EP1710446B1 - Commande hydraulique et bloc de commande - Google Patents

Commande hydraulique et bloc de commande Download PDF

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Publication number
EP1710446B1
EP1710446B1 EP06007227A EP06007227A EP1710446B1 EP 1710446 B1 EP1710446 B1 EP 1710446B1 EP 06007227 A EP06007227 A EP 06007227A EP 06007227 A EP06007227 A EP 06007227A EP 1710446 B1 EP1710446 B1 EP 1710446B1
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EP
European Patent Office
Prior art keywords
pressure
valve
return
consumer
control device
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.)
Not-in-force
Application number
EP06007227A
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German (de)
English (en)
Other versions
EP1710446A2 (fr
EP1710446A3 (fr
Inventor
Thomas Fedde
Thorsten Lang
Hans Heinrich Prof. Dr. Dr. Harms
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication date
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Publication of EP1710446A2 publication Critical patent/EP1710446A2/fr
Publication of EP1710446A3 publication Critical patent/EP1710446A3/fr
Application granted granted Critical
Publication of EP1710446B1 publication Critical patent/EP1710446B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/305—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
    • 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
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in 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
    • F15B2211/50—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
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow 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
    • F15B2211/50—Pressure control
    • F15B2211/57—Control of 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a hydraulic consumer according to the preamble of patent claim 1 and a control block for controlling a plurality of consumers, wherein each consumer is associated with such a control arrangement.
  • the movement control hydraulic consumers of mobile equipment is usually via proportional directional valves, via which the pressure fluid flow direction and the pressure fluid flow to and from the consumer is adjustable.
  • a problem in mobile hydraulics are so-called pulling loads, in which the load acts in the direction of movement of the consumer. This may for example occur in a hydraulic cylinder, when the piston rod is extended and the pulling load acts in the direction of the extension movement. This can lead to an undersupply of the unloaded cylinder space, d. h., In the extension movement of the piston rod come to a shortage of the bottom-side cylinder space, so that cavitations may occur in this, over which the hydraulic cylinder or the Steueranordung is damaged.
  • lowering brake valves are used to avoid an undersupply of hydraulic consumers.
  • Such lowering brake valves are throttling valves that regulate the pressure medium volume flow of a pressure chamber flowing away from the consumer as a function of the pressure in the second, increasing pressure chamber.
  • the problem here is the mutual influence of the pressures in the two pressure chambers at the same time bad damping.
  • a movement control of the consumer with high dynamics is limited possible, the vote of the valves is extremely problematic in practice.
  • the tuning of the valves should generally be done together with the connected consumers, so that there is no possibility to operate with a universal lowering brake arbitrary consumers.
  • a control arrangement in which the inlet and the outlet are assigned separate directional valve spool for adjusting an inlet cross section and a flow cross section.
  • the control of the two valve spool is independent of each other via pilot pressure reducing valves, which are arranged in response to the pressures in the flow to and in the return from the consumer.
  • the consumer is at the in the US 5,138,838 solution shown a double-acting hydraulic cylinder.
  • the pressure drop in the supply line is detected by the pressure sensor and in the case of a deficiency, ie, when the pressure in the return is higher than that in the flow, the return cross section throttled over the valve slide arranged in the return, so that a shortage the increasing pressure space can be prevented.
  • the US 5,568,759 also discloses a control arrangement with separate valve spools in flow and return. In the case of a load change, too, a high outlay must be exerted in the case of a load change in order to adjust the cross section of the valve spool so that the speed of the consumer remains constant.
  • the present invention seeks to provide a hydraulic control arrangement for controlling a hydraulic load and a control block with a plurality of such control arrangements, which prevents a low supply with low device complexity in the case of a pulling load can be and beyond even with load changes a constant speed of movement of the driven consumer is guaranteed.
  • the pressure medium volume flow in the flow and in the return is adjusted via separately controllable valve slides, to which an individual pressure balance is assigned on the pump side, via which the pressure medium flows to a metering orifice controlled by one of the valve slides.
  • the two-way valve spool are independently position-controlled.
  • the two valve spools can each be arranged in an electro-hydraulically pilot-operated directional control valve whose pressure connections are connected to an output of the common individual pressure compensator.
  • This individual pressure compensator is preferably acted upon in the closing direction by a pressure upstream of the respectively effective metering orifice and in the opening direction by the force of a pressure compensating spring and the load pressure of the associated consumer.
  • This load pressure can be tapped via a shuttle valve from the flow to and from the return from the consumer.
  • a pressure sensor can be arranged in each case, so that can be detected in a simple manner when the pressure in the flow falls below a predetermined threshold.
  • the directional valves receiving the valve slides are in a preferred embodiment designed with a pressure connection, a tank connection, a working connection and an LS connection.
  • control arrangement is designed with a control unit via which the directional control valve arranged in the return line is controlled so that the return flow cross-section is reduced when the pressure drops in the flow under the aforementioned control value.
  • the LS control block according to the invention for controlling a plurality of consumers has a plurality of valve disks with the control arrangement according to claim 1.
  • valve disc 1 of a mobile control block, via which a consumer can be controlled.
  • the dashed lines indicated valve disc 1 has a pressure port P, a tank port T and two working ports A, B, which are connected via a flow line 2 and a return line 4 with a hydraulic consumer 6, which is designed in the illustrated embodiment as a double-acting hydraulic cylinder.
  • the feed line 2 is connected to a bottom-side cylinder chamber 8 and the return line 4 to an annular space of the cylinder 6.
  • valve disc 1 two-way valve units, hereinafter called directional control valves 12, 14 are formed, each having a pressure port P, a return port R and a working port A and B respectively.
  • directional control valve units 12 can also be accommodated in a common valve bore of the valve disc. That is, the directional control valves need not be separate components, but may also be integrated into a housing or the like.
  • Each of the directional control valves 12, 14 is about electro-hydraulic pilot valves 16, 18 and 20, 22 from its illustrated basic position in which the ports P, R, A are locked against each other in working positions (a) or (b) to adjust.
  • the return port R is shut off - it is opened a metering orifice 26 and 28, which determines the pressure medium flow to the load 6 and thus its speed.
  • the respective working port A or B is connected to the LS port.
  • the port A of the directional control valve 12 via a flow channel 30 and the port B of the directional control valve 14 via a return passage 32 to the working port B of the valve disc 1 is connected.
  • Both in the flow channel 30 and in the return channel 32 each have a pressure sensor 35 or 37 is provided, via which the pressure in the respective channel can be detected. This pressure corresponds to the load pressure of the consumer.
  • the two-way valves 12, 14 - as mentioned - each have a LS connection, this is via a respective LS branch channel 48, 50 with the input a change-over valve 52 whose output is connected via an LS-channel 54 to the LS port of the valve disc 1.
  • the individual pressure compensator 40 is acted upon in the closing direction by a pressure upstream of the two metering orifices 26, 28, in the present case by the pressure between the pressure port P of the valve disc 1 and the input port P of the individual pressure compensator 40.
  • This effective in the closing direction of the control pressure is applied via a branched off from the pump line 38 control line 56 to an effective in the closing direction control surface of the pressure compensator piston.
  • In the opening direction acts on the pressure compensator piston, the force of a pressure compensator spring 58 and the load pressure in the LS channel, which is guided via an LS branch channel 60 to an effective in the opening direction control surface of the pressure compensator piston.
  • the highest load pressure of all valve disks 1 of the mobile control block is tapped via a shuttle valve cascade (not shown) and fed to the pump regulator of a variable displacement pump, which is controlled such that there is always a pressure in the pump line 38, which is a predetermined pump ⁇ p above this highest load pressure is (LS control).
  • the two-way valves 12, 14 are each provided with a position control (not shown) via which the opening cross-section of the metering orifices and the outlet cross-sections (depending on the direction of flow) can be controlled exactly.
  • the directional control valve 12 is adjusted in one of its (a) and the directional control valve 14 in one of its (b) marked positions.
  • the pressure medium is then conveyed by the pump via the pressure port P of the valve disk 1, the pump line 38, the individual pressure compensator 40, the inlet channel 34, the metering orifice 26, the feed channel 30 and the feed line 2 into the bottom-side cylinder chamber 8, so that the piston of the Cylinder is extended.
  • the pressure medium displaced from the annular space 10 flows via the return line 4, the return channel 32, the outlet cross section of the directional control valve 14, the drainage channel 44 and the tank channel 46 to the tank connection T and from there to the tank.
  • the individual pressure compensator 40 the pressure drop across the metering orifice 26 is kept constant independent of the load, so that even with changes in the load pressure, a constant extension speed of the hydraulic cylinder 6 is ensured.
  • the degree of opening of the two valve spool of the directional control valves 12, 14 is controlled by means of the self-adjusting and via the pressure sensors 35 and 37 detected load pressures.
  • the respectively effective inlet orifice 26 (or 28) is opened in accordance with the valve flow rate preset by the user, and thus a fixed preselected pressure medium volume flow is supplied.
  • the opening of the valve slide located in the return is realized by an adapted connection of the opening of the inlet orifice 26 in the sense of a politicianssisten.
  • the current load pressure of the pressure medium volume flow flowing to the consumer is monitored.
  • the pump-side arrangement of the individual pressure compensator 40 has opposite consumer-side individual pressure compensators (LUDV systems) the advantage that only a single pressure balance must be provided, thus the solution of the invention is much simpler structure than the LUDV systems described above.
  • LUDV systems consumer-side individual pressure compensators
  • valve concept explained with reference to the figure also makes it possible to connect two single-acting consumers to the connections A, B and to operate them separately.
  • the control block does not necessarily have to be implemented as an LS control block.
  • the pump can be a variable displacement pump or a fixed displacement pump with bypass pressure compensator.
  • a hydraulic control arrangement for controlling a hydraulic consumer and executed with at least one such control device mobile control block, wherein in the flow to the consumer and in the return from the consumer in each case a valve spool for adjusting the inlet or outlet cross section is arranged. Both valve spools are preceded on the pump side by an individual pressure balance, via which the pressure medium flows to an inlet orifice plate controlled by one of the valve spools.

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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)
  • Vehicle Cleaning, Maintenance, Repair, Refitting, And Outriggers (AREA)
  • Magnetically Actuated Valves (AREA)

Claims (10)

  1. Ensemble de commande hydraulique destiné à commander un récepteur (6) hydraulique avec un ensemble de distributeur à plusieurs voies réglable en permanence (12, 14) qui possède un tiroir de distributeur d'arrivée pour le réglage d'un débit volumique de fluide hydraulique vers le récepteur et un tiroir de distributeur de retour, par le biais duquel la section de retour pour le débit volumique de fluide hydraulique sortant du récepteur (6) peut être réglée, les deux tiroirs de distributeur étant séparés, caractérisé en ce qu'un compensateur de pression individuel (40) commun est monté en amont des deux tiroirs de distributeur côté pompe, par le biais duquel le fluide hydraulique s'écoule vers un orifice de mesure d'alimentation (26, 28) actionné par l'un des tiroirs de distributeur.
  2. Ensemble de commande hydraulique selon la revendication 1, dans lequel les positions des tiroirs de distributeur sont réglées indépendamment l'une de l'autre.
  3. Ensemble de commande hydraulique selon la revendication 1 ou 2, dans lequel les tiroirs de distributeur sont disposés dans un distributeur à plusieurs voies respectif (12, 14), dont le raccordement de pression (P) est relié à un raccordement de sortie (C) du compensateur de pression individuel (40).
  4. Ensemble de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel le compensateur de pression individuel (40) est sollicité dans le sens de fermeture par une pression en amont de l'orifice de mesure (26, 28) respectif et dans le sens d'ouverture par la force d'un ressort de compensateur de pression (58) et la pression de charge du récepteur (6).
  5. Ensemble de commande hydraulique selon la revendication 4, dans lequel la pression de charge est prélevée par le biais d'un distributeur à deux voies (52) de l'arrivée au récepteur (6) et du retour au récepteur (6).
  6. Ensemble de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel un capteur de pression (35, 37) est respectivement disposé dans l'arrivée et dans le retour.
  7. Ensemble de commande hydraulique selon l'une quelconque des revendications liées à la revendication 3, dans lequel les distributeurs à plusieurs voies (12, 14) possèdent chacun un raccordement de pression (P), un raccordement de réservoir (R) et un raccordement de travail (A, B) ainsi qu'un raccordement LS (LS).
  8. Ensemble de commande hydraulique selon l'une quelconque des revendications précédentes, avec une unité de commande, par le biais de laquelle un signal de réduction de la section de retour peut être émis aux distributeurs à plusieurs voies (12, 14), si la pression de l'arrivée baisse sous une valeur seuil, de préférence sous la pression du retour.
  9. Unité de commande hydraulique selon la revendication 8, dans laquelle la section d'ouverture côté retour est complètement actionnée par l'unité de commande au cas où la pression de l'arrivée est nettement supérieure à celle du retour.
  10. Bloc de commande destiné à commander plusieurs récepteurs, un ensemble de commande selon l'une quelconque des revendications précédentes étant associé à chaque récepteur.
EP06007227A 2005-04-05 2006-04-05 Commande hydraulique et bloc de commande Not-in-force EP1710446B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005015689 2005-04-05
DE102005022891A DE102005022891A1 (de) 2005-04-05 2005-05-18 Hydraulische Steueranordnung und Steuerblock

Publications (3)

Publication Number Publication Date
EP1710446A2 EP1710446A2 (fr) 2006-10-11
EP1710446A3 EP1710446A3 (fr) 2007-03-21
EP1710446B1 true EP1710446B1 (fr) 2008-12-24

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06007227A Not-in-force EP1710446B1 (fr) 2005-04-05 2006-04-05 Commande hydraulique et bloc de commande

Country Status (3)

Country Link
EP (1) EP1710446B1 (fr)
AT (1) ATE418683T1 (fr)
DE (2) DE102005022891A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009047035A1 (de) * 2009-11-24 2011-06-09 Technische Universität Dresden Steuerungssystem mit aufgelösten Steuerkanten

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007054134A1 (de) * 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102011114241B4 (de) * 2011-06-09 2014-09-04 Sms Meer Gmbh Hydraulische Antriebsvorrichtung, Hydraulische Endstufe eines hydraulischen Servo-Regelventils, Servo-Regelventil und Pulverpresse
US10337532B2 (en) 2016-12-02 2019-07-02 Caterpillar Inc. Split spool valve
US10947997B2 (en) 2018-04-13 2021-03-16 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
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EP1710446A2 (fr) 2006-10-11
DE102005022891A1 (de) 2006-10-12
ATE418683T1 (de) 2009-01-15
EP1710446A3 (fr) 2007-03-21
DE502006002405D1 (de) 2009-02-05

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