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EP1574720B1 - Commande électro-hydraulique et méthode de sa déactivation - Google Patents

Commande électro-hydraulique et méthode de sa déactivation Download PDF

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Publication number
EP1574720B1
EP1574720B1 EP20040026604 EP04026604A EP1574720B1 EP 1574720 B1 EP1574720 B1 EP 1574720B1 EP 20040026604 EP20040026604 EP 20040026604 EP 04026604 A EP04026604 A EP 04026604A EP 1574720 B1 EP1574720 B1 EP 1574720B1
Authority
EP
European Patent Office
Prior art keywords
pressure
line
working
solenoid
valve
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
EP20040026604
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German (de)
English (en)
Other versions
EP1574720A1 (fr
Inventor
Martin Dipl.-Ing. Univ. Heusser
Georg Dipl.-Ing. Neumair (Fh)
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.)
Hawe Hydraulik SE
Original Assignee
Hawe Hydraulik SE
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Filing date
Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Publication of EP1574720A1 publication Critical patent/EP1574720A1/fr
Application granted granted Critical
Publication of EP1574720B1 publication Critical patent/EP1574720B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B11/003—Systems with load-holding 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31529—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and a single output member
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated
    • Y10T137/87209—Electric
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—Motor

Definitions

  • the invention relates to an electro-hydraulic control device specified in the preamble of claim 1 and according to claim 8, a method for switching off the control device.
  • the circulation circuit has an adjustable throttle in the pressure supply line and upstream of the throttle directly from the pressure supply line against spring force pressure-controlled discharge valve in a provided from the pressure supply line to a return drain line.
  • the two load-holding valves of the working lines are hydraulically releasable check valves, and the two main-way solenoid seat valves are designed as 3/2-way magnetic seat valves, each of which blocks a working line from the pressure source and connects to the return, or shut off to the return and connects to the pressure source.
  • the control line system is supplied with the control pressure from the respective higher working pressure leading working line to pressurize the circulation circuit.
  • the control pressure taken from the respective working pressure leading to the higher working pressure is used to unblock the load pressure in the load-bearing line closed by the pressure source, so that this working line is relieved to the return flow.
  • Such electro-hydraulic control devices are preferably used for portable working devices such as screwdrivers, riveting tools, building displacement devices and the like.
  • extremely high working pressures can be built up, for example up to about 800 bar, with a pressure source operating at maximum pressure with a relatively low flow rate.
  • poppet valves are absolutely necessary, which have leak-free shut-off positions.
  • the hydraulically releasable check valves which are used as load-holding valves, the effect occurs that after switching off the control device in at least one working line the working pressure is maintained. Due to the seat valves, this pressure remains for very long periods without noticeable waste. This is a significant operating hazard.
  • it is sometimes necessary to disconnect the working line with the control device disconnected which, however, can not be carried out at maintained working pressure or is dangerous for violent separation or pollutes the environment with the hydraulic fluid.
  • a known electro-hydraulic control device four 2/2-way proportional solenoid seat valves are provided in a bridge circuit between the two admission sides of the hydraulic motor and the pressure source or the tank. Between the pressure source and the return, a circulation circuit with two solenoid-operated 2/2-way valves is also provided.
  • a controller of the control device different operating modes are programmed, which can be controlled not only the speed-controlled retraction and extension of the hydraulic motor, but also a floating position, under load speed controlled retraction, a load-controlled under load extension, a tank make-up mode and include a tank and pump make-up mode. If, after the movement of the hydraulic motor controlled by the pressure source, the control device is switched off under pressure, then this increased pressure remains trapped in a working line.
  • JP 571 07 486 A known multi-way valve without load-holding valves is in the neutral position a Abströmweg in Steuerkammem and loose loose fit of valve elements to the tank open. Only one working line can be relieved of pressure in each case.
  • both chambers of a hydraulic consumer via electro-hydraulic proportional valves are secured, each of which consists of a 2/2-solenoid proportional pressure control valve and a 2/2-hydraulic proportional valve.
  • the load leak-free tight holding load-retaining valves are missing.
  • the invention has for its object to provide an electro-hydraulic control device of the type mentioned, whose operational hazard after switching off the Electro-hydraulic control device is reduced, and to provide a method for switching off the electro-hydraulic control device.
  • each load-holding valve is a 2/2-way magnetic seat valve which can be electrically switched to return flow
  • the working pressure in at least one working line need not be maintained permanently, but can be reduced to the return after a shutdown of the possibly high clogged working pressure by the switching magnet of a load-holding valve is briefly energized. This can be done routinely (via the associated control device) after each shutdown of the control device, or optionally in the event that a working pressure leading working line must be released after shutdown for some reason.
  • the optional pressure relief of a working line under working pressure is expedient to carry out comfortably when it is derived after switching off the control device from the pressure source pending pressure on the circulation circuit.
  • the circulation circuit is suitably operated by a load-dependent control pressure.
  • the control pressure can be tapped directly or indirectly from the respective working line or via the control line system from the pressure line.
  • the circulation circuit reliably enters the position for non-pressurized circulation, a magnetically confirmed control pressure relief seat valve is connected to the return line to the control line system for each working line.
  • the relief seat valve is closed and leak-tight, so that the control pressure is reliably maintained.
  • the control pressure collapses and the circulation circuit switches to the non-pressurized circulation position.
  • the 2/2-way magnetic seat valve for the respective one working line and the main-way magnetic seat valve of the other working line have a common switching magnet. If one working line is acted on, the other working line is automatically relieved to return.
  • a separate solenoid allows, however, to actuate the respective 2/2-way solenoid seat valve independently of the solenoid of the main-way solenoid seat valve, and to connect a pressurized working line to the return, by an optional actuation of the separate solenoid of the 2/2-way magnetic seat valve, whose working line is to be relieved.
  • each relief seat valve is mitbetätigt by the solenoid of the main-way magnetic seat valve.
  • each relief seat valve it would be possible to give each relief seat valve its own switching magnet, which, for special situations, is actuated separately from the solenoid of the main path magnetic seat valve.
  • the relief seat valve may additionally be assigned the task of tapping the control pressure from the respective working line or, alternatively, from the pressure line.
  • the relief seat valve is designed as a 3/2-way solenoid seat valve.
  • the relief poppet valve may be a simple 2/2-solenoid seated valve designed only to process the pilot pressure, i. relatively compact, is to train.
  • the circulation circuit may include a 2/2-way pressure compensator circulation valve, conveniently also in poppet design, between the pressure line and the return.
  • the seat valve design is suitable for high working pressures because of the leak-free shut-off position.
  • the pressure compensator circulation valve it may be appropriate to assign the pressure compensator circulation valve a two-way flow regulator, which operates between the pressure line and the control line system.
  • non-inventive electro-hydraulic control device H is used for example for directional control of a hydraulic load or hydraulic motor, which is connected to two working lines A, B (not shown).
  • a pressure line 1 is supplied, from which a further pressure line 2 to two main-way solenoid seat valves VA, VB branches off for each working line A, B.
  • the two main-way magnetic seat valves VA, VB 3/2-way magnetic seat valves each actuated by a solenoid MA, MB.
  • MB load lines A, B are shut off from the pressure line 2 and connected at the same time with return lines 3 and a return line 4 with a return R.
  • Leakage-free return valves 9 in the working lines A, B verhindem but a return flow.
  • a circulation circuit U is contained in a line loop 5, which contains a conventional 2/2-way switching or control valve with leak-free seat function in the shut-off, with the derived from the pressure line 1 control pressure in the opening direction and is acted upon by a control line system 7 acting control pressure and a control spring in the closing direction.
  • the control line system 7 is connected to the working lines A, B output of the main-way magnetic seat valves VA, VB.
  • the respective higher control pressure of a working line is brought via appropriately interconnected shuttle valves 8 to the closing side of the circulation circuit U.
  • the control line system 7 is connected via a bypass line 7 'to the return manifold 4, if the electro-hydraulic control device H is provided only for a hydraulic consumer. If, however, other similar or differently designed control devices connected to the pressure line 1 and the return manifold 4, then the control line system 7 shown can be connected via a connecting line 7 "to another shuttle valve 8 ', feeds the control pressure in the control line system, if the electro-hydraulic control device H. is not actuated or the control pressure in the shuttle valve 8 'is correspondingly high.
  • a line 11 branches off to a branch 12 of the return line 3.
  • a 2/2-solenoid seat valve is provided as a load-holding valve LB, which is held by a spring 16 in the leak-free shut-off position shown.
  • the 2/2-solenoid seat valve is solenoid operated, either via the solenoid MA of Hauptweg solenoid seat valve VA, or (indicated by dashed lines) via its own solenoid M, which can always be operated together with the solenoid MA.
  • the line 14 is also included as a load-holding valve LA a 2/2-solenoid seat valve, which is actuated by the solenoid MB of the main-way magnetic seat valve VB (or optionally has its own switching magnet M).
  • Fig. 1 the electro-hydraulic control device is switched off. If the pressure source P promotes the pressure medium is passed through the circulation circuit U in the return. If the hydraulic consumer to be acted upon via the working line A, at the same time the pressure medium is discharged via the working line B to the return, the solenoid MA is energized (function a) to change the main-way magnetic seat valve VA and the load-holding valve LB. Then, the pressure line 2 is connected to the working line A, and also the working pressure in the working line A is fed into the control line system 7. As a result, the circulation circuit U is brought into the shut-off position shown or held in this. The hydraulic consumer moves.
  • the load holding valves LB, LA are similar to the 2/2-solenoid seat valves of Fig. 1 , with the difference, in the shut-off position in both flow directions leak-tight shut off.
  • the line parts 11a and 14a each lead directly to the return manifold 4. From the line part 11a branches off at a branch 17, a line 18 to a relief solenoid seat valve EA for the control line system 7, which also comes with a coming from a branch 19 line 20 with control pressure from the Working line A can be supplied.
  • the relief solenoid seat valve EA in this embodiment is a 3/2-way magnetic seat valve operated by the solenoid MA, which also operates the load holding valve LB and the main-way solenoid seat valve VA.
  • the relief valve EA or the load-holding valve LB have their own switching magnet.
  • a conduit 22 branches off to a relief solenoid seat valve EB which is also formed as a 3/2-way magnetic seat valve and actuated by the solenoid MB of the other main-way solenoid seat valve VB.
  • a relief solenoid seat valve EB which is also formed as a 3/2-way magnetic seat valve and actuated by the solenoid MB of the other main-way solenoid seat valve VB.
  • the switching magnet MA is energized (function a), which converts the valves VA, LB and EA substantially simultaneously into their other switching positions.
  • the pressure line 2 is then connected to the working line A, while the working line B is connected via the line 11 and the conduit part 11 a to the return manifold 4.
  • the control device H is turned off, then initially the working pressure in the working line A is maintained, because the lines 20 and 14 are shut off leak-free, as well as the working line A itself.
  • the embodiment of the electro-hydraulic control device H in Fig. 3 is different from that of Fig. 2 in that the control pressure for the control line system 7 is tapped directly from the pressure line 2. For this purpose lead from a branch 25 of the pressure line 2 lines 26 to the relief solenoid seat valves EA and EB.
  • the other function corresponds to that of Fig. 2 ,
  • the embodiment of the Fig. 4 is different from those of Fig. 2 and 3 by another way of tapping the control pressure for the control line system 7. And although the control pressure is tapped directly at a branch 27 from the pressure line 1 here.
  • the relief solenoid seat valves EA and EB are simple 2/2-way solenoid seat valves in the control line system 7, which also need to be designed only to the control pressure medium quantity, and leak-tight shut off only in the flow direction to the return R.
  • the two relief magnetic seat valves EA and EB are arranged in series in the control line system 7. The function largely corresponds to that for the Fig. 2 and 3 explained function.
  • the solenoid MB is briefly energized; however, to reduce the working pressure in the working line B briefly the solenoid MA.
  • Fig. 5 largely corresponds to that of Fig. 4 , The only difference is that in the control line system 7, the control pressure is tapped directly from the branch 27 in the pressure line 1, a two-way flow regulator Z is provided as part of the circulation circuit U, which doses the amount of the control pressure medium in the control line system 7 finely.
  • the two-way flow regulator operates on the principle of a pressure compensator, the upstream of pilot pressures and downstream of a Throttle and a control spring is actuated.
  • the other function corresponds to the in Fig. 4 explained.
  • the non-inventive embodiment in Fig. 6 corresponds largely to the embodiments of Fig. 4 and 5 , Different is the circulation circuit U, which is operated here without control line system with a working line 29, which leads from a branch 28 in the pressure line 1 via the series arranged in relief solenoid seat valves EA, EB to the return R.
  • the relief magnetic seat valves EA, EB are designed so that they can process the entire working flow from the pressure source in the non-pressurized circulation.
  • the further function corresponds to that to the Fig. 4 and 5 described.
  • To reduce the working pressure from the working line A it is sufficient to briefly energize the switching magnet MB after switching off (function b); however, to reduce the working pressure in the working line B, a short-term actuation of the solenoid MA (function a).

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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)
  • Forklifts And Lifting Vehicles (AREA)

Claims (8)

  1. Dispositif de commande électro-hydraulique (H) pour la commande de direction d'au moins un moteur hydraulique, en particulier pour des pressions de service allant jusqu'au dessus d'environ 450 bars dans un dispositif de travail portable, comprenant deux conduites de travail (A, B), deux électrovannes à siège (VA, VB) à voies principales, et une source de pression (P), les conduites de travail (A, B) pouvant être raccordées sélectivement en alternance, par l'intermédiaire de chacune des électrovannes à siège (VA, VB) à voies principales, à la source de pression (P) ou être verrouillées par la source de pression (P), une soupape de maintien de charge (LA, LB) par conduite de travail (A, B), réalisée sous forme d'une électrovanne à siège à 2/2 voies, laquelle soupape peut être commutée dans la position de commutation de l'électrovanne à siège (VA, VB) à voies principales, reliant la source de pression (P) à l'autre conduite de travail respective, d'une position de maintien de charge pour chacune des conduites de travail, pour l'éjection de l'agent sous pression du moteur hydraulique, au moyen de respectivement un aimant de commutation à excitation électrique (MA, MB, M), sur passage à un retour (R), et comprenant un montage de circulation (U) actif entre la source de pression (P) et le retour (R) en position de verrouillage des conduites (A, B) par la source de pression (P), caractérisé en ce que le montage de circulation (U) peut être sollicité par une pression de commande prise directement ou indirectement par l'intermédiaire d'un système de conduite pilote (7), qui fait partie du dispositif de commande électro-hydraulique (H), sélectivement d'une conduite de travail (A, B) ou d'une conduite sous pression (1, 2) reliée à la source de pression (P), et qu'une soupape à siège de détente sous pression de commande (EA, EB) à actionnement magnétique, qui fait partie du dispositif de commande électro-hydraulique (H), est raccordée en direction du retour (R) au système de conduite pilote (7) pour chaque conduite de travail (A, B).
  2. Dispositif de commande électro-hydraulique suivant la revendication 1, caractérisé en que l'électrovanne à siège à 2/2 voies de maintien de charge pour l'une des conduites de travail respective (A ou B) et l'électrovanne à siège (VA, VB) à voies principales pour l'autre conduite de travail respective (B ou A) sont actionnées par un aimant de commutation commun (MA, MB).
  3. Dispositif de commande électro-hydraulique suivant la revendication 1, caractérisé en ce que la soupape à siège de détente sous pression de commande (EA, EB) est commutable sur passage, soit par un aimant de commutation propre (M) actionnable avec l'aimant de commutation (MA MB) de l'électrovanne à siège à voies principales (VA, VB) de cette conduite de travail (A ou B), soit par les aimants de commutation (MA, MB) de l'électrovanne à siège à voies principales (VA, VB).
  4. Dispositif de commande électro-hydraulique suivant la revendication 1, caractérisé en ce que la soupape à siège de détente (EA, EB), en cas de prise indirecte de la pression de commande de la conduite de travail (A, B) ou de la conduite sous pression (1, 2), est une électrovanne à siège à 3/2 voies.
  5. Dispositif de commande électro-hydraulique suivant la revendication 1, caractérisé en ce que la soupape à siège de détente (EA, EB), en cas de prise directe de la pression de commande de la conduite sous pression (1, 2), est une électrovanne à siège à 2/2 voies.
  6. Dispositif de commande électro-hydraulique suivant la revendication 1, caractérisé en ce que le montage de circulation (U) comporte une vanne de circulation à balances de pression à 2/2 voies entre la conduite sous pression (1) et le retour (R) et que, dans le système de conduite pilote (7), en cas de prise directe de la pression de commande de la conduite sous pression (1), il est prévu un régulateur de débit à deux voies (Z) associé à la vanne de circulation à balances de pression à 2/2 voies.
  7. Dispositif de commande électro-hydraulique suivant la revendication 1, caractérisé en ce que, dans le montage de circulation (U), les deux soupapes à siège de détente (EA, EB) respectivement conçues sur le débit de travail total sont montées en série dans un parcours de débit de travail (29) de la conduite sous pression (1) en direction du retour (R).
  8. Procédé de désactivation du dispositif de commande électro-hydraulique (H) suivant la revendication 1, caractérisé en ce que, pour supprimer la pression de service d'une conduite de travail (A ou B) sous pression de service après la désactivation, l'aimant de commutation (MA, MB, M) de la soupape de maintien de charge (LA, LB), associé à la conduite de travail (A ou B) sous pression de travail après la désactivation, est excité momentanément après la désactivation du dispositif de commande (H).
EP20040026604 2004-03-10 2004-11-09 Commande électro-hydraulique et méthode de sa déactivation Expired - Lifetime EP1574720B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE202004003749U DE202004003749U1 (de) 2004-03-10 2004-03-10 Elektrohydraulische Steuervorrichtung
DE202004003749U 2004-03-10

Publications (2)

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EP1574720A1 EP1574720A1 (fr) 2005-09-14
EP1574720B1 true EP1574720B1 (fr) 2009-03-11

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EP20040026604 Expired - Lifetime EP1574720B1 (fr) 2004-03-10 2004-11-09 Commande électro-hydraulique et méthode de sa déactivation

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US (1) US7320335B2 (fr)
EP (1) EP1574720B1 (fr)
AT (1) ATE425370T1 (fr)
DE (2) DE202004003749U1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7849686B2 (en) * 2007-02-07 2010-12-14 Sauer-Danfoss Aps Valve assembly and a hydraulic actuator comprising the valve assembly
DE102008037235A1 (de) * 2008-08-09 2010-02-11 Volkswagen Ag Hydraulikkreislauf
ES2372042T3 (es) 2009-04-15 2012-01-13 Hawe Hydraulik Se Dispositivo de control.
EP2392819B1 (fr) * 2010-05-31 2013-04-03 HAWE Hydraulik SE Dispositif de réglage rotatif hydroélectrique des pales de rotor sur le rotor d'une éolienne
CN103742615B (zh) * 2013-12-31 2016-08-17 广船国际有限公司 一种重载生产线链条的自动张紧液压装置

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DE2928005A1 (de) * 1978-07-18 1980-02-14 Diesel Kiki Co Ferngesteuerte proportionalregelungs- richtungsumschalt-regelventilvorrichtung
DE3006259A1 (de) * 1980-02-20 1981-08-27 Wabco Fahrzeugbremsen Gmbh, 3000 Hannover Wechselventil fuer pneumatisch gesteuerte tueranlgen
JPS57107486A (en) 1980-12-25 1982-07-03 Toyooki Kogyo Co Ltd Fluid control valve
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DE4340283A1 (de) * 1993-11-26 1995-06-01 Claas Ohg Hydraulisches Steuerventil
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Also Published As

Publication number Publication date
US7320335B2 (en) 2008-01-22
US20050199295A1 (en) 2005-09-15
DE502004009132D1 (de) 2009-04-23
EP1574720A1 (fr) 2005-09-14
ATE425370T1 (de) 2009-03-15
DE202004003749U1 (de) 2005-07-28

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