 1996-11-05
PCT/EP1997/005396 WO1998020258A1 (fr) 1996-11-05 1997-10-01 Machine a pistons axiaux comportant un element d'amortissement pour le disque incline ou oscillant

Publications (2)

Publication Number Publication Date
EP0953111A1 true EP0953111A1 (fr) 1999-11-03
EP0953111B1 EP0953111B1 (fr) 2001-12-19

Family

ID=7810702

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97910399A Expired - Lifetime EP0953111B1 (fr) 1996-11-05 1997-10-01 Machine a pistons axiaux comportant un element d'amortissement pour le disque incline ou oscillant

Country Status (5)

Country Link
US (1) US6174139B1 (fr)
EP (1) EP0953111B1 (fr)
JP (1) JP3956058B2 (fr)
DE (2) DE19645580C1 (fr)
WO (1) WO1998020258A1 (fr)

Families Citing this family (15)

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Publication number Priority date Publication date Assignee Title
DE19857082A1 (de) * 1998-12-10 2000-06-21 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine
DE19912509C2 (de) * 1999-03-19 2002-11-07 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine
EP1045304A1 (fr) 1999-04-16 2000-10-18 Martine Naillon Procédé de pilotage d'un processus décisionnel lors de la poursuite d'un but dans un domaine d'application déterminé, tel qu'économique, technique organisationnel ou analogue et système pour la mise en oeuvre du procédé
DE10035630C1 (de) * 2000-07-21 2002-03-14 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit einer Rückzugeinrichtung
DE10360452B3 (de) * 2003-12-22 2005-09-08 Brueninghaus Hydromatik Gmbh Axialkolbenmaschine mit fixierbarem Gleitstein an der Schrägscheibe
US7308790B1 (en) 2004-09-30 2007-12-18 Hydro-Gear Limited Partnership Adjustable hydraulic motor apparatus
EP1705372A1 (fr) * 2005-03-11 2006-09-27 Innas B.V. Pompe variable ou moteur hydraulique
JP2008128222A (ja) * 2006-11-27 2008-06-05 Shin Caterpillar Mitsubishi Ltd 斜板型液圧回転装置
DE102006062065A1 (de) * 2006-12-29 2008-07-03 Robert Bosch Gmbh Axialkolbenmaschine mit einem einen radial erweiterten Innenraumabschnitt aufweisenden Gehäuse
US7806040B2 (en) * 2007-09-12 2010-10-05 Sauer-Danfoss Inc. Ball supported swashplate for axial piston hydraulic machine
US8333571B2 (en) * 2008-12-12 2012-12-18 Caterpillar Inc. Pump having pulsation-reducing engagement surface
US8334604B1 (en) * 2010-09-30 2012-12-18 The United States Of America As Represented By The Secretary Of The Navy Integrated external combustion cam engine-generator
US20140134008A1 (en) * 2012-11-13 2014-05-15 Caterpillar Inc. Pump having pulsation-reducing engagement surface
JP2015031223A (ja) * 2013-08-05 2015-02-16 カヤバ工業株式会社 可変容量型ピストンポンプ・モータ
JP2015031224A (ja) * 2013-08-05 2015-02-16 カヤバ工業株式会社 可変容量型ピストンポンプ・モータ

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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
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Also Published As

Publication number Publication date
JP3956058B2 (ja) 2007-08-08
JP2001503493A (ja) 2001-03-13
EP0953111B1 (fr) 2001-12-19
US6174139B1 (en) 2001-01-16
DE19645580C1 (de) 1998-04-02
DE59705927D1 (de) 2002-01-31
WO1998020258A1 (fr) 1998-05-14

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