EP1504191B1 - Dispositif de reglage pour des machines a piston hydrostatiques - Google Patents

Dispositif de reglage pour des machines a piston hydrostatiques Download PDF

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Publication number
EP1504191B1
EP1504191B1 EP03727295A EP03727295A EP1504191B1 EP 1504191 B1 EP1504191 B1 EP 1504191B1 EP 03727295 A EP03727295 A EP 03727295A EP 03727295 A EP03727295 A EP 03727295A EP 1504191 B1 EP1504191 B1 EP 1504191B1
Authority
EP
European Patent Office
Prior art keywords
piston
leg
adjusting device
control
setting
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
EP03727295A
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German (de)
English (en)
Other versions
EP1504191A1 (fr
Inventor
Winfried Lilla
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
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Brueninghaus Hydromatik GmbH
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Publication date
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Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1504191A1 publication Critical patent/EP1504191A1/fr
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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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery

Definitions

  • the invention relates to an adjusting device for hydrostatic piston engines, in particular hydraulic motors of traction drives.
  • An adjusting device in which can be adjusted by a control piston movement, a pivot angle of a hydrostatic piston engine, wherein the actuating movement of the actuating piston is fed back to a control valve is from the DE 195 40 654 C1 known.
  • On the two oppositely oriented piston surfaces of the actuating piston acts in the control pressure chamber in each case a control pressure which is adjusted by a control valve.
  • the two control pressure chambers are acted upon by a corresponding control pressure.
  • the control piston is acted upon for deflection from its central position at its two end faces in each case with a control pressure.
  • the adjusting piston in a certain end position, while the control piston of the control valve is in its neutral position.
  • the control piston In this rest position, the control piston is free of forces. Since a deflection of the actuating piston from its end position is possible only in one direction, only a control force is generated on the control piston over the entire travel path up to its second end position, which is oriented in one direction. Due to the omitted change of direction of the control force on the control piston, the inharmonic pivot angle adjustment is prevented in the region of the central position.
  • the return force may not be equal to zero.
  • the control piston in the central rest position of the adjusting device, the return force may not be equal to zero.
  • a first embodiment of an adjusting device 1 is shown.
  • a control piston 2 is acted upon in a control pressure chamber 3 and a second control pressure chamber 4 with a control pressure.
  • the actuating pressures acting in the first and second actuating pressure chambers 3 and 4 act on the oppositely oriented piston surfaces of the actuating piston 2, at which a resultant force acts on a pressure difference.
  • a control pressure control valve 5 is provided.
  • the control pressure control valve 5 has a control piston 6 which is arranged axially displaceably in a bore of a housing 7.
  • a first feed pressure bore 8 and a second feed pressure bore 9 are introduced into the housing 7.
  • the first feed pressure bore 8 and second feed pressure bore 9 are connected to a feed pressure line 14, which may be connected, for example, to an auxiliary pressure source.
  • the feed pressure line 14 and the first feed pressure bore 8 or the second feed pressure bore 9 with a first actuating pressure line 12 or a second actuating pressure line 13 connectable.
  • the first actuating pressure line 12 is connected to a first actuating pressure channel 10, which opens on the part of the control piston 6 in a first groove 15.
  • the second actuating pressure line 13 is connected via a second actuating pressure channel 11 with a second groove 16.
  • the control piston 6 has a first control piston section 17 and a second control piston section 18, respectively.
  • the two control piston sections 17 and 18 respectively have a first control pressure control edge 19 and a second control pressure control edge 20, which are arranged at the oppositely oriented ends of the respective control piston section 17 or 18.
  • the first control pressure control edge 19 and the second control pressure control edge 20 form with the respective first groove 15 and second groove 16 a variable depending on the axial position of the control piston 6 throttle point.
  • the first actuating pressure channel 10 is connected via the first groove 15 with a first feed pressure 21 and thus the first actuating pressure chamber 3 is depressed with the pressure from the feed pressure line 14.
  • the second actuating pressure channel 11 is connected via the second groove 16 with a second feed pressure groove 22 when the control piston 6 is deflected in the opposite direction.
  • a first expansion control edge 23 is arranged on the side remote from the first control pressure control edge 19 side of the first control piston portion 17.
  • a second expansion control edge 24 is arranged at the second control piston portion 18 .
  • the respective control pressure chamber 3 or 4 is expanded via the two expansion control edges 23 and 24 via the first groove 15 and the second groove 16 into a tank volume 25.
  • the rear control piston chambers 27 and 27' are Also connected to the tank volume 25 via the volume equalization channels 26 and 26 ', the rear control piston chambers 27 and 27'.
  • the slight volume fluctuations that arise in the rear control piston chambers 27 and 27 'by an axial movement of the control piston 6 are thus compensated.
  • a proportional solenoid 28 is provided, which is arranged on the housing 7 of the control valve 5.
  • the proportional magnet 28 has a plunger 29, wherein the plunger 29 acts on an end face 30 of the control piston 6.
  • a control force can be transmitted to the control piston 6 in the axial direction, which is generated by the proportional magnet 28 in response to a control signal which is supplied to the proportional magnet 28 via an electrical connection 41. If the proportional magnet 28 is supplied with such a control signal via the electrical connection 41, it generates a force which displaces the control piston 6. In this case, a flow-through gap is generated by the axial movement of the control piston 6 at the first control pressure control edge 19.
  • the pressure medium supplied via the feed pressure line 14 and the first feed pressure bore 8 can reach the first setting pressure chamber 3 via the first setting pressure passage 10.
  • the thus increased pressure in the first actuating pressure chamber 3 causes an adjustment of the actuating piston 2 against the force of a return spring 40 in the direction of its second end position.
  • the throttle point of the second discharge control edge 24 is opened in the second control piston section 18.
  • the second control pressure chamber 4 is expanded via the second control pressure line 13 and the second control pressure channel 11 in the tank volume 25.
  • a Mit supportiveausnaturalung 33 is provided in the adjusting piston 2, in which a driving head 32 is arranged, which is connected to the adjusting lever 31.
  • the adjusting lever 31 is rotatably mounted on a bearing pin 34, so that the adjusting movement of the actuating piston 2 leads to a rotation of the actuating lever 31.
  • Also rotatably mounted on the bearing pin 34 are a first leg 35 and a second leg 36.
  • the first leg 35 and the second leg 36 are connected via a tension spring 37 with each other, so that a deflection of one of the two legs relative to the other to a voltage the tension spring 37 leads.
  • a driving pin 38 is arranged at the opposite end to the driving head 32 of the actuating lever 31 end of the actuating lever 31.
  • the driving pin 38 moves in opposite directions to the actuating piston movement.
  • the driving pin 38 abuts against the second leg 36, so that the second leg 36 is deflected relative to the first leg 35 by the rotational movement of the actuating lever 31 and the spring 37 is tensioned.
  • Fig. 2 the adjusting piston 2 is shown in its second end position, wherein, as described, the second leg 36 is deflected relative to the first leg 35, so that the tension spring 37 is maximally tensioned. Due to the tension of the tension spring is on the first leg 35 a Force generated with which the first leg 35 of the movement of the second leg 36 tries to follow. However, the first leg 35 is in abutment with a contact pin 39, which is arranged on the control piston 6. Thereby, the force of the tension spring 37 is transmitted from the first leg 35 to the abutment pin 39 and the control piston 6 experiences a return force, which is opposite to the control force of the proportional magnet 28.
  • This return force is the greater, the further the actuating piston 2 is deflected in the direction of its second end position.
  • the return force transmitted from the first leg 35 to the control piston 6 by means of the abutment pin 39 moves the control piston 6 counter to the control force generated by the proportional magnet 28 until an equilibrium of forces from the return force and the control force is achieved.
  • the control piston 6 is again in its neutral position, in which the throttles formed on the control pressure control edges 19 and 20 are closed.
  • the deflecting control signal which is supplied via the electrical connection 41 to the proportional magnet 28, withdrawn.
  • the control piston 6 is no longer in the balance of power and is characterized by the overwhelming return force in the representation of Fig. 2 deflected to the right.
  • a flow-through gap is now generated at the second control pressure control edge 20 and correspondingly at the first expansion control edge 23 of the first control piston section 17, a gap also through which can flow.
  • the second control pressure chamber 4 is depressed with the pressure medium from the feed pressure line 14, the first control pressure chamber 3, however, relaxed.
  • the adjusting piston 2 follows the changed pressure ratio and moves in the direction of its first end position.
  • a control force is generated on the control piston 6, which acts in one direction. Free of a control force is the control piston 6 only when the actuator piston 2 is in its first end position. A transfer and an associated change of direction of the force between the two legs 35 and 36 is not required, so that the control characteristic is harmonious.
  • the control force proportional to the deflection of the actuating piston 2 likewise generates an actuating piston movement 2, which is proportional to the control signal applied to the proportional magnet 28.
  • a second embodiment of the adjusting device according to the invention is shown.
  • an exercise with a compression spring 42 wherein the compression spring 42 between a first spring bearing 43 and a second spring bearing 44 is supported.
  • the second spring bearing 44 is part of a sleeve which is arranged displaceably on a sliding cylinder 45.
  • the spring bearing 44 is rotatably connected to the second leg 36 in an eye 48 of the leg 36.
  • the first spring bearing 43 is connected to the sliding cylinder 45 via a Retaining pin 46 connected.
  • a control pressure port 47 is provided. Via the control pressure port 47, a control force is applied to the end face 30 of the control piston 6, wherein the control force is generated in a known manner, for example from an auxiliary pressure source.
  • Fig. 4 is a partial section along the line AA the Fig. 1 shown.
  • the adjusting lever 31, the leg 35 and the second leg 36 are rotatably mounted on a common bearing pin 34.
  • the bearing pin 34 is designed in multiple stages, and fixed in the housing 7 in a first and a second bore 48 and 49, respectively.
  • the driving pin 38 is arranged in a bore.
  • the investment pin 39 is also arranged in a bore.
  • the driving pin 38 and the contact pin 39 are fixed with a press fit in their holes. As already described, the driving pin 38 acts on the second leg 36, the contact pin 39, however, on the first leg 35, which in the Fig.
  • Fig. 5 is an enlarged view in the section V of Fig. 1 shown.
  • the section shows a part of the first leg 35 and of the control piston 6 with the abutment pin 39 arranged therein.
  • the first leg 35 has a flattening 50.
  • the flattening 50 is oriented so that the longitudinal axis of the control piston 6 with the flattened point 50 encloses a right angle. This prevents that the introduction of the return force to the control piston 6 deviates from the central axis and thus its direction of movement.
  • the return force in the then central rest position of the adjusting device 1 also be non-zero, even if the feed pressure p sp is equal to zero.
  • the central rest position is then by two arranged on each side of the control piston 2 compression springs 40 as in the DE 195 40 654 C1 guaranteed. In this case, the control piston 6 will not located in the central rest position to its neutral position when no control power is transmitted to the regulating piston 6 from the proportional solenoid 28 or by the control pressure p tax.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (14)

  1. Dispositif de réglage pour des machines à piston hydrostatiques avec un piston de réglage (2), qui est déplaçable entre deux positions d'extrémité et qui peut être chargé en pressions de réglage agissant d'une manière opposée sur celui-ci, et une vanne de régulation de pression de réglage (5) par laquelle les pressions de réglage sont réglables, où la vanne de régulation de pression de réglage (5) présente un piston de régulation (6) pouvant être dévié d'une position neutre qui est chargé par une force de rappel dépendant de la position du piston de réglage (2), qui est opposée à une force de commande s'appliquant au piston de régulation (6), où en position de repos du dispositif de réglage (1), la force de rappel est zéro,
    caractérisé en ce qu'
    en position de repos, le piston de régulation (6) se trouve dans sa position neutre et le piston de réglage (2) se trouve dans une position d'extrémité déterminée.
  2. Dispositif de réglage selon la revendication 1,
    caractérisé en ce que
    le piston de régulation (6) peut être chargé sur un côté par une force de commande.
  3. Dispositif de réglage pour des machines à piston hydrostatiques avec un piston de réglage (2) qui est déplaçable entre deux positions d'extrémité et qui peut être chargé en pressions de réglage agissant d'une manière opposée à celui-ci, et une vanne de régulation de pression de réglage (5) par laquelle les pressions de réglage peuvent être réglées, où la vanne de régulation de pression de réglage (5) présente un piston de régulation (6) pouvant être dévié d'une position neutre, qui est chargé en force de rappel dépendant de la position du piston de réglage (2), qui est opposée à une force de commande s'appliquant au piston de régulation (6), où en une position de repos médiane du dispositif de réglage (1), la force de rappel est différente de zéro,
    caractérisé en ce qu'
    en position de repos médiane, le piston de régulation (6) ne se trouve pas dans sa position neutre lorsqu'aucune force de commande n'est transmise au piston de régulation (6).
  4. Dispositif de réglage selon la revendication 2 ou 3, caractérisé en ce que
    pour la production de la force de commande, un aimant proportionnel (28) est prévu.
  5. Dispositif de réglage selon la revendication 3,
    caractérisé en ce que
    pour la production de la force de commande, une face frontale (30) du piston de régulation (6) peut être chargée par une pression de commande (psteuer).
  6. Dispositif de réglage selon l'une des revendications 1 à 5, caractérisé en ce que
    la force de rappel peut être transférée par une première branche (35) par une tige d'application (39) au piston de régulation (6).
  7. Dispositif de réglage selon la revendication 6,
    caractérisé en ce que
    la force de rappel est proportionnelle à la tension d'un ressort (37, 42), qui est disposé entre la première branche (35) et une deuxième branche (36) en liaison active par le ressort (37, 42) avec la première branche (35).
  8. Dispositif de réglage selon la revendication 7,
    caractérisé en ce que
    la deuxième branche (36) peut être déviée relativement à la première branche (35) et que la déviation dépend de la position du piston de réglage (2).
  9. Dispositif de réglage selon la revendication 8,
    caractérisé en ce que
    la deuxième branche (36) peut être déviée par une tige d'entraînement (38) disposée à un levier de réglage (31), et que le levier de réglage (31) est couplé en vue du recouplage de la position avec le piston de réglage (2).
  10. Dispositif de réglage selon la revendication 9,
    caractérisé en ce que
    la première branche (35), la deuxième branche (36) et le levier de réglage (31) présente un point de rotation commun (34).
  11. Dispositif de réglage selon l'une des revendications 7 à 10,
    caractérisé en ce que
    le ressort disposé entre la première et la deuxième branche (35, 36) est un ressort de traction (37).
  12. Dispositif de réglage selon l'une des revendications 7 à 10,
    caractérisé en ce que
    le ressort disposé entre la première et la deuxième branche (35, 36) est un ressort de pression (42) qui s'appuie sur deux paliers de ressort (43,44), où à chaque fois un palier de ressort (43,44) est relié à la première, respectivement la deuxième branche (35, 36), et
    en ce que le ressort de pression (42), lors d'une déviation de la deuxième branche (36) relativement à la première branche (35), s'oppose à la déviation.
  13. Dispositif de réglage selon l'une des revendications 6 à 12, caractérisé en ce que
    la première branche (35) présente une face d'application (50) pour la tige d'application (39), dont la normale de face, en position de repos du dispositif de réglage (1), est orientée parallèlement à la direction de mouvement de la tige d'application (39).
  14. Dispositif de réglage selon l'une des revendications 1 à 13, caractérisé en ce que
    le piston de réglage (2) pour chaque enceinte de pression de réglage (3,4) présente une section de piston de régulation (17,18) avec respectivement deux arêtes de commande (19, 23, 20, 24) par lesquelles l'enceinte de pression de réglage respective (3, 4) peut être reliée à une source de pression d'alimentation ou à un volume de réservoir (25).
EP03727295A 2002-05-10 2003-04-11 Dispositif de reglage pour des machines a piston hydrostatiques Expired - Lifetime EP1504191B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10220889 2002-05-10
DE10220889A DE10220889C5 (de) 2002-05-10 2002-05-10 Verstellvorrichtung für hydrostatische Kolbenmaschinen
PCT/EP2003/003793 WO2003095831A1 (fr) 2002-05-10 2003-04-11 Dispositif de reglage pour des machines a piston hydrostatiques

Publications (2)

Publication Number Publication Date
EP1504191A1 EP1504191A1 (fr) 2005-02-09
EP1504191B1 true EP1504191B1 (fr) 2009-06-24

Family

ID=29413733

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03727295A Expired - Lifetime EP1504191B1 (fr) 2002-05-10 2003-04-11 Dispositif de reglage pour des machines a piston hydrostatiques

Country Status (4)

Country Link
US (1) US7171887B2 (fr)
EP (1) EP1504191B1 (fr)
DE (2) DE10220889C5 (fr)
WO (1) WO2003095831A1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004033314B3 (de) * 2004-07-09 2005-12-08 Sauer-Danfoss (Neumünster) GmbH & Co OHG Axialkolbenmaschine mit einer Einrichtung zur elektrisch proportionalen Verstellung ihres Fördervolumens
DE102004033376B3 (de) * 2004-07-09 2005-12-01 Sauer-Danfoss (Neumünster) GmbH & Co OHG Axialkolbenmaschine mit einer Einrichtung zur elektrisch proportionalen Verstellung des Fördervolumens
DE102005059808B3 (de) * 2005-12-14 2007-06-14 Sauer-Danfoss Gmbh & Co Ohg Axialkolbenmaschine mit einer Verstelleinheit zur elektrisch proportionalen Verstellung des Fördervolumens
DE102008048507A1 (de) 2008-09-23 2010-03-25 Robert Bosch Gmbh Vorrichtung mit einstellbarer Spielfreiheit für ein Ansteuergerät
DE102009006288B4 (de) * 2009-01-27 2019-06-19 Robert Bosch Gmbh Verstellvorrichtung einer hydrostatischen Maschine
DE102010009975A1 (de) * 2010-03-03 2011-09-08 Sauer-Danfoss Gmbh & Co Ohg Verstellvorrichtung für Axialkolbenmaschinen
DE102011112215A1 (de) * 2011-09-02 2013-03-07 Robert Bosch Gmbh Spannhebelanordnung, Verfahren zum Herstellen eines Spannhebels und Ansteuergerät
JP5822141B2 (ja) * 2012-03-29 2015-11-24 Ｋｙｂ株式会社 サーボレギュレータ
DE102014203202A1 (de) 2014-02-24 2015-08-27 Robert Bosch Gmbh Einseitiges Ansteuergerät für eine verstellbare hydrostatische Verdrängermaschine
EP3669096B1 (fr) 2017-08-18 2022-10-19 Danfoss Power Solutions II Technology A/S Systèmes de commande pour machines hydrauliques à déplacement axial
EP3690229B8 (fr) 2019-01-31 2021-11-24 Danfoss Power Solutions II Technology A/S Commande de déplacement comportant un réglage du capteur d'angle
DE102020211288A1 (de) * 2020-02-13 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulisches Antriebssystem
IT202000005020A1 (it) * 2020-03-09 2021-09-09 Pmp Pro Mec S P A Pompa idraulica a cilindrata variabile
DE102022206422A1 (de) 2022-06-27 2023-12-28 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatischen Axialkolbenmaschine

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JPS60128999U (ja) * 1984-02-08 1985-08-29 株式会社小松製作所 可変液圧ポンプの容量制御装置
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Also Published As

Publication number Publication date
DE10220889C5 (de) 2009-05-28
US20050252369A1 (en) 2005-11-17
WO2003095831A9 (fr) 2004-10-21
EP1504191A1 (fr) 2005-02-09
DE10220889B3 (de) 2004-02-12
US7171887B2 (en) 2007-02-06
DE50311633D1 (de) 2009-08-06
WO2003095831A1 (fr) 2003-11-20

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