EP2188543A1 - Dispositif de commande electrohydraulique - Google Patents

Dispositif de commande electrohydraulique

Info

Publication number
EP2188543A1
EP2188543A1 EP08803982A EP08803982A EP2188543A1 EP 2188543 A1 EP2188543 A1 EP 2188543A1 EP 08803982 A EP08803982 A EP 08803982A EP 08803982 A EP08803982 A EP 08803982A EP 2188543 A1 EP2188543 A1 EP 2188543A1
Authority
EP
European Patent Office
Prior art keywords
pressure
line
control device
control
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP08803982A
Other languages
German (de)
English (en)
Inventor
Otto Ebner
Christoph RÜCHARDT
Reiner Keller
Martin Rossmann
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP2188543A1 publication Critical patent/EP2188543A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D29/00—Clutches and systems of clutches involving both fluid and magnetic actuation
    • F16D29/005—Clutches and systems of clutches involving both fluid and magnetic actuation with a fluid pressure piston driven by an electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/02—Control by fluid pressure
    • F16D48/0206—Control by fluid pressure in a system with a plurality of fluid-actuated clutches
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D48/00—External control of clutches
    • F16D48/06—Control by electric or electronic means, e.g. of fluid pressure
    • F16D48/066—Control of fluid pressure, e.g. using an accumulator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D2500/00—External control of clutches by electric or electronic means
    • F16D2500/30—Signal inputs
    • F16D2500/302—Signal inputs from the actuator
    • F16D2500/3026—Stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26—Generation or transmission of movements for final actuating mechanisms
    • F16H61/28—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/2807—Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted using electric control signals for shift actuators, e.g. electro-hydraulic control therefor

Definitions

  • the invention relates generally to an electro-hydraulic control device, comprising a pressure supply device for conveying a pressure medium from a reservoir into a main pressure line, wherein the promotion of the pressure medium via a drivable by a controllable electric motor pump element, and with an actuating device for actuating at least one hydraulic actuator, wherein the Actuation of the actuator via a producible by at least one control valve connection of at least one pressure chamber of the actuator to the main pressure line and / or is carried out with a pressure-free line.
  • an electrohydraulic control device of an automated step transmission comprising a pressure supply device for conveying a pressure medium from a reservoir into a main pressure line, wherein the promotion of the pressure medium via a pump element drivable by a controllable electric motor, and with an actuating device for actuating at least one hydraulic Kupplungsaktuators and / or a hydraulic Wählaktuators and / or a hydraulic Wegaktuators, wherein the actuation of the relevant actuator via a producible by at least one control valve connection of at least one pressure chamber of the actuator with the main pressure line and / or with a pressure-free line.
  • Electro-hydraulic control devices are preferably used in motor vehicles, for example for the actuation of clutches, brakes and transmissions; however, they may also be used in other technical equipment and installations.
  • electro-hydraulic control mecanicsvoriquesen particularly suitable, since they have in addition to compact dimensions and a high energy density generally good control properties, ie well metered actuating forces for engagement and disengagement of friction clutches and for synchronizing and loading and unloading of aisles.
  • the components used in electrohydraulic control devices such as control valves and actuating cylinders, are sufficiently tested and reliable due to many years of development and application practice.
  • the pressure supply device of an electrohydraulic control device typically has a hydraulic pump as the pumping element, by means of which a pressure medium (hydraulic oil) is conveyed via a check valve from a reservoir (oil sump) into the main pressure line which is under system pressure.
  • the hydraulic pump used is usually a piston pump with crank mechanism, an axial piston pump or a gear pump, which is preferably driven by an electric motor.
  • a pressure accumulator To the main pressure line of the pressure supply device usually a pressure accumulator, a pressure sensor and a pressure relief valve are connected.
  • Such a structure of the pressure supply device ensures that the hydraulic pump does not have to be driven permanently, but can be driven intermittently, ie as needed, whereby a higher overall efficiency of the control device is achieved. If, by means of the pressure sensor connected to the main pressure line, a drop in the system pressure prevailing in the main pressure line is determined below a lower first limit value, then the hydraulic pump is put into operation by switching on the electric motor and pressure medium thereby increasing the system pressure from the reservoir to the main pressure line and the pressure reservoir promoted. Then, by means of the pressure sensor, an increase in the pressure prevailing in the pressure line system pressure over an upper second Determined limit, the hydraulic pump is switched off by switching off the electric motor again.
  • a subsequent consumption of pressure medium which can be caused by the actuation of actuators and leaks in control valves and actuators, is compensated for as long as from the accumulator until the pressure prevailing in the main pressure line system pressure has again reached or fallen below the lower first limit.
  • the pressure relief valve is usually designed to be effective automatically, that is not actively controlled, and limits the effective system pressure in the main pressure line system by a return, if necessary, of pressure medium from the main pressure line in the reservoir.
  • shut-off valves In order to avoid high leakage, it is known to connect a shut-off valve to proportional valves, with which they can be shut off outside of their operating phases against the main pressure line and thus relieved of the system pressure.
  • shut-off valves represent an additional expenditure on equipment and form an additional potential source of error.
  • an electro-hydraulic control device of an automated manual transmission is known, in accordance with the local Fig. 1 designed as a proportional solenoid valve control valve designed as a single-acting actuator cylinder Wählaktua- and the two formed as a proportional solenoid valves control valves designed as a double-acting actuator cylinder Wegvik together upstream of a pressure-controlled shut-off valve.
  • the shut-off valve is closed in the unactuated state and controlled by the actuating pressure of the clutch actuator so that it is opened when a certain pressure limit is exceeded and closed when the pressure falls below the pressure limit.
  • a further electrohydraulic control device of an automatic transmission is known, in accordance with the local Fig. 1 designed as a proportional solenoid valve control valve designed as a double-acting actuating cylinder Wählaktua- sector and formed as a proportional solenoid valve control valve designed as a double-acting actuating cylinder Wegaktuators together a solenoid switching valve is connected upstream, by which the pressure chambers of the actuating cylinder are depressurized in the unactuated state. In each case a pressure chamber of the actuating cylinder is connected via the associated control valve with the magnetic switching valve in connection.
  • the other pressure chamber of the Wählaktuators is directly connected to the magnetic switching valve in connection, whereas the other pressure chamber of the Weguators a pressure reducing valve is connected upstream, which is mechanically controlled by a selector rod via a piston rod. Also in this control device, the control valves and the associated actuators only as needed, so if a circuit should take place, connected to the main pressure line and thus subjected to the system pressure or a reduced pressure.
  • the present invention has the object to provide a generally usable, preferably also suitable for controlling an automated step transmission suitable electro-hydraulic control device having a functional structure and improved control properties without function restrictions.
  • the invention initially relates to an electro-hydraulic control device, comprising a pressure supply device for conveying a pressure medium from a reservoir into a main pressure line, wherein the promotion of the pressure medium via a drivable by a controllable electric motor pump element, and with an actuating device for actuating at least one hydraulic actuator, wherein the actuation of the actuator via a producible by at least one control valve connection of at least one pressure chamber of the actuator to the main pressure line and / or is carried out with a pressure-free line.
  • the pumping element is designed as a single-acting pressure cylinder, in which a connected via a spindle gear with the electric motor piston is axially movable and axially bounded on one side a pressure chamber, which is provided with a check valve with a suction line to the reservoir and a pressure line communicates with the main pressure line.
  • the invention according to the independent claim 2 is based on an electrohydraulic control device of an automated step transmission, with a pressure supply device for conveying a pressure medium from a reservoir into a main pressure line, wherein the promotion of the pressure medium via a drivable by a controllable electric motor pumping element, and with an adjusting device for actuating at least one hydraulic Kupplungsaktuators and / or a hydraulic Wählaktuators and / or a hydraulic GmbHaktuators, wherein the actuation of the relevant actuator via a manufacturable by at least one control valve connection of at least one pressure chamber of the actuator with the main pressure line and / or with a Pressure-free line takes place.
  • the pumping element is designed as a single-acting pressure cylinder, in which a connected via a spindle gear to the electric motor piston is axially movably axially bounded on one side and a pressure chamber over a suction line provided with a check valve with the reservoir and via a pressure line to the main pressure line is in communication.
  • the invention is therefore based on an electro-hydraulic control device, for example a control device of an automated step transmission, the pressure supply device for conveying a pressure medium from a reservoir into a main pressure line and an actuating device for actuating at least one hydraulic actuator, in particular a hydraulic Kupplungsaktuators and / or a hydraulic Wählaktuators and / or a hydraulic Wegua- sector comprises.
  • the delivery of the pressure medium is effected via a pump element which can be driven by a controllable electric motor.
  • an actuator such as a hydraulic Kupplungsaktuators, a hydraulic Wählaktuators and / or a hydraulic Weguators, via a producible by at least one control valve connection of at least one pressure chamber of the actuator to the main pressure line and / or with a pressure line.
  • the inventive design of the pumping element as a single-acting pressure cylinder whose piston is driven by a spindle gear from the electric motor, resulting in conjunction with a simplified construction of the pressure generating device good control properties for setting a desired system pressure in the main pressure line and to supply the actuator with a required Pressure medium volume flow, which is due to the actuation of the hydraulic actuators and leakage in the actuators and in the associated control valves.
  • the piston of the pressure cylinder By generating a certain drive torque of the electric motor, the piston of the pressure cylinder is loaded via the spindle gear with an axial force in the direction of the pressure chamber, whereby the pressure in the pressure chamber and in the main pressure line connected to these increases and, if necessary, pressure medium is conveyed from the pressure chamber into the main pressure line.
  • the drive torque of the electric motor which is proportional to the controllable load current of the electric motor, therefore, a sufficiently accurate adjustment of the system pressure prevailing in the main pressure line is possible.
  • auxiliary elements such as a pressure sensor, a pressure relief valve and a pressure accumulator, thus space and cost can be dispensed with.
  • the control valve arrangement of the adjusting device can be made simpler, since the function of a pressure regulating valve can be fulfilled by a corresponding control of the pressure cylinder by the pressure generating device.
  • a servo pressure is generated via the relevant hydraulic pressure cylinder, which is used in parallel or serial arrangement to support a manually generated control pressure for disengaging a clutch, wherein the control of the associated electric motor and thus the servo pressure in response to the sensory detected encoder pressure and / or the encoder travel of a manually operated master cylinder takes place.
  • the control device comprises two pumping elements designed as single-acting impression cylinders which mirror axially on both sides of the electric motor. are arranged symmetrically, the pistons are connected via a provided with a common spindle shaft spindle gear to the electric motor, and the pressure chambers are each provided via a provided with a check valve suction with the reservoir and a provided with a check valve pressure line with the main pressure line in combination.
  • the piston of a pressure cylinder sucks pressure medium from the reservoir into its pressure chamber, while the piston of the other pressure cylinder promotes pressure medium from its pressure chamber with a corresponding pressure in the main pressure line.
  • the permanent supply of the main pressure line and the adjusting device connected thereto is ensured with a pressure medium pressure and with a pressure medium volume flow.
  • the pumping element is designed as a double-acting pressure cylinder, the piston axially on both sides each delimiting a pressure chamber, and its pressure chambers each provided with a check valve Suction line to the reservoir and via a provided with a check valve pressure line with the main pressure line in conjunction.
  • the spindle gear is preferably designed as a ball screw screw drive.
  • Such a spindle gear is particularly free of play and low in resistance, so that this results in a particularly accurate and low-hysteresis relationship between the torque of the electric motor and prevailing in the pressure chamber and the main pressure line connected thereto system pressure.
  • the pressure cylinder or the pressure cylinder of the pressure supply device advantageously has a resilient portion.
  • This resilient portion is expediently designed in each case as a ring-cylindrical diaphragm and arranged at the front end of the pressure chamber between a rigid cylinder portion and a rigid bottom of the impression cylinder.
  • the resilient portion of the printing cylinder is formed as a plate-shaped membrane and is arranged in the pressure chamber limiting the bottom or forms the pressure chamber bounding bottom.
  • the pressure cylinder of the pressure supply device is expediently assigned a displacement sensor which is mechanically or non-contactly in operative connection with the piston, the piston rod or the spindle of the spindle transmission.
  • a displacement sensor which is mechanically or non-contactly in operative connection with the piston, the piston rod or the spindle of the spindle transmission.
  • a shut-off device for inclusion of a control pressure in at least one of the actuators is suitably provided.
  • the shut-off device may be formed by at least one shut-off valve, which is connected upstream of a control valve which is associated with one of the actuators and is closed to include the control pressure.
  • the shut-off device can also be formed by a shut-off position of at least one control valve assigned to one of the actuators, wherein the control valve is controlled to include the setting pressure in the shut-off position.
  • the shut-off device can also be formed by the formation of at least one control valve assigned to one of the actuators as a clock valve, which is closed to include the pressure medium.
  • the system pressure which is effective as pilot pressure can then be increased, lowered or changed with a desired passage of time in a suitable manner via the pressure cylinder of the pressure-generating device.
  • the description is accompanied by a drawing with exemplary embodiments. In this shows
  • FIG. 1 shows an electro-hydraulic control device of an automated manual transmission with a first embodiment of the pressure supply device according to the invention in a schematic representation
  • FIG. 2 shows an electro-hydraulic control device that is advantageously developed in comparison with the embodiment according to FIG. 1, FIG.
  • FIG. 3 shows the electrohydraulic control device according to FIG. 1 with a second embodiment of the pressure supply device according to the invention
  • FIG. 4 shows the electrohydraulic control device according to FIG. 1 with a third embodiment of the pressure supply device according to the invention.
  • a pressure supply device 2.1 for conveying a pressure medium from a reservoir 3 into a main pressure line 4, an actuating device 5.1 for actuating hydraulic clutch and gear actuators 6, 7 and 8, and an electronic control unit 9 for controlling the pressure supply device 2.1 and the actuators 6, 7, 8 of the actuating device 5.1.
  • the pressure supply device 2.1 has a pump element 10 which can be driven by an electric motor 9 which can be actuated by the control device 9 via electrical supply lines which are not particularly designated.
  • the pumping element 10 is designed as a single-acting pressure cylinder 12, in which a via a spindle gear 13 with the electric motor 1 1 connected piston 14 is guided axially movable and axially bounded on one side a pressure chamber 15.
  • the pressure chamber 15 is connected via a provided with a check valve 16 suction line 17 with the reservoir (oil sump) 3 and a pressure line 18 to the main pressure line 4 in connection.
  • the piston 14 of the pressure cylinder 12 By generating a certain drive torque of the electric motor 11, the piston 14 of the pressure cylinder 12 is loaded via the spindle gear 13 with an axial force in the direction of the pressure chamber 15, whereby the pressure in the pressure chamber 15 and in the main pressure line 4 connected thereto and, if necessary, pressure medium is conveyed from the pressure chamber 15 in the main pressure line 4.
  • the drive torque of the electric motor 1 1 By reducing the drive torque of the electric motor 1 1, the pressure in the pressure chamber 15 and in the main pressure line 4 is reduced accordingly.
  • the piston 14 of the pressure cylinder 12 By reducing the drive torque of the electric motor 1 1, the piston 14 of the pressure cylinder 12 is loaded via the spindle gear 13 with an axial force in the direction of the pressure chamber 15, whereby the pressure in the pressure chamber 15 and in the main pressure line 4 connected thereto and, if necessary, pressure medium is conveyed from the pressure chamber 15 in the main pressure line 4.
  • a mechanical or non-contact with the piston 14 in operative connection path sensor 20 is provided over in each case a not further designated sensor line with the control unit 9 are in communication. Due to the control properties of the pressure supply device 2.1 according to the invention can be dispensed with a pressure relief valve and a pressure accumulator, which are usually connected as part of a pressure supply device to the main pressure line 4.
  • the adjusting device 5.1 comprises a clutch actuator 6 for engagement and disengagement of a passively closable clutch, a Wählaktuator 7 for selecting a shift gate, ie for selective change of the internal transmission actuating connection between a shift shaft and a plurality of shift rails, and a shift actuator 8 for engaging and disengaging one of selected shift gate or shift rod associated gear.
  • the clutch actuator 6 is designed as a single-acting actuating cylinder 21 with a single pressure chamber 22, the three as 2/2-way solenoid valves seated control valves 23, 24, 25 are assigned. Via the first control valve 23, the pressure chamber 22 of the clutch actuator 6 can be connected to the disengagement of the associated clutch connected to the main pressure line 4. Via the second control valve 24, the pressure chamber 22 of the clutch actuator 6 can be connected to the rapid engagement of the clutch regulated with a leading to the reservoir 3 pressure line 26. Via the third control valve 25, which is connected via a throttle 27 to the pressure-free line 26, the pressure chamber 22 of the clutch actuator 6 can be connected to the slow engagement of the clutch connected to the pressure-free line 26.
  • the Wählaktuator 7 is designed as a double-acting actuator cylinder 28 with two pressure chambers 29, 30, each of which a valve as a 3/2-way solenoid valve, for example, as a ball seat valve, formed control valve 31, 32 is assigned.
  • a valve as a 3/2-way solenoid valve, for example, as a ball seat valve, formed control valve 31, 32 is assigned.
  • the first control valve 31 the first pressure chamber 29 of the Wählaktuators 7 for controlling a change of the shift gate by Pulsed control pulse width modulated mutually connected to the main pressure line 4 and the pressure line 26 are connected.
  • the pressure and the piston travel of the selector 7 can be regulated by a displacement or current control of the piston 14 of the pressure supply device 2.1.
  • the second pressure chamber 30 of the Wählaktuators 7 for controlling a change of the shift gate with the main pressure line 4 and the pressure line 26 can be connected in the same way.
  • the shift actuator 8 is also formed as a double-acting Stellzylin- 33 with two pressure chambers 34, 35, each associated with a designed as a 3/2-way solenoid valve control valve 36, 37 are assigned. Via the first control valve 36, the first pressure chamber 34 and the second control valve 37 of the second pressure chamber 35 of the Wegaktuators 8 for controlling a gear change with the main pressure line 4 and the pressure line 26 are connected.
  • a displacement sensor 38, 39, 40 is assigned to each of them. which are connected via not further designated sensor lines with the control unit 9 in connection.
  • the solenoid valves designed as control valves 23, 24, 25; 31, 32; 36, 37 of the actuators 6, 7, 8 connected to their control via non-designated control lines to the control unit 9.
  • the electrohydraulic control device 1.2 according to FIG. 2 is significantly simplified compared with the embodiment according to FIG.
  • the pressure sensor 19 is dispensed with, since the system pressure prevailing in the main pressure line 4 due to exact controllability of the pressure applied to the piston 14 or caused by the piston 14 in the pressure chamber 15 of the pressure cylinder 12 via the electric motor 1 1 from the height of the load current of the electric motor 1 1 can be derived.
  • the control valves 24 and 25 over which in the embodiment of FIG. 1, the emptying of the pressure chamber 22 of the clutch actuator 6 is controlled to engage the associated clutch, saved.
  • the emptying of the pressure chamber 22 by a corresponding control of the electric motor 1 1 takes place by receiving the corresponding pressure medium volume in the pressure chamber 15 of the pressure cylinder 12 of the pressure supply device 2.2.
  • the selector actuator 7 in contrast to the embodiment according to FIG. 1, is designed as a single-acting actuating cylinder 41 with a single pressure chamber 42, to which a control valve 43 designed as a 2/2-way solenoid clock valve is assigned. Via the control valve 43, the pressure chamber 42 of the Wählaktuators 7 can be controlled to control a change of the shift gate in one direction with the main pressure line 4.
  • the electrohydraulic control device 1.3 according to FIG. 3 has an altered pressure supply device 2.3 compared with the embodiment according to FIG. 1 with the same positioning device 5.1.
  • the pumping element 10 is formed as a double-acting pressure cylinder 46, the piston 47 axially on both sides each defining a pressure chamber 48, and its pressure chambers 48 each have a provided with a check valve 16 suction line 17 with the Reservoir 3 and via a provided with a check valve 45 pressure line 18 with the main pressure line 4 are in communication.
  • the pressure supply device 2.4 is at rotating electric motor 1 1 with the same effect alternately automatically a pressure chamber 48 of the pressure cylinder 46 in the suction mode and the other pressure chamber 48 of the pressure cylinder 46 in the printing operation.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)

Abstract

L'invention concerne un dispositif de commande électrohydraulique comportant un dispositif d'alimentation en pression (2.1, 2.2) destiné à transporter un fluide de pression d'un contenant de stockage (3) vers une conduite de pression principale (4), le transport du fluide de pression étant réalisé au moyen d'un élément pompe (10) pouvant être entraîné par un moteur électrique commandable (11). Le dispositif de commande électrohydraulique comporte également un dispositif de réglage (5.1, 5.2) destiné à actionner au moins un actionneur hydraulique (6, 7, 8), l'actionnement de l'actionneur (6, 7, 8) étant réalisé au moyen d'une connexion, établie à l'aide d'au moins une soupape de commande (23, 24, 25; 31, 32; 36, 37; 43), entre au moins une chambre de pression (22; 29, 30; 34, 35; 42) de l'actionneur (6, 7, 8) et la conduite de pression principale (4) et/ou une conduite sans pression (26). Pour simplifier le dispositif de commande, l'élément pompe (10) est conçu en tant que cylindre de pression (12) à effet simple, dans lequel un piston (14) connecté au moteur électrique (11) au moyen d'un entraînement à broche (13), est guidé axialement mobile et délimite, de façon axialement unilatérale, une chambre de pression (15) connectée au contenant de stockage (3) au moyen d'une conduite d'aspiration (17) pourvue d'un clapet antiretour (16), et à la conduite de pression principale (4) au moyen d'une conduite de pression (18).
EP08803982A 2007-09-18 2008-09-11 Dispositif de commande electrohydraulique Withdrawn EP2188543A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007044431A DE102007044431A1 (de) 2007-09-18 2007-09-18 Elektrohydraulische Steuerungsvorrichtung
PCT/EP2008/062015 WO2009037170A1 (fr) 2007-09-18 2008-09-11 Dispositif de commande électrohydraulique

Publications (1)

Publication Number Publication Date
EP2188543A1 true EP2188543A1 (fr) 2010-05-26

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08803982A Withdrawn EP2188543A1 (fr) 2007-09-18 2008-09-11 Dispositif de commande electrohydraulique

Country Status (3)

Country Link
EP (1) EP2188543A1 (fr)
DE (1) DE102007044431A1 (fr)
WO (1) WO2009037170A1 (fr)

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