EP1504191A1 - Dispositif de reglage pour des machines a piston hydrostatiques - Google Patents

Dispositif de reglage pour des machines a piston hydrostatiques

Info

Publication number
EP1504191A1
EP1504191A1 EP03727295A EP03727295A EP1504191A1 EP 1504191 A1 EP1504191 A1 EP 1504191A1 EP 03727295 A EP03727295 A EP 03727295A EP 03727295 A EP03727295 A EP 03727295A EP 1504191 A1 EP1504191 A1 EP 1504191A1
Authority
EP
European Patent Office
Prior art keywords
control
piston
leg
adjusting device
actuating
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
EP03727295A
Other languages
German (de)
English (en)
Other versions
EP1504191B1 (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
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=29413733&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1504191(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1504191A1 publication Critical patent/EP1504191A1/fr
Application granted granted Critical
Publication of EP1504191B1 publication Critical patent/EP1504191B1/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
    • 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 machines, in particular hydraulic motors of travel drives.
  • An adjusting device in which a pivoting angle of a hydrostatic piston machine can be set by means of an actuating piston movement, the actuating movement of the actuating piston being fed back to a control valve is known from DE 195 40 654 C1.
  • the feedback of the actuating movement of the actuating piston makes it possible to set a swivel angle that is proportional to a control variable.
  • An actuating pressure which is set by a control valve, acts on the two oppositely oriented piston surfaces of the actuating piston in the actuating pressure chamber. Depending on an axial position of a control piston, the two signal pressure chambers are acted upon by a corresponding signal pressure.
  • the control piston can be acted upon by a control pressure on its two end faces for deflection from its central position.
  • a force proportional to the deflections of the actuating piston from its central position can be fed back to the regulating piston via an adjusting lever and two legs coupled with a spring.
  • the feedback takes place in such a way that a force is exerted on the control piston which is directed against the control pressure present at one end of the control piston.
  • a disadvantage of the adjusting device described is that when the actuating piston travels from one end position to the other end position, the middle position must be passed, in which case the feedback is transferred from one leg to the other leg. Since a play-free execution of the Lever, the two legs and the corresponding driver is not possible, this inevitably leads to an inharmonic swivel angle adjustment.
  • the control piston is in a certain end position in the rest position of the adjusting device according to claim 1, while the control piston of the control valve is in its neutral position. In this rest position, the control piston is free of forces. Since deflection of the actuating piston from its end position is only possible in one direction, only a regulating force which is oriented in one direction is generated over the entire travel path up to its second end position. The lack of a change of direction of the control force on the control piston prevents the inharmonic swivel angle adjustment in the area of the central position.
  • the return force can also be non-zero in the central rest position of the adjusting device.
  • the control piston is not in its neutral position in the central rest position if no control force is transmitted to the control piston.
  • Figure 1 is a schematic representation of a first embodiment of the adjusting device according to the invention in the rest position.
  • Figure 2 is a schematic representation of the first embodiment of the adjusting device according to the invention in its second end position.
  • Fig. 3 shows a second embodiment of the adjusting device according to the invention in
  • Fig. 4 is a partial section along the line A-A of Fig. 1;
  • Fig. 5 is an enlarged view in section V of the
  • FIG. 1 shows a first exemplary embodiment of an adjusting device 1 according to the invention.
  • an actuating piston 2 in an actuating pressure chamber 3 and a second actuating pressure chamber 4 is acted upon by an actuating 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, to which a resulting force acts when there is a pressure difference.
  • a control pressure control valve 5 is provided for setting the pressure difference in the two control pressure chambers 3 and 4.
  • the control pressure control valve 5 has a control piston 6, which is arranged axially displaceably in a bore in a housing 7.
  • first feed pressure bore 8 and a second feed pressure bore 9 are made in the housing 7.
  • the first feed pressure bore 8 and the second feed pressure bore 9 are connected to a feed pressure line 14, which can be connected to an auxiliary pressure source, for example.
  • the feed pressure line 14 or the first feed pressure bore 8 or the second feed pressure bore 9 is provided with a first signal pressure line 12 or a second signal pressure line
  • the first signal pressure line 12 is connected to a first signal pressure channel 10, which opens into a first groove 15 on the part of the control piston 6.
  • the second signal pressure line 13 is connected to a second groove 16 via a second signal pressure channel 11.
  • the control piston 6 has a first control piston section 17 or a second control piston section 18.
  • the two control piston sections 17 and 18 have a first signal 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 and 18, respectively.
  • the first signal pressure channel 10 is thus connected via the first groove 15 to a first feed pressure groove 21 and thus the first
  • the second actuating pressure channel 11 is connected via the second groove 16 to 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 of the first control piston section 17 facing away from the first signal pressure control edge 19. Likewise on that second control piston section 18, a second relaxation control edge 24 is arranged. Depending on the axial position of the regulating piston 6, the respective actuating pressure chamber 3 or 4 is expanded into a tank volume 25 via the first relief 15 and the second groove 16 via the two expansion control edges 23 and 24.
  • the rear control piston chambers 27 and 27 ' are also connected to the tank volume 25 via the volume compensation channels 26 and 26'.
  • the slight volume fluctuations that arise in the rear control piston chambers 27 and 27 'due to an axial movement of the control piston 6 are thus compensated.
  • part of the control piston leakage is discharged into the tank volume 25 via the volume compensation channels 26 and 26 '.
  • a proportional magnet 28 is provided, which is arranged on the housing 7 of the control valve 5.
  • the proportional magnet 28 has a plunger 29, the plunger 29 acting on an end face 30 of the control piston 6.
  • a control force can be transmitted in the axial direction to the control piston 6, which is generated by the proportional magnet 28 as a function of a control signal that 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.
  • the axial movement of the control piston 6 on the first signal pressure control edge 19 creates a flow-through gap.
  • the pressure medium supplied via the feed pressure line 14 and the first feed pressure bore 8 can reach the first signal pressure chamber 3 via the first signal pressure channel 10.
  • the pressure thus increased in the first actuating pressure chamber 3 effects an adjustment of the actuating piston 2 against the force of a return spring 40 in the direction of its second end position.
  • This return force is 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 contact pin 39 moves the control piston 6 against the control force generated by the proportional magnet 28 until a balance of forces from the return force and the control force is reached.
  • the control piston 6 is again in its neutral position, in which the throttles formed on the steep pressure control edges 19 and 20 are closed.
  • the deflecting control signal which is supplied to the proportional magnet 28 via the electrical connection 41, is withdrawn.
  • the control piston 6 is no longer in the equilibrium of forces and is deflected to the right by the predominant return force in the illustration in FIG. 2.
  • a flow-through gap is now generated at the second actuating pressure control edge 20 and correspondingly at the first expansion control edge 23 of the first control piston section 17, a flow-through gap as well.
  • control piston 2 By selecting the rest position of the control piston 2 in its first end position when the control force disappears, a control force is generated on the control piston 6 over the entire control range or the control range of the control piston 2, which force acts in one direction.
  • the control piston 6 is free of a control force only when the control piston 2 is in its first end position. A transfer and an associated change in direction of the force between the two legs 35 and 36 is not necessary, 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.
  • FIG. 3 shows a second exemplary embodiment of the adjustment device according to the invention.
  • a compression spring 42 is shown here, the compression spring 42 being supported between a first spring bearing 43 and a second spring bearing 44.
  • the second spring bearing 44 is part of a sleeve which is slidably arranged 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 with the sliding cylinder 45 via a 9
  • Holding pin 46 connected.
  • slots not shown, are provided, in which the split pin 46 can carry out a longitudinal displacement, so that the first spring bearing 44 can be moved longitudinally on the outside of the sleeve.
  • the sliding cylinder 45 is also rotatably mounted in an eye 49 of the first leg 35. A relative deflection of the second leg 36 to the first leg 35 thus leads to a compression of the compression spring 42.
  • the function of such an arrangement differs from the mode of operation explained in relation to FIG. 2 only in that the return force is generated by compression of the compression spring 42 ,
  • a control pressure connection 47 is provided instead of the proportional magnet 28.
  • a control force is applied to the end face 30 of the control piston 6 via the control pressure connection 47, the control force being generated in a known manner, for example from an auxiliary pressure source.
  • FIG. 4 shows a partial section along the line AA of FIG. 1.
  • 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 several stages and is fixed in the housing 7 in a first and a second bore 48 and 49.
  • the driving pin 38 is arranged in a bore.
  • the contact pin 39 is also arranged in a bore.
  • the driving pin 38 and the contact pin 39 are fixed in their bores with an interference fit.
  • the driving pin 38 acts on the second leg 36, while the contact pin 39 acts on the first leg 35, which is shown in FIG.
  • FIG. 5 shows an enlarged view in section V of FIG. 1.
  • the detail shows part of the first leg 35 and of the control piston 6 with the contact pin 39 arranged therein.
  • the first leg 35 has a flattened portion 50.
  • the flattened portion 50 is oriented such that the longitudinal axis of the control piston 6 forms a right angle with the flattened point 50. This prevents the introduction of the return force on the control piston 6 from its central axis and thus its direction of movement.
  • the illustrated right-angled arrangement between the flattened point 50 and the axis of the control piston 6 only applies exactly in the rest position of the adjusting device 1, in which the control piston is in its neutral position and the control piston 2 is in its first end position. However, the adjustment paths of the control piston 6 are small, so that approximately the right angle is maintained.
  • the return force in the then central rest position of the adjusting device 1 can also be non-zero, even if the feed pressure p sp is equal to zero.
  • the central rest position is then ensured by two compression springs 40 arranged on one side of the control piston 2, as in DE 195 40 654 Cl.
  • the control piston 6 is not in its neutral position in the central rest position if no control force is transmitted to the control piston 6 by the proportional magnet 28 or by the control pressure p s teu e r.

Landscapes

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

Abstract

L'invention concerne un dispositif de réglage destiné à des machines à piston hydrostatiques et comprenant un piston de réglage (2) déplaçable entre deux positions finales et pouvant être sollicité par des pressions de réglage agissant sur lui en sens inverse. Une soupape de pression de réglage (5) sert à réguler les pressions de réglage et comprend un piston de régulation (6) qui peut être déplacé hors d'une position neutre et qui est sollicité par une force de régulation dépendante de la position du piston de réglage (2). La force de régulation est dirigée contre une force de commande appliquée au piston de régulation (6) et est égale à zéro dans une position de repos du dispositif de réglage (1). Dans la position de repos du dispositif de réglage (1), le piston de régulation (6) se trouve dans sa position neutre et le piston de réglage (2) dans une position finale définie.
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 true EP1504191A1 (fr) 2005-02-09
EP1504191B1 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
DE102004033376B3 (de) * 2004-07-09 2005-12-01 Sauer-Danfoss (Neumünster) GmbH & Co OHG Axialkolbenmaschine mit einer Einrichtung zur elektrisch proportionalen Verstellung des Fördervolumens
DE102004033314B3 (de) * 2004-07-09 2005-12-08 Sauer-Danfoss (Neumünster) GmbH & Co OHG Axialkolbenmaschine mit einer Einrichtung zur elektrisch proportionalen Verstellung ihres 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
WO2019035891A1 (fr) 2017-08-18 2019-02-21 Eaton Intelligent Power Limited 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
DE102020211284A1 (de) * 2020-02-13 2021-08-19 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise
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

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
DE2146586C3 (de) * 1971-09-17 1981-12-17 G.L. Rexroth Gmbh, 8770 Lohr Mit einer Konstantzug-Regelung versehener hydrostatischer Antrieb
DE2823559A1 (de) * 1978-05-30 1979-12-06 Linde Ag Steuer- und regeleinrichtung fuer ein hydrostatisches getriebe
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
DE3404534A1 (de) 1984-02-09 1985-09-05 Mannesmann Rexroth GmbH, 8770 Lohr Hydraulische antriebsanordnung
DE3539220A1 (de) * 1985-11-05 1987-05-21 Hydromatik Gmbh Steuereinrichtung fuer ein hydrostatisches getriebe
US4722186A (en) * 1986-01-24 1988-02-02 Sundstrand Corporation Dual pressure displacement control system
US5160245A (en) * 1991-05-01 1992-11-03 Sauer, Inc. Displacement control feedback apparatus and method
DE19540654C1 (de) * 1995-10-31 1996-12-19 Brueninghaus Hydromatik Gmbh Verstellvorrichtung mit hydraulischer Zentriereinrichtung
DE19842029B4 (de) 1998-09-14 2005-02-17 Sauer-Sundstrand Gmbh & Co. Verstellung von hydrostatischen Axialkolbenmaschinen mittels Schrittmotor

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See references of WO03095831A1 *

Also Published As

Publication number Publication date
EP1504191B1 (fr) 2009-06-24
DE10220889B3 (de) 2004-02-12
US7171887B2 (en) 2007-02-06
DE50311633D1 (de) 2009-08-06
WO2003095831A9 (fr) 2004-10-21
DE10220889C5 (de) 2009-05-28
US20050252369A1 (en) 2005-11-17
WO2003095831A1 (fr) 2003-11-20

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