EP0953111B1 - 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 Download PDF

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Publication number
EP0953111B1
EP0953111B1 EP97910399A EP97910399A EP0953111B1 EP 0953111 B1 EP0953111 B1 EP 0953111B1 EP 97910399 A EP97910399 A EP 97910399A EP 97910399 A EP97910399 A EP 97910399A EP 0953111 B1 EP0953111 B1 EP 0953111B1
Authority
EP
European Patent Office
Prior art keywords
damping
axial piston
piston machine
machine according
pressure fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP97910399A
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German (de)
English (en)
Other versions
EP0953111A1 (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
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Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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 A1.
  • Cylinder bores are formed in which pistons are movably guided.
  • the pistons are supported by sliding shoes on a non-rotating swashplate.
  • the inclination the swash plate which determines the displacement of the axial piston machine adjustable by means of a hydraulic adjusting piston by turning the swash plate by one Swivel axis is pivotable within a certain angular range.
  • DE 44 40 452 A1 describes an axial piston machine in a swashplate design in which two separate for the variation of the inclination of the swash plate Hydraulic cylinders are provided.
  • One of the hydraulic cylinders serves the purpose Swinging out the swash plate and the second hydraulic cylinder Swing the swashplate back.
  • the swashplate is used in this solution guided throughout the entire movement, but the second requires Hydraulic cylinder a comparatively large design effort, which can be found in relative high manufacturing costs.
  • the present invention is therefore based on the object of an axial piston machine in swashplate or swashplate construction so that the movement when swashing the swashplate or swashplate not suddenly, but done continuously.
  • the object is in connection with the characterizing features of claim 1 solved with the generic features.
  • the invention is based on the finding that by providing an inclined or swash plate attacking damping element swiveling back the inclined or swashplate can be checked.
  • the damping piston is in one Damping cylinder arranged movably, which via a throttle element and a Check valve arranged parallel to the throttle element with a pressure fluid reservoir connected is.
  • the check valve ensures an unthrottled inflow of the pressure fluid from the pressure fluid reservoir into the damping cylinder and prevented an unthrottled outflow of the pressure fluid from the damping cylinder below Bypassing the throttle element.
  • the return spring, the damping piston act that this pressure fluid from the pressure fluid reservoir via the Check valve and, if necessary, the throttle element as soon as the damping piston is in Direction of an increase in the volume of the damping cylinder is freely movable. This ensures that the damping cylinder is instantly filled with pressurized fluid is refilled and thus the swiveling movement of the swashplate or swashplate immediately follows.
  • the pressure medium reservoir can be a leakage fluid collecting space according to claim 4 be in the vicinity of the damping element, the leakage fluid collecting space usually through the housing interior of the axial piston machine is formed.
  • the swash plate or swash plate can be a first according to claim 5 Swivel position with a larger angle of inclination and a second swivel position have a smaller angle of inclination and between these two Be swiveling back and forth.
  • the axial piston machine can also be designed according to claim 6 in swash plate construction, wherein Damping element according to claim 7 in the swash plate or accordingly Claim 9 in a stationary counterpart opposite the swash plate can be arranged.
  • the return spring holds the damping piston on the Swash plate according to claim 10 or on the stationary counterpart according to claim 8 on surcharge.
  • the swash plate can also according to claim 11 on the side facing away from the piston Side have a first and a second stop surface, each having a stop for form the first and second swivel positions of the swash plate.
  • FIG. 1 and 2 show an axial longitudinal section through an only partially shown, Axial piston machine 1 developed according to the invention.
  • the in FIG. 1 and FIG. 2 Axial piston machine 1 shown by way of example is designed in a swashplate design and comprises a cylinder block 2, in which several, evenly on a pitch circle Distributed cylinder bores 3, 4 are provided.
  • pistons 5, 6 are arranged movably.
  • the cylinder bores 3, 4 are over Connection channels 7, 8 with the kidney-shaped control openings 9, 10 of a stationary Control disc 11 connected.
  • the cylinder block 2 rotates about the cylinder block axis 12, see above that the cylinder bores 3, 4 cyclically with one at the control opening 9 connected, not shown low pressure line and one at the control opening 10 connected, not shown high pressure line can be connected.
  • the pistons 5, 6 are formed into spherical heads 13, 14 at the ends facing away from the control disk 11, the sliding shoes 17, 18 assigned by the pistons 5, 6 in spherical bearings 15, 16 are stored.
  • the pistons 5, 6 are designed as hollow pistons and each have one Piston recess 19, 20 on.
  • the piston recesses 19, 20 are over 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 with on the sliding shoes 17, 18 provided pressure pockets connected.
  • the pistons 5, 6 are supported by the sliding shoes 17, 18 on a sliding surface 26 Swashplate 25 from.
  • the swash plate 25 is pivotable about a pivot axis 27 mounted and has a first stop surface 28 on the side facing away from the pistons 5, 6 and a second stop surface 29. If the swash plate, as shown in Fig. 1, is in contact with a stationary counterpart 30 on its first stop surface 28 Swash plate or its sliding surface 26 with a first, relatively large angle of inclination inclined with respect to the cylinder block axis 12. If the swash plate, as in Fig.
  • the swash plate or its sliding surface 26 is opposite the cylinder block axis 12 with a second, smaller than the first angle of inclination Inclination angle inclined to the cylinder block axis 12.
  • the inclination of the Swash plate 25 is therefore in the embodiment between two discrete Swivel positions by means of a swivel device which is only indicated schematically 31 can be swung back and forth.
  • the pivot device 31 can e.g. one hydraulic act upon actuating piston which is non-positively on the swash plate 25 attacks.
  • the damping piston 40 also engages on the swash plate 25 generally indicated at 41 damping element. 1 and 2
  • the exemplary embodiment shown is the damping element 41 in the swash plate 25 integrated.
  • the damping piston 40 is in one in the exemplary embodiment of FIGS. 1 and 2 provided in the swash plate 25 provided damping cylinder 42 movable.
  • the Damping cylinder 42 is designed as a blind bore on the second stop surface 29 of the swash plate 25 opens out.
  • the damping piston 40 is also by means of a in the damping cylinder 42 arranged return spring 43 on the stationary Counterpart 30 brought to the plant.
  • the stationary counterpart 30 can e.g. act as a housing end plate.
  • the damping cylinder 42 is over a Check valve 44 and an inlet channel 45 with which the swash plate 25 and Cylinder block 2 surrounding housing interior 46 connected as a leakage fluid collection space serves and is filled accordingly with leakage fluid.
  • the damping cylinder 42 is also via a throttle element 47 with the housing interior 46 Axial piston machine 1 connected.
  • the throttle element 47 is shown in FIG Embodiment designed as a bore with a relatively small cross section.
  • the Inlet channel 45 and check valve 44 are thus parallel to throttle element 47 arranged.
  • the damping element 41 according to the invention works as follows:
  • the damping piston 40 is by means of Return spring 43 held on the stationary counterpart 30 in contact. Doing so Pressure fluid via the inlet channel 45 and the open check valve 44 and in parallel Via the throttle element 47 from the housing interior 46 filled with leakage fluid sucked in.
  • the damping cylinder 42 is filled via the inlet channel 45 and the check valve 44 so quickly that the damping piston 40 on the stationary Counterpart 30 is kept in constant investment.
  • the Swiveling process therefore slightly delayed and a continuous, not abrupt Swiveling movement of the swash plate 25 achieved.
  • This also ensures Damping element 41 according to the invention in the second shown in Fig. 1 Pivotal position and during the pivoting of the first shown in Fig. 1 A certain pivot position in the second pivot position shown in FIG. 2 Support of the section of FIG. 1 located above the pivot axis 27 Swash plate 25 so that the loads to which the swash plate 25 is exposed can be advantageously reduced by the training according to the invention.
  • FIG. 3 illustrates the mode of operation of the damping element 41 according to the invention based on a hydraulic equivalent circuit diagram. Elements already described are included Identical reference numerals designated to facilitate the assignment. How already described, 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 that arranged between the inlet channel 45 and the damping cylinder 42 Check valve 44. This is parallel to the check valve 44 and the inlet channel 45 Throttle element 47 arranged, which when the check valve 44 is closed throttled outflow of the pressure fluid from the pressure fluid cylinder 42 into the Pressure fluid reservoir 48 provides.
  • a pressure fluid reservoir 48 which e.g. the housing interior 46 can be via the inlet channel 45 and that arranged between the inlet channel 45 and the damping cylinder 42
  • Check valve 44 This is parallel to the check valve 44 and the inlet channel 45
  • Throttle element 47 arranged, which when the check valve 44 is closed throttled outflow of the pressure fluid from the pressure fluid
  • FIGS. 1 and 2 illustrate the distribution of forces on the invention further developed axial piston machine 1 corresponding to that already shown in FIGS. 1 and 2 explained embodiment.
  • 4A shows one corresponding to FIG. 1 Representation
  • Fig. 4B is a side view looking towards the piston 5
  • 6 shows the side of the swash plate 25 facing away
  • FIG 4A shows the arrangement shown.
  • FIGS. 5 and 6 differs from that in 1 and 2 embodiment shown in that the inventive Damping element 41 not in the swash plate 25, but on that of the swash plate 25 opposite stationary counterpart 30, e.g. in a housing end plate, is arranged.
  • the damping element 41 essentially has the already based on Fig. 1 described structure.
  • the damping piston 40 is in the damping cylinder 42 is movably arranged 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 interior of the housing 46 takes place via the inlet channel 49 and the check valve opened in the suction phase 44.
  • the invention is not restricted to the exemplary embodiments shown. How mentioned at the beginning, the present invention can also be used in axial piston machines Swashplate construction are used.
  • the damping arrangement can also be arranged at any other place, provided that it is guaranteed that the Damping piston 40 in a suitable manner on the swash plate 25 or Swashplate attacks.
  • additional damping elements in the area of First stop surface 28 may be provided to a for the other pivoting direction to ensure adequate cushioning.

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

Claims (12)

  1. Machine (1) à pistons axiaux comprenant un bloc-cylindres (2) dans lequel sont prévus des alésages cylindriques (3, 4) dans lesquels sont guidés, avec mobilité, des pistons (5, 6) prenant appui contre un disque (25) incliné ou oscillant, en vue d'accomplir une course, et un dispositif de pivotement (31) conçu pour faire varier l'inclinaison du disque (25) incliné ou oscillant, par pivotement autour d'un axe de pivotement (27),
    caractérisée par
    au moins un élément d'amortissement (41) muni d'un piston amortisseur (40) venant en prise avec le disque (25) incliné ou oscillant et logé, avec mobilité, dans un cylindre amortisseur (42) qui est raccordé à un réservoir (48) à fluide pressurisé, par l'intermédiaire d'un élément d'étranglement (47) et d'un clapet antiretour (44) agencé parallèlement audit élément d'étranglement (47),
    sachant que ledit clapet antiretour (44) permet l'afflux non étranglé du fluide pressurisé dans le cylindre amortisseur (42), à partir du réservoir (48) à fluide pressurisé, et empêche l'évacuation non étranglée dudit fluide pressurisé, à partir dudit cylindre amortisseur (42), avec contournement de l'élément d'étranglement (47).
  2. Machine à pistons axiaux selon la revendication 1,
    caractérisée par le fait qu'un ressort de rappel (43) sollicite le piston amortisseur (40) de façon telle que ce dernier continue d'aspirer du fluide pressurisé à partir du réservoir (48) à fluide pressurisé, par l'intermédiaire du clapet antiretour (44), aussitôt que ledit piston amortisseur (40) peut se mouvoir librement dans le sens d'un accroissement du volume du cylindre amortisseur (42).
  3. Machine à pistons axiaux selon la revendication 2,
    caractérisée par le fait que le fluide pressurisé subit une post-aspiration additionnelle de la part de l'élément d'étranglement (47).
  4. Machine à pistons axiaux selon l'une des revendications 1 à 3,
    caractérisée par le fait que le réservoir (48) à fluide pressurisé se présente comme une chambre collectrice de fuites de fluide, en particulier comme l'espace interne (46) du carter de ladite machine (1) à pistons axiaux.
  5. Machine à pistons axiaux selon l'une des revendications 1 à 4,
    caractérisée par le fait que le disque (25) incliné ou oscillant peut être animé d'un va-et-vient pivotant, au moyen du dispositif de pivotement (31), entre une première position prise par pivotement (figure 1, figure 5) et correspondant à un grand angle d'inclinaison, et une seconde position prise par pivotement (figure 2, figure 6) et correspondant à un angle d'inclinaison plus petit,
    sachant que l'élément d'amortissement (41) amortit le mouvement pivotant lors du pivotement du disque (25) incliné ou oscillant s'opérant depuis la première jusqu'à la seconde position prise par pivotement, du fait de l'évacuation étranglée du fluide pressurisé à partir du cylindre amortisseur (42).
  6. Machine à pistons axiaux selon l'une des revendications 1 à 5,
    caractérisée par le fait que ladite machine (1) à pistons axiaux est du type de réalisation à disque incliné, et les pistons (5, 6), logés dans les alésages cylindriques (3, 4) du bloc-cylindres (2) tournant autour d'un axe (12), prennent appui contre un disque incliné (25) fixe.
  7. Machine à pistons axiaux selon la revendication 6,
    caractérisée par le fait que l'élément d'amortissement (41) est disposé dans ou sur le disque incliné (25).
  8. Machine à pistons axiaux selon la revendication 7,
    caractérisée par le fait que le piston amortisseur (40) est maintenu, par l'intermédiaire du ressort de rappel (43), en butée contre une pièce complémentaire fixe (30) située en vis-à-vis du disque incliné (25).
  9. Machine à pistons axiaux selon la revendication 6,
    caractérisée par le fait que l'élément d'amortissement (41) est disposé dans ou sur une pièce complémentaire fixe (30) située en vis-à-vis du disque incliné (25).
  10. Machine à pistons axiaux selon la revendication 9,
    caractérisée par le fait que le piston amortisseur (40) est maintenu en butée contre le disque incliné (25) par l'intermédiaire du ressort de rappel (43).
  11. Machine à pistons axiaux selon la revendication 5 et l'une des revendications 6 à 10,
    caractérisée par le fait que le disque incliné (25) présente des première (28) et seconde (29) surfaces de butée, du côté tourné à l'opposé des pistons (5, 6) ; et ledit disque incliné prend la première position prise par pivotement (figure 1, figure 5), et associée à un grand angle d'inclinaison, lors d'une venue en butée contre la première surface de butée (28), et la seconde position prise par pivotement (figure 2, figure 6), et associée à un angle d'inclinaison plus petit, lors d'une venue en butée contre la seconde surface de butée (29).
  12. Machine à pistons axiaux selon l'une des revendications 6 à 11,
    caractérisée par le fait que le point d'attaque, auquel le ou chaque piston amortisseur (40a ; 40b) vient respectivement en prise avec le disque incliné (25), est décalé, par rapport à l'axe (12) du bloc-cylindres, de façon telle que la force résultante, composée de la force (FDR) appliquée au disque incliné (25) par le piston amortisseur (40a ; 40b), de la force (FV) appliquée au disque incliné (25) par le dispositif de pivotement (31) au cours du processus de pivotement, et de la force (FKL) appliquée au disque incliné (25) par les pistons (5, 6), agisse sur un centre de gravité (S) situé sur ledit axe (12) du bloc-cylindres.
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 EP0953111A1 (fr) 1999-11-03
EP0953111B1 true 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)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008034337B4 (de) * 2007-09-12 2010-12-02 Sauer-Danfoss Inc. Auf Kugeln gelagerte Schwenkscheibe für Axialkolbenhydraulikmaschinen

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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
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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
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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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008034337B4 (de) * 2007-09-12 2010-12-02 Sauer-Danfoss Inc. Auf Kugeln gelagerte Schwenkscheibe für Axialkolbenhydraulikmaschinen

Also Published As

Publication number Publication date
DE59705927D1 (de) 2002-01-31
US6174139B1 (en) 2001-01-16
JP2001503493A (ja) 2001-03-13
JP3956058B2 (ja) 2007-08-08
WO1998020258A1 (fr) 1998-05-14
DE19645580C1 (de) 1998-04-02
EP0953111A1 (fr) 1999-11-03

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