EP2496843B1 - Ensemble de commande hydraulique présentant une chute de pression régulatrice pouvant être modifiée par l'intermédiaire d'une soupape de détection de charge - Google Patents

Ensemble de commande hydraulique présentant une chute de pression régulatrice pouvant être modifiée par l'intermédiaire d'une soupape de détection de charge Download PDF

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Publication number
EP2496843B1
EP2496843B1 EP10752313.6A EP10752313A EP2496843B1 EP 2496843 B1 EP2496843 B1 EP 2496843B1 EP 10752313 A EP10752313 A EP 10752313A EP 2496843 B1 EP2496843 B1 EP 2496843B1
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EP
European Patent Office
Prior art keywords
pressure
switching valve
control
line
valve
Prior art date
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Not-in-force
Application number
EP10752313.6A
Other languages
German (de)
English (en)
Other versions
EP2496843A1 (fr
Inventor
Rolf Siegenführ
Wolfgang KÖTTER
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2496843A1 publication Critical patent/EP2496843A1/fr
Application granted granted Critical
Publication of EP2496843B1 publication Critical patent/EP2496843B1/fr
Not-in-force legal-status Critical Current
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves

Definitions

  • the present invention relates to a hydraulic control arrangement with variable control pressure gradient according to the preamble of patent claim 1.
  • a control or valve block of a constant or controllable pump is connected downstream, which includes a pressure compensator and a preferably adjustable pressure relief valve.
  • a control block of a known control arrangement is in the appended Fig. 2 shown.
  • control block of a generic control arrangement has a 2/2-way proportional valve whose input port is connected to the pump and whose output port is connected to a hydraulic tank.
  • One control side of the proportional directional valve is acted upon by the pump pressure and the other control side is acted upon by two series-connected throttles with the load pressure of a consumer and a biasing spring.
  • This structure forms a pressure compensator whose pre-tensioning spring determines a pressure gradient or pressure difference between the pump pressure and the load pressure, which is kept constant by the pressure compensator.
  • the biasing spring opposite control side of the pressure compensator is connected via a throttle to the pump pressure line, in parallel with a built-in pressure compensator 2/2 switching valve is arranged, which can connect the pump pressure line to the control line.
  • the 2/2-way valve blocks the connection line between the pump line and the control line, so that the pump spring pressure is applied to the control side of the pressure compensator opposite the pretension spring.
  • a neutral circulation pressure corresponding to the control force of the biasing spring is established.
  • control pressure in the control line increases, whereby the 2/2-way valve opens and a corresponding control pressure acts in addition to the biasing spring on the pressure compensator.
  • the pump pressure rises to a correspondingly higher pressure value, which is held by the pressure compensator.
  • the essence of the invention is therefore to equip the hydraulic control assembly with an inlet pressure compensator consisting of a proportional directional control valve whose one control side is acted upon by a throttled load load and a biasing spring and the other control side with a throttled pump pressure, wherein a hydraulically controlled switching valve is provided to the selected throttled connection of the two control sides of the proportional directional control valve.
  • this basic structure corresponds to that in the FIG. 3 shown known control arrangement.
  • a further preferably electromagnetic switching valve is now arranged which selectively opens a bypass line to the hydraulically actuated switching valve to force-connect a throttled bypass connection between the two control sides of the proportional directional control valve.
  • This further switching valve is selectively actuated in order to start the preselected in neutral circulation low pressure gradient (only dependent on the biasing spring) to a predeterminable value (corresponding to the throttle setting in the bypass line), which allows a start of a further consumption via the (external) control block.
  • a preferably adjustable throttle in the bypass line is connected directly upstream of the electromagnetic switching valve.
  • This throttle may thus have a different setting than the hydraulically actuated switching valve immediately upstream throttle, so that upon activation of the electromagnetic switching valve, a neutral circulation pressure differential is different from the pressure drop in the consumer operation with non-activated electromagnetic switching valve.
  • a number of hydraulically operated 2-position / 3-way switching valves are serially interposed in a connecting line between the electromagnetic switching valve and the pressure balance, whose output terminal in each case with the one input terminal of each connected downstream of the switching valve whose other input terminal is connected via a respective branch line to the pump-pressure-loaded control side of the pressure compensator and whose respective control side is connected to the consumer pressure line of the respective associated control block.
  • it is preferably provided to connect a further preferably adjustable throttle in each branch line to the respective hydraulically actuated switching valve.
  • the control arrangement is integrated according to a preferred embodiment of the invention in an internal control block and has a pressure compensating 2-way / 2-position proportional directional control valve 1, at its input terminal a pump 2 is connected and the output terminal leads to a pressure medium tank 4.
  • the one control side x of the proportional directional valve 1 is connected to the pump 2 via a second throttle D2.
  • the other control side y of the proportional directional valve 1 is spring-loaded and connected via a first throttle D1 with a consumer pressure main line 6. From this consumer pressure main 6 is a pressure relief line 8 into the tank 4, in which a preferably adjustable pressure relief valve 10 is interposed.
  • Each of the manually operated switching valves 12 has a consumer pressure port, which is connected via an internal consumer pressure branch line 14 to the consumer pressure main line 6 upstream of the throttle D1, and a consumer pressure expansion port, which is connected to the pressure medium tank 4.
  • the two control sides x, y of the pressure compensator forming proportional directional control valve 1 are hydraulically connected to each other via a short line 16, in which a hydraulically controlled switching valve ZV1, in the present case a 2/2-switching valve is interposed, whose one control side is spring-biased and the other control side of the pressure is acted upon by the spring-biased control side of the proportional directional valve 1.
  • This hydraulically controlled switching valve ZV1 is a preferably adjustable throttle / aperture D3 immediately upstream.
  • the component combination consisting of the hydraulically controlled switching valve ZV1 and the immediately upstream throttle D3 is provided with a bypass line 18 bypassing this, the upstream of the throttle D3 branches off from the short-circuit line 16 and downstream to the hydraulically controlled switching valve ZV1 back in the short-circuit line 16 opens.
  • an electromagnetic 3-way / 2-position switching valve ZVA is interposed, a preferably adjustable throttle / aperture DA is connected immediately upstream.
  • This throttle DA is / can be set differently to the throttle D3.
  • the electromagnetic switching valve ZVA connects in a first switching position (preferably not activated), the hydraulically controlled switching valve ZV1 with the spring-biased control side of the pressure compensator 1.
  • a second switching position blocks the electromagnetic switching valve ZVA the hydraulically controlled switching valve ZV1 and instead connects the Short-circuit line 16 via the throttle DA with the spring-loaded control side of the pressure compensator 1.
  • each external control block 20, 22 is connected via a pump line 24 directly to the pump 2 and further has an external consumer pressure branch line 26, 28, which opens via an external shuttle valve 30 in the consumer pressure main line 6.
  • Each external control block 20, 22 is an external hydraulically controlled 3-way / 2-position switching valve ZV2, ZV3 assigned and connected in series in the short-circuit line 16 to the electromagnetic switching valve ZVA.
  • the hydraulically actuated switching valve ZV2 assigned to the first external control block 20 is immediately downstream of the electromagnetic switching valve ZVA, wherein one of its input terminals is connected to the output terminal of the electromagnetic switching valve ZVA and its second input terminal is connected via an immediately upstream, preferably adjustable Throttle D4 with the short-circuit line 16 upstream is connected to the throttle D3 (ie directly with the pump-pressure-loaded control side of the pressure compensator 1).
  • the external hydraulically-operated switching valve ZV3 associated with the second external control block 22 is immediately connected in the short-circuit line 16 to the external hydraulically operated switching valve ZV2 of the first external control block 20, and its one input port is connected to the output port of the external hydraulically-operated switching valve ZV2 of the first external control block 20 is and whose second input terminal is connected via an immediately upstream, preferably adjustable throttle D5 with the short-circuit line 16 upstream of the throttle D3 (ie directly with the pump pressure-loaded control side of the pressure compensator 1).
  • the one control side of both external hydraulically actuated switching valves ZV2, ZV3 is spring-biased, wherein the other control side in each case with the consumption pressure of the first, and the second external control block 20, 22 are acted upon.
  • the order of the serially arranged external hydraulically actuated switching valves ZV2, ZV3 is not arbitrary, but corresponds to the required pressure drop of the external control blocks 20, 22 in the consumer mode.
  • the hydraulically operated switching valve ZV2 of the first external pressure control block 20 is immediately downstream of the electromagnetic switching valve ZVA and is followed by the hydraulically operated switching valve Z3 of the second higher pressure differential control block 22 and so on.
  • the consumer pressure main line 6 is depressurized, since the control oil flow in the consumer pressure line 6 via the manually operable Switching valves 12 is relaxed in the pressure medium tank 4. Furthermore, the short-circuit line 16 between the two control sides x, y of the pressure compensator 1 is locked, since the interposed hydraulically controlled switching valve ZV1 is not activated in the absence of a consumer pressure.
  • the control pressure gradient depends solely on the spring force of the biasing spring on the pressure compensator 1, which is set according to the selection of the spring force to a low value.
  • Fig. 1 is closed by activating the solenoid valve ZVA, the short-circuit line 16, whereby a control oil flow from the pump 2 via a series circuit of the restrictors (orifices) D2 and DA and the pump-pressure-loaded control side x of the pressure compensator 1 to the spring-biased control side y flows.
  • the pressurization of the spring-biased control side y of the pressure compensator 1 can be changed so that the desired control pressure increase over the standard neutral circulation described above is achieved.
  • the required higher control pressure signal is selected at the shuttle valve WSV-EX and passed to the pressure compensator 1 (at the spring-biased control side y).
  • the hydraulically actuated switching valve ZV3 switches by the supplied consumer pressure from the external second control block 22 and thus activates the diaphragm row D2 and D5.
  • a suitable diaphragm variation at the diaphragm D5 the even higher control pressure gradient for the external second control block 22 can be set.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (8)

  1. Dispositif de commande hydraulique comportant une balance de pression d'entrée constituée d'une valve de distribution proportionnelle (1), dont un côté de commande (y) est sollicité par une pression de charge d'appareil consommateur ainsi qu'un ressort de précontrainte et dont l'autre côté de commande (x) est sollicité par une pression de pompage réduite, et d'une soupape de commutation (ZV1) commandée hydrauliquement afin de relier de manière sélectionnée et réduite les deux côtés de commande (x,y) de la valve de distribution proportionnelle (1), caractérisé par une soupape de commutation (ZVA) électromagnétique, qui offre au choix une conduite de dérivation (18) vers la soupape de commutation (ZV1) actionnée hydrauliquement, afin de raccorder par contrainte une liaison de dérivation réduite entre les deux côtés de commande (x,y) de la valve de distribution proportionnelle (1).
  2. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que la soupape de commutation électromagnétique (ZVA) est une soupape de commutation à 3 voies/ 2 positions comportant un raccord de sortie, qui est relié au côté de commande (y) précontraint par ressort de la valve de distribution proportionnelle (1), un premier raccord d'entrée, qui est relié à la soupape de commutation (ZV1) actionné hydrauliquement et un deuxième raccord d'entrée, qui est relié par l'intermédiaire de la conduite de dérivation (18) au côté de commande (x) sollicité par la pression de pompage réduite de la valve de distribution proportionnelle (1), dans lequel la soupape de commutation électromagnétique (ZVA) relie au choix ses raccords d'entrée à son raccord de sortie respectif.
  3. Dispositif de commande hydraulique selon une des revendications précédentes, caractérisé en ce que un étranglement (DA) de préférence ajustable dans la conduite de dérivation (18) est raccordé en amont de la soupape de commutation électromagnétique (ZVA).
  4. Dispositif de commande hydraulique selon une des revendications précédentes, caractérisé en ce que un étranglement (D3) de préférence ajustable est raccordé en amont de la soupape de commutation (ZV1) actionnée hydrauliquement dans une portion de conduite contournée par la conduite de dérivation (18).
  5. Dispositif de commande hydraulique selon une des revendications précédentes, caractérisé par une pluralité d'appareils consommateurs, qui peuvent être respectivement actionnés par l'intermédiaire d'un bloc de commande externe (20,22), qui sont raccordés respectivement à une conduite de pression de pompage (24) ainsi qu'à une conduite de pression d'appareil consommateur (26,28) menant à la balance de pression (1) par l'intermédiaire d'une soupape interchangeable (30).
  6. Dispositif de commande hydraulique selon la revendication 5, caractérisé en ce que correspondant à la pluralité de blocs de commande externes (20,22) une pluralité de soupapes de commutation à 3 voies/2 positions (ZV2,ZV3) sont intercalées sériellement dans une conduite de court-circuit (16) entre la soupape de commutation électromagnétique (ZVA) et la balance de pression (1), dont le raccord de sortie est respectivement relié à un des raccords d'entrée de la soupape de commutation successive, dont l'autre raccord d'entrée est raccordé par l'intermédiaire d'un embranchement externe respectif au côté de commande (x) sollicité par une pression de pompage réduite de la balance de pression (1)et dont respectivement un côté de commande est raccordé à la conduite de pression d'appareil consommateur (26,28) du bloc de commande (20,22) respectivement coordonné.
  7. Dispositif de commande hydraulique selon la revendication 6, caractérisé en ce que dans chaque embranchement externe, un étranglement (D4,D5) de préférence ajustable est raccordé en amont de la soupape de commutation (ZV2,ZV3) respective actionnée hydrauliquement.
  8. Dispositif de commande hydraulique selon une des revendications précédentes, caractérisé en ce que la balance de pression (1) est intégrée dans un bloc de commande interne, dans lequel une pluralité de soupapes de commutation (12) actionnables manuellement sont disposées en vue de l'activation d'appareils consommateurs internes, dans lequel à partir de chaque soupape de commutation (12) actionnable manuellement, une conduite de pression d'appareil consommateur (14) mène au côté de commande précontraint par ressort (y) de la balance de pression (1), auquel un étranglement (D1) est raccordé en amont directement dans la conduite d'appareil consommateur.
EP10752313.6A 2009-11-05 2010-09-06 Ensemble de commande hydraulique présentant une chute de pression régulatrice pouvant être modifiée par l'intermédiaire d'une soupape de détection de charge Not-in-force EP2496843B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910052077 DE102009052077A1 (de) 2009-11-05 2009-11-05 Hydraulische Steueranordnung mit über ein LS-Ventil veränderbarem Regeldruckgefälle
PCT/EP2010/005460 WO2011054408A1 (fr) 2009-11-05 2010-09-06 Ensemble de commande hydraulique présentant une chute de pression régulatrice pouvant être modifiée par l'intermédiaire d'une soupape de détection de charge

Publications (2)

Publication Number Publication Date
EP2496843A1 EP2496843A1 (fr) 2012-09-12
EP2496843B1 true EP2496843B1 (fr) 2013-11-06

Family

ID=43242607

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10752313.6A Not-in-force EP2496843B1 (fr) 2009-11-05 2010-09-06 Ensemble de commande hydraulique présentant une chute de pression régulatrice pouvant être modifiée par l'intermédiaire d'une soupape de détection de charge

Country Status (4)

Country Link
EP (1) EP2496843B1 (fr)
BR (1) BR112012010582A8 (fr)
DE (1) DE102009052077A1 (fr)
WO (1) WO2011054408A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015212556A1 (de) * 2015-07-06 2017-01-12 Robert Bosch Gmbh Steuervorrichtung mit Pumpendruckwaage und Vorsteuerdruckwaage

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE9300084L (sv) * 1993-01-14 1994-04-18 Voac Hydraulics Boraas Ab Förfarande för styrning av en hydraulmotor, jämte hydraulventil härför
DE10011936A1 (de) * 2000-03-11 2001-09-13 Bosch Gmbh Robert Hydraulische Steuereinrichtung
DE102004005606B3 (de) * 2004-02-05 2005-10-06 Hydac Fluidtechnik Gmbh Schaltungsanordnung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015212556A1 (de) * 2015-07-06 2017-01-12 Robert Bosch Gmbh Steuervorrichtung mit Pumpendruckwaage und Vorsteuerdruckwaage

Also Published As

Publication number Publication date
WO2011054408A1 (fr) 2011-05-12
BR112012010582A8 (pt) 2016-10-04
BR112012010582A2 (pt) 2016-03-22
EP2496843A1 (fr) 2012-09-12
DE102009052077A1 (de) 2011-05-12

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