EP1710446A2 - Hydraulic control device and control block - Google Patents

Hydraulic control device and control block Download PDF

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Publication number
EP1710446A2
EP1710446A2 EP06007227A EP06007227A EP1710446A2 EP 1710446 A2 EP1710446 A2 EP 1710446A2 EP 06007227 A EP06007227 A EP 06007227A EP 06007227 A EP06007227 A EP 06007227A EP 1710446 A2 EP1710446 A2 EP 1710446A2
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EP
European Patent Office
Prior art keywords
pressure
valve
return
consumer
hydraulic control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06007227A
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German (de)
French (fr)
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EP1710446A3 (en
EP1710446B1 (en
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 of EP1710446A2 publication Critical patent/EP1710446A2/en
Publication of EP1710446A3 publication Critical patent/EP1710446A3/en
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Publication of EP1710446B1 publication Critical patent/EP1710446B1/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05Systems 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042Systems 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"
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044Systems 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"
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30525Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053In combination with a pressure compensating valve
    • F15B2211/30535In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/3056Assemblies of multiple valves
    • F15B2211/30565Assemblies 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/3056Assemblies of multiple valves
    • F15B2211/30565Assemblies 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
    • F15B2211/3057Assemblies 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/35Directional control combined with flow control
    • F15B2211/351Flow control by regulating means in feed line, i.e. meter-in control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/35Directional control combined with flow control
    • F15B2211/353Flow control by regulating means in return line, i.e. meter-out control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/505Pressure control characterised by the type of pressure control means
    • F15B2211/50563Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572Pressure 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/57Control of a differential pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/63Electronic controllers
    • F15B2211/6303Electronic controllers using input signals
    • F15B2211/6306Electronic controllers using input signals representing a pressure
    • F15B2211/6313Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/63Electronic controllers
    • F15B2211/6303Electronic controllers using input signals
    • F15B2211/634Electronic controllers using input signals representing a state of a valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/665Methods of control using electronic components
    • F15B2211/6654Flow rate control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/60Circuit components or control therefor
    • F15B2211/665Methods of control using electronic components
    • F15B2211/6658Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051Linear output members
    • F15B2211/7053Double-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 respective 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.
  • each valve spool ie, both the inlet side and the outlet side of a LUDV pressure compensator downstream, in the closing direction of the respective load pressure is charged.
  • 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 valve slides which can be controlled separately, 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 disk 1 of a mobile control block, via which a consumer can be controlled.
  • the dashed lines indicated valve disk 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.

Abstract

The arrangement has a continuous adjustable solenoid valve arrangement with a forward motion valve gate to adjust a pressurizing medium flow rate to a load. A reverse motion cross section is adjustable for the flow rate diverting from the load by the reverse motion valve gate. Pump side of valve gates upstream a common individual pressure scale, over which pressurizing medium flows to an inlet orifice controlled by one of the gates. An independent claim is also included for a control block for controlling several loads.

Description

Die Erfindung betrifft eine hydraulische Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers gemäß dem Oberbegriff des Patentanspruchs 1 und einen Steuerblock zur Ansteuerung mehrerer Verbraucher, wobei jedem Verbraucher eine derartige Steueranordnung zugeordnet ist.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.

Die Bewegungssteuerung hydraulischer Verbraucher von mobilen Arbeitsgeräten erfolgt in der Regel über Proportionalwegeventile, über die die Druckmittelströmungsrichtung und der Druckmittelvolumenstrom zum und vom Verbraucher einstellbar ist. Ein Problem in der Mobilhydraulik sind sogenannte ziehende Lasten, bei der die Last in Bewegungsrichtung des Verbrauchers wirkt. Dies kann beispielsweise bei einem Hydraulikzylinder vorkommen, wenn die Kolbenstange ausgefahren wird und die ziehende Last in Richtung der Ausfahrbewegung wirkt. Dabei kann es zu einer Unterversorgung des unbelasteten Zylinderraums, d. h., bei der Ausfahrbewegung der Kolbenstange zu einer Unterversorgung des bodenseitigen Zylinderraums kommen, so dass in diesem Kavitationen auftreten können, über die der Hydraulikzylinder oder die Steueranordung geschädigt wird.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.

Üblicherweise werden zur vermeidung einer Unterversorgung von hydraulischen Verbrauchern sogenannte Senkbremsventile eingesetzt. Derartige Senkbremsventile sind drosselnde Ventile, die den vom Verbraucher abströmenden Druckmittelvolumenstrom eines Druckraums in Abhängigkeit vom Druck in dem zweiten, sich vergrößernden Druckraum regeln. Problematisch ist dabei das gegenseitige Beeinflussen der Drücke in den beiden Druckräumen bei gleichzeitiger schlechter Dämpfung. Weiterhin ist eine Bewegungssteuerung des Verbrauchers mit hoher Dynamik nur begrenzt möglich, die Abstimmung der Ventile ist in der Praxis äußerst problematisch. Die Abstimmung der Ventile sollte im Allgemeinen zusammen mit den jeweils angeschlossenen Verbrauchern erfolgen, so dass keine Möglichkeit besteht, mit einer universellen Senkbremseinheit beliebige Verbraucher zu betreiben.Usually so-called 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. Furthermore, 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 respective connected consumers, so that there is no possibility to operate with a universal lowering brake arbitrary consumers.

In der US 5,138,838 ist eine Steueranordnung offenbart, bei der dem Zulauf und dem Ablauf getrennte Wegeventilschieber zur Einstellung eines Zulaufquerschnitts und eines Ablaufquerschnitts zugeordnet sind. Die Ansteuerung der beiden Ventilschieber erfolgt unabhängig voneinander über Pilotdruckreduzierventile, die in Abhängigkeit von den Drücken im Vorlauf zum und im Rücklauf vom Verbraucher angeordnet sind. Der Verbraucher ist bei der in der US 5, 138,838 gezeigten Lösung ein doppeltwirkender Hydraulikzylinder. Im Falle einer ziehenden Last wird der Druckabfall in der Vorlaufleitung über den Drucksensor erfasst und im Fall einer Unterversorgung, d. h., dann wenn der Druck im Rücklauf höher als derjenige im Vorlauf ist, der Rücklaufquerschnitt über den im Rücklauf angeordneten Ventilschieber angedrosselt, so dass eine Unterversorgung des sich vergrößernden Druckraums verhindert werden kann.In the US 5,138,838 a control arrangement is disclosed, 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. In the case of a towing load, 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.

In der EP 0 809 737 ist eine ähnlich aufgebaute Lösung offenbart, bei der der Druckmittelvolumenstrom im Zulauf und im Ablauf über getrennte, elektrohydraulisch vorgesteuerte Ventilschieber steuerbar ist.In the EP 0 809 737 a similarly constructed solution is disclosed in which the pressure medium volume flow in the inlet and in the drain via separate, electro-hydraulically pilot operated valve spool is controllable.

Nachteilig bei diesen bekannten Lösungen ist, dass bei Änderungen des Lastdrucks eine sehr schnelle Reaktion der Regelung für die beiden Ventilschieber erforderlich ist, um die Geschwindigkeit des Verbrauchers konstant zu halten.A disadvantage of these known solutions is that changes in the load pressure requires a very fast reaction of the control for the two valve spools is to keep the speed of the consumer constant.

In der US 6,073,652 ist eine Steueranordnung offenbart, bei der ebenfalls die Einstellung des Zulauf- und Ablaufquerschnitts über getrennte Ventilschieber (aufgelöste Steuerkanten) erfolgt, wobei jedem Ventilschieber, d. h., sowohl dem zulaufseitigen als auch dem ablaufseitigen eine LUDV-Druckwaage nachgeschaltet ist, die in Schließrichtung vom jeweiligen Lastdruck beaufschlagt ist.In the US 6,073,652 a control arrangement is disclosed, in which also the adjustment of the inlet and outlet cross section via separate valve spool (dissolved control edges) takes place, each valve spool, ie, both the inlet side and the outlet side of a LUDV pressure compensator downstream, in the closing direction of the respective load pressure is charged.

Eine derartige Lösung erfordert einen erheblichen vorrichtungstechnischen Aufwand.Such a solution requires considerable device complexity.

In der WO 02/075162 A1 ist anhand der Figuren 12 und 13 eine Steueranordnung erläutert, bei der zulauf- und ablaufseitig jeweils ein Ventilschieber vorgesehen ist, denen jeweils eine LUDV-Druckwaage nachgeschaltet ist. Auch bei dieser Lösung ist der vorrichtungstechnische Aufwand erheblich.In the WO 02/075162 A1 is explained with reference to Figures 12 and 13, a control arrangement in which each inlet and outlet side a valve spool is provided, each of which a LUDV pressure compensator is connected downstream. Also in this solution, the device complexity is considerable.

Die US 5,568,759 offenbart ebenfalls eine Steueranordnung mit getrennten Ventilschiebern in Vorlauf und Rücklauf. Auch bei dieser Lösung muss regelungstechnisch ein hoher Aufwand getrieben werden, um im Fall einer Laständerung den Querschnitt der Ventilschieber so zu verstellen, dass die Geschwindigkeit des Verbrauchers konstant bleibt.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.

Dem gegenüber liegt der Erfindung die Aufgabe zugrunde, eine hydraulische Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers und einen Steuerblock mit mehreren derartigen Steueranordnungen zu schaffen, bei denen mit geringem vorrichtungstechnischen Aufwand im Fall einer ziehenden Last eine Unterversorgung verhindert werden kann und darüber hinaus auch bei Laständerungen eine konstante Bewegungsgeschwindigkeit des angesteuerten Verbrauchers gewährleistet ist.On the other hand, 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.

Diese Aufgabe wird hinsichtlich der hydraulischen Steueranordnung durch die Merkmalskombination des Patentanspruchs 1 und hinsichtlich des Steuerblocks durch die Merkmale des Patentanspruchs 10 gelöst.This object is achieved with regard to the hydraulic control arrangement by the combination of features of claim 1 and with respect to the control block by the features of claim 10.

Erfindungsgemäß wird der Druckmittelvolumenstrom im Vorlauf und im Rücklauf über jeweils getrennt voneinander ansteuerbare Ventilschieber eingestellt, denen pumpenseitig eine Individualdruckwaage zugeordnet ist, über die das Druckmittel zu einer von einem der Ventilschieber aufgesteuerten Zumessblende strömt.According to the invention, the pressure medium volume flow in the flow and in the return is adjusted via valve slides which can be controlled separately, 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.

Über die beiden Ventilschieber ist es möglich, einen unterversorgungsfreien Vier-Quadrantenbetrieb des Verbrauchers bei freier Wahl des Flächen- bzw. Druckmittelvolumenstromverhältnisses zu gewährleisten. Es müssen keine die Dynamik vermindernde Drosseleinrichtungen zwischen dem Ventilschieber und dem Verbraucher vorgesehen werden, wobei durch das Zusammenwirken der Zumessblende und der dieser vorgeschalteten Individualdruckwaage der Druckabfall über der Zumessblende lastunabhängig konstant gehalten werden kann, so dass der Verbraucher auch bei Änderungen des Lastdrucks mit konstanter Geschwindigkeit verfahren werden kann.About the two valve spool, it is possible to ensure a lack of supply four-quadrant operation of the consumer with free choice of area or pressure medium volume flow ratio. There must be no dynamics reducing throttle devices between the valve spool and the consumer are provided, the pressure drop across the metering orifice can be kept constant independent of load by the interaction of the metering and the upstream of this pressure gauge, so that the consumer even with changes in load pressure at a constant speed can be moved.

In dem Fall, in dem der Druck im Vorlauf unter einen vorbestimmten Wert abfällt, kann über den im Rücklauf angeordneten Ventilschieber der Ablaufquerschnitt verringert werden, so dass durch dieses Androsseln des Rücklaufs eine Unterversorgung des unbelasteten Druckraums des Verbrauchers verhindert werden kann.In the case in which the pressure drops in the flow below a predetermined value, can be reduced via the arranged in the return valve spool, the flow area, so that by this throttling of the return a shortage of the unloaded pressure chamber of the consumer can be prevented.

Erfindungsgemäß wird es besonders bevorzugt, wenn die beiden Wegeventilschieber unabhängig voneinander lagegeregelt sind.According to the invention it is particularly preferred if the two-way valve spool are independently position-controlled.

Die beiden Ventilschieber können jeweils in einem elektrohydraulisch vorgesteuerten Wegeventil angeordnet werden, deren Druckanschlüsse mit einem Ausgang der gemeinsamen Individualdruckwaage verbunden sind.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.

Diese Individualdruckwaage wird vorzugsweise in Schließrichtung von einem Druck stromaufwärts der jeweils wirksamen Zumessblende und in Öffnungsrichtung von der Kraft einer Druckwaagenfeder und dem Lastdruck des zugeordneten Verbrauchers beaufschlagt.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.

Dieser Lastdruck kann über ein Wechselventil vom Vorlauf zum und vom Rücklauf vom Verbraucher abgegriffen werden.This load pressure can be tapped via a shuttle valve from the flow to and from the return from the consumer.

Im Vorlauf und im Rücklauf kann jeweils ein Drucksensor angeordnet werden, so dass auf einfache Weise erfasst werden kann, wenn der Druck im Vorlauf einen vorbestimmten Schwellwert unterschreitet.In the flow and in the return, 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.

Die die Ventilschieber aufnehmenden Wegeventile sind bei einem bevorzugten Ausführungsbeispiel mit einem Druckanschluss, einem Tankanschluss, einem Arbeitsanschluss sowie ein LS-Anschluss ausgeführt.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.

Bei einem bevorzugten Ausführungsbeispiel ist die Steueranordnung mit einer Steuereinheit ausgeführt, über die das im Rücklauf angeordnete Wegeventil so angesteuert wird, dass beim Abfallen des Drucks im Vorlauf unter den vorgenannten Stellwert der Rücklaufquerschnitt verringert wird. Dadurch wird der ablaufende Druckmittelvolumenstrom angedrosselt und entsprechend eine Unterversorgung verhindert.In a preferred embodiment, the 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. As a result, the running pressure medium volume flow throttled and prevented accordingly a shortage.

In dem Fall, in dem eindeutig eine drückende Last vorliegt, d. h., wenn eine ziehende Last ausgeschlossen werden kann, kann die Ablaufmessblende zur Minimierung der Druckverluste vollständig aufgesteuert werden.In the case where there is clearly an oppressive load, i. That is, if a pulling load can be excluded, the drain orifice can be fully opened to minimize pressure losses.

Der erfindungsgemäße LS-Steuerblock zur Ansteuerung mehrerer Verbraucher weist mehrere Ventilscheiben mit der Steueranordnung gemäß Patentanspruch 1 auf.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.

Sonstige vorteilhafte Weiterbildungen der Erfindung sind Gegenstand sonstiger Unteransprüche.Other advantageous developments of the invention are the subject of other dependent claims.

Im Folgenden wird ein bevorzugtes Ausführungsbeispiel der Erfindung anhand einer einzigen Figur erläutert, die einen stark vereinfachten Hydraulikschaltplan einer erfindungsgemäßen Steueranordnung zeigt. Eine derartige Steueranordnung kann beispielsweise durch eine Ventilscheibe 1 eines Mobilsteuerblocks realisiert sein, über die ein Verbraucher ansteuerbar ist. Die gestrichelt angedeutete Ventilscheibe 1 hat einen Druckanschluss P, einen Tankanschluss T sowie zwei Arbeitsanschlüsse A, B, die über eine Vorlaufleitung 2 bzw. eine Rücklaufleitung 4 mit einem hydraulischen Verbraucher 6 verbunden sind, der beim dargestellten Ausführungsbeispiel als doppeltwirkender Hydraulikzylinder ausgeführt ist. Die Vorlaufleitung 2 ist dabei an einen bodenseitigen Zylinderraum 8 und die Rücklaufleitung 4 an einen Ringraum des Zylinders 6 angeschlossen.In the following, a preferred embodiment of the invention will be explained with reference to a single figure, which shows a highly simplified hydraulic circuit diagram of a control arrangement according to the invention. Such a control arrangement can be realized for example by a valve disc 1 of a mobile control block, via which a consumer can be controlled. The dashed lines indicated valve disk 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.

In der Ventilscheibe 1 sind zwei Wegeventileinheiten, im Folgenden Wegeventile 12, 14 genannt, ausgebildet, die jeweils einen Druckanschluss P, einen Rücklaufanschluss R und einen Arbeitsanschluss A bzw. B aufweisen. Prinzipiell können diese Wegeventileinheiten auch in einer gemeinsamen Ventilbohrung der Ventilscheibe aufgenommen sein. Das heißt, die Wegeventile müssen nicht getrennte Bauelemente sein, sondern können auch in ein Gehäuse oder dergleichen integriert sein.In the 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. in principle These directional control valve units 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.

Jedes der Wegeventile 12, 14 ist über elektrohydraulisch Vorsteuerventile 16, 18 bzw. 20, 22 aus seiner dargestellten Grundposition, in der die Anschlüsse P, R, A gegeneinander abgesperrt sind in Arbeitsstellungen (a) oder (b) zu verstellen. In den Positionen (a) ist der jeweilige Druckanschluss P mit dem zugeordneten Arbeitsanschluss A bzw. B verbunden, der Rücklaufanschluss R ist abgesperrt - es wird eine Zumessblende 26 bzw. 28 aufgesteuert, die den Druckmittelvolumenstrom zum Verbraucher 6 und damit dessen Geschwindigkeit bestimmt. Außerdem ist der jeweilige Arbeitsanschluss A bzw. B mit dem LS-Anschluss verbunden.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. In the positions (a) of the respective pressure port P is connected to the associated working port A and B, 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. In addition, the respective working port A or B is connected to the LS port.

In den mit (b) gekennzeichneten Arbeitspositionen sind die beiden Arbeitsanschlüsse A oder B mit dem Rücklaufanschluss R verbunden, der Druckanschluss P ist jeweils abgesperrt. Der jeweilige Ventilschieber steuert dann einen Ablaufquerschnitt auf.In the working positions marked with (b), the two working ports A or B are connected to the return port R, the pressure port P is shut off in each case. The respective valve slide then controls a flow cross-section.

Wie der Figur entnehmbar ist, ist der Anschluss A des Wegeventils 12 über einen Vorlaufkanal 30 und der Anschluss B des Wegeventils 14 über einen Rücklaufkanal 32 mit dem Arbeitsanschluss B der Ventilscheibe 1 verbunden. Sowohl im Vorlaufkanal 30 als auch im Rücklaufkanal 32 ist jeweils ein Drucksensor 35 bzw. 37 vorgesehen, über den der Druck im jeweiligen Kanal erfassbar ist. Dieser Druck entspricht dem Lastdruck des Verbrauchers.As the figure can be seen, 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.

An den Druckanschluss P der beiden parallel geschalteten Wegeventile 12, 14 ist jeweils ein Zulaufkanal 34, 36 angeschlossen. Beide Zulaufkanäle 34, 36 münden in einen gemeinsamen Pumpenkanal 38 ein, der an den Ausgang C einer Individualdruckwaage 40 angeschlossen ist. Ein Eingangsanschluss P der Individualdruckwaage 40 ist über die Pumpenleitung 38 mit dem Druckanschluss P der Ventilscheibe 1 verbunden. An die beiden Rücklaufanschlüsse R der Wegeventile 12, 14 ist jeweils ein Ablaufkanal 42, 44 angeschlossen. Beide Ablaufkanäle 42, 44 münden in einer mit dem Tankanschluss T der Ventilscheibe 1 verbundenen Tankkanal 46. Die beiden Wegeventile 12, 14 haben - wie erwähnt - jeweils einen LS-Anschluss, dieser ist über jeweils einen LS-Zweigkanal 48, 50 mit dem Eingang eines Wechselventils 52 verbunden, dessen Ausgang über einen LS-Kanal 54 an den LS-Anschluss der Ventilscheibe 1 angeschlossen ist. Die Individualdruckwaage 40 ist in Schließrichtung von einem Druck stromaufwärts der beiden Zumessblenden 26, 28, im vorliegenden Fall vom Druck zwischen dem Druckanschluss P der Ventilscheibe 1 und dem Eingangsanschluss P der Individualdruckwaage 40 beaufschlagt. Dieser in Schließrichtung wirksame Steuerdruck wird über eine von der Pumpenleitung 38 abzweigende Steuerleitung 56 an eine in Schließrichtung wirksame Steuerfläche des Druckwaagenkolbens angelegt. In Öffnungsrichtung wirkt auf den Druckwaagenkolben die Kraft einer Druckwaagenfeder 58 und der Lastdruck im LS-Kanal, der über einen LS-Zweigkanal 60 zu einer in Öffnungsrichtung wirksamen Steuerfläche des Druckwaagenkolbens geführt ist.To the pressure port P of the two parallel-way valves 12, 14 is in each case an inlet channel 34, 36 connected. Both inlet channels 34, 36 open into a common pump channel 38 which is connected to the output C of an individual pressure compensator 40. An input port P of the individual pressure compensator 40 is connected via the pump line 38 to the pressure port P of the valve disc 1. To the two return ports R of the directional control valves 12, 14, a respective flow channel 42, 44 is connected. Both drainage channels 42, 44 open into a connected to the tank port T of the valve disc 1 tank channel 46. 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.

Der höchste Lastdruck aller Ventilscheiben 1 des Mobilsteuerblocks wird über eine Wechselventilkaskade (nicht dargestellt) abgegriffen und zum Pumpenregler einer Verstellpumpe geführt, die derart angesteuert wird, dass in der Pumpenleitung 38 stets ein Druck anliegt, der um ein vorbestimmtes Pumpen-Δp über diesem höchsten Lastdruck liegt (LS-Steuerung).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 Δp above this highest load pressure is (LS control).

Die beiden Wegeventile 12, 14 sind jeweils mit einer Lageregelung (nicht dargestellt) ausgeführt, über die der Öffnungsquerschnitt der Zumessblenden und der Ablaufquerschnitte (je nach Durchströmungsrichtung) exakt regelbar ist.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.

Zum Ausfahren des Zylinders 6 wird das Wegeventil 12 in eine seiner mit (a) und das Wegeventil 14 in eine seiner (b) gekennzeichneten Positionen verstellt. Das Druckmittel wird dann von der Pumpe über den Druckanschluss P der Ventilscheibe 1, die Pumpenleitung 38, die Individualdruckwaage 40, den Zulaufkanal 34, die Zumessblende 26, den Vorlaufkanal 30 und die Vorlaufleitung 2 in den bodenseitigen Zylinderraum 8 gefördert, so dass der Kolben des Zylinders ausgefahren wird. Das aus dem Ringraum 10 verdrängte Druckmittel strömt über die Rücklaufleitung 4, den Rücklaufkanal 32, den Ablaufquerschnitt des Wegeventils 14, den Ablaufkanal 44 und den Tankkanal 46 zum Tankanschluss T und von dort zum Tank hin ab. Über die Individualdruckwaage 40 wird der Druckabfall über der Zumessblende 26 lastunabhängig konstant gehalten, so dass auch bei Änderungen des Lastdrucks eine konstante Ausfahrgeschwindigkeit des Hydraulikzylinders 6 gewährleistet ist.To extend the cylinder 6, 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. About 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.

Mit Hilfe eines Steuerungs- und Regelkonzepts wird der Öffnungsgrad der beiden Ventilschieber der Wegeventile 12, 14 mit Hilfe der sich einstellenden und über die Drucksensoren 35 und 37 erfassten Lastdrücke geregelt. Dabei wird bei Ansteuerung des Verbrauchers 6 die jeweils wirksame Zulaufmessblende 26 (oder 28) entsprechend der durch den Benutzer vorgegebenen Ventildurchfluss-Sollgröße geöffnet und somit ein fest vorgegebener Druckmittelvolumenstrom zugeführt. Die Öffnung des im Rücklauf gelegenen Ventilschiebers (im vorliegenden Wegeventil 14) wird durch eine angepasste Aufschaltung der Öffnung der Zulaufmessblende 26 im Sinne einer Führungsgrößenaufschaltung realisiert. Zusätzlich wird der aktuelle Lastdruck des zum Verbraucher strömenden Druckmittelvolumenstroms überwacht. Sinkt nun aufgrund einer ziehenden Last (Pfeil am Verbraucher 6) der Lastdruck im Zylinderraum 8 und damit im Vorlaufkanal 30 unterhalb einen in der Steuereinheit abgespeicherten Schwellwert ab, so erfolgt aufgrund eines Signals der Steuereinheit über das Wegeventil 14 eine zusätzliche Androsselung des vom Ringraum 10 abströmenden Druckmittelvolumenstroms durch Verkleinerung des Öffnungsquerschnitts des Wegeventils 14 - der ablaufende Druckmittelvolumenstrom wird angedrosselt und eine Unterversorgung des Zylinderraums 8 und dadurch auftretende Kavitationen werden verhindert.With the help of a control and regulating concept, 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. In this case, upon actuation of the consumer 6, 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 (in the present directional valve 14) is realized by an adapted connection of the opening of the inlet orifice 26 in the sense of a Führungsgrößenaufschaltung. In addition, the current load pressure of the pressure medium volume flow flowing to the consumer is monitored. If, due to a pulling load (arrow on the consumer 6), the load pressure in the cylinder chamber 8 and thus in the supply channel 30 drops below a threshold value stored in the control unit, an additional throttling of the effluent from the annular space 10 occurs due to a signal from the control unit via the directional control valve 14 Pressure medium volume flow by reducing the opening cross-section of the directional control valve 14 - the running pressure medium flow is throttled and a shortage of the cylinder chamber 8 and thereby occurring cavitations are prevented.

Beim Einfahren des Hydraulikzylinders 6 erfolgt ein Wechsel der Regelungsstrategie, da die beiden Wegeventile 12, 14 dann ihre Funktion als Zumess- und Ablaufmessblende wechseln.When retracting the hydraulic cylinder 6, there is a change in the control strategy, since the two-way valves 12, 14 then change their function as a metering and drain metering orifice.

Durch die guten dynamischen Eigenschaften der Individualdruckwaage 40 ist es möglich, mit Hilfe eines konventionellen Schieberventils vergleichsweise geringer Dynamik die Regelung des Drucks auf der Zulaufseite zu betreiben. Die pumpenseitige Anordnung der Individualdruckwaage 40 hat gegenüber verbraucherseitigen Individualdruckwaagen (LUDV-Systeme) den Vorteil, dass nur eine einzige Druckwaage vorgesehen werden muss, dadurch ist die erfindungsgemäße Lösung wesentlich einfacher aufgebaut als die eingangs beschriebenen LUDV-Systeme.Due to the good dynamic properties of the individual pressure compensator 40, it is possible to operate with the help of a conventional spool valve comparatively low dynamics, the regulation of the pressure on the inlet side. 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.

In dem Fall, in dem die Last eindeutig der Bewegung des Zylinders entgegenwirkt (drückende Last) ist eine Verringerung der Druckverluste durch eine vollständige Öffnung der im Rücklauf gelegenen Steuerkante des Wegeventils 14 (oder bei Umkehrung der Druckmittelvolumenstromrichtung des Wegeventils 12) möglich.In the case where the load clearly opposes the movement of the cylinder (pushing load), a reduction in the pressure losses is due to a complete opening of the return control edge of the directional control valve 14 (or upon reversal of the pressure medium flow direction of the directional control valve 12) possible.

Das anhand der Figur erläuterte Ventilkonzept ermöglicht es auch, zwei einfach wirkende Verbraucher an die Anschlüsse A, B anzuschließen und separat zu betreiben.The 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.

Der Steuerblock muss nicht notwendigerweise als LS-Steuerblock ausgeführt sein. Die Pumpe kann eine Verstellpumpe oder eine Konstantpumpe mit Bypassdruckwaage sein.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.

Offenbart sind eine hydraulische Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers und ein mit zumindest einer derartigen Steueranordnung ausgeführter Mobilsteuerblock, wobei im Vorlauf zum Verbraucher und im Rücklauf vom Verbraucher jeweils ein Ventilschieber zur Einstellung des Zulauf- bzw. Ablaufquerschnitts angeordnetist. Beiden Ventilschiebern ist pumpenseitig eine Individualdruckwaage vorgeschaltet, über die das Druckmittel zu einer von einem der Ventilschieber aufgesteuerten Zulaufmessblende strömt.Disclosed are 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.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Ventilscheibevalve disc
22
Vorlaufleitungsupply line
44
RücklaufleitungReturn line
66
Zylindercylinder
88th
Zylinderraumcylinder space
1010
Ringraumannulus
1212
Wegeventilway valve
1414
Wegeventilway valve
1616
Vorsteuerventilpilot valve
1818
Vorsteuerventilpilot valve
2020
Vorsteuerventilpilot valve
2222
Vorsteuerventilpilot valve
2424
Vorsteuerventilpilot valve
2626
Zumessblendemetering orifice
2828
Zumessblendemetering orifice
3030
Vorlaufkanalforward channel
3232
RücklaufkanalReturn channel
3434
Zulaufkanalinlet channel
3535
Drucksensorpressure sensor
3636
Zulaufkanalinlet channel
3737
Drucksensorpressure sensor
3838
Pumpenleitungpump line
4040
IndividualdruckwaageIndividual pressure compensator
4242
Ablaufkanaldrain channel
4444
Ablaufkanaldrain channel
4646
Tankkanaltank channel
4848
LS-ZweigkanalLS branch channel
5050
LS-ZweigkanalLS branch channel
5252
Wechselventilshuttle valve
5454
LS-KanalLS-channel
5656
Steuerleitungcontrol line
5858
DruckwaagenfederCompensator spring
6060
LS-ZweigkanalLS branch channel

Claims (10)

Hydraulische Steueranordnung zur Ansteuerung eines hydraulischen Verbrauchers (6), mit einer stetig verstellbaren Wegeventilanordnung (12, 14), die einen Vorlauf-Ventilschieber zum Einstellen eines Druckmittelvolumenstroms zum Verbraucher und einen Rücklauf-Ventilschieber hat, über den der Rücklaufquerschnitt für den vom Verbraucher (6) abströmenden Druckmittelvolumenstrom einstellbar ist, dadurch gekennzeichnet, dass beiden Ventilschiebern pumpenseitig eine gemeinsame Individualdruckwaage (40) vorgeschaltet ist, über die Druckmittel zu einer von einem der Ventilschieber aufgesteuerten Zulaufmessblende (26, 28) strömt.Hydraulic control arrangement for controlling a hydraulic consumer (6), with a continuously adjustable directional control valve arrangement (12, 14), which has a flow valve spool for adjusting a pressure medium volume flow to the consumer and a return valve spool over which the return cross section for the consumer (6 ) is adjustable, characterized in that the two valve spools on the pump side, a common individual pressure compensator (40) is connected upstream of the pressure medium to a controlled by one of the valve spool inlet orifice meter (26, 28) flows. Hydraulische Steueranordnung, wobei die ventilschieber unabhängig voneinander lagegeregelt sind.Hydraulic control arrangement, wherein the valve spool are independently position-controlled. Hydraulische Steueranordnung nach Patentanspruch 1 oder 2, wobei die Ventilschieber in jeweils einem Wegeventil (12, 14) angeordnet sind, dessen Druckanschluss (P) mit einem Ausgangsanschluss (C) der Individualdruckwaage (40) verbunden ist.Hydraulic control arrangement according to claim 1 or 2, wherein the valve slide in each case a directional control valve (12, 14) are arranged, the pressure port (P) with an output terminal (C) of the individual pressure compensator (40) is connected. Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, wobei die Individualdruckwaage (40) in Schließrichtung von einem Druck stromaufwärts der jeweiligen Zumessblende (26, 28) und in Öffnungsrichtung von der Kraft einer Druckwaagenfeder (58) und dem Lastdruck des Verbrauchers (6) beaufschlagt ist.Hydraulic control arrangement according to one of the preceding claims, wherein the individual pressure compensator (40) in the closing direction of a pressure upstream of the respective metering orifice (26, 28) and in the opening direction of the force of a pressure compensator spring (58) and the load pressure of the consumer (6) is acted upon. Hydraulische Steueranordnung nach Patentanspruch 4, wobei der Lastdruck über ein Wechselventil (52) vom Vorlauf zum Verbraucher (6) und vom Rücklauf vom Verbraucher (6) abgegriffen ist.Hydraulic control arrangement according to claim 4, wherein the load pressure via a shuttle valve (52) from Supply to the consumer (6) and from the return from the consumer (6) is tapped. Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, wobei im Vorlauf und im Rücklauf jeweils ein Drucksensor (35, 37) angeordnet ist.Hydraulic control arrangement according to one of the preceding claims, wherein in each case a pressure sensor (35, 37) is arranged in the flow and in the return. Hydraulische Steueranordnung nach einem der auf Patentanspruch 3 zurückbezogenen Patentansprüche, wobei die Wegeventile (12, 14) jeweils einen Druckanschluss (P), einen Tank (R) und einen Arbeitsanschluss (A, B) sowie einen LS-Anschluss (LS) haben.Hydraulic control arrangement according to one of the claims back to claim 3, wherein the directional control valves (12, 14) each have a pressure port (P), a tank (R) and a working port (A, B) and an LS port (LS). Hydraulische Steueranordnung nach einem der vorhergehenden Patentansprüche, mit einer Steuereinheit, über die an die Wegeventile (12, 14) ein Signal zum Verringern des Rücklaufquerschnitts abgebbar ist, wenn der Druck im Vorlauf unter einem Schwellwert, vorzugsweise unter dem Druck im Rücklauf absinkt.Hydraulic control arrangement according to one of the preceding claims, with a control unit, via which a signal for reducing the return cross section can be delivered to the directional control valves (12, 14) if the pressure in the supply drops below a threshold value, preferably under the pressure in the return line. Hydraulische Steuereinheit nach Patentanspruch 8, wobei über die Steuereinheit in dem Fall, dass der Druck im Vorlauf eindeutig höher als im Rücklauf ist, der rücklaufseitige Öffnungsquerschnitt vollständig aufgesteuert wird.Hydraulic control unit according to claim 8, wherein the control unit in the case that the pressure in the flow is clearly higher than in the return, the return-side opening cross-section is completely turned on. Steuerblock zur Ansteuerung mehrerer Verbraucher, wobei jedem Verbraucher eine Steueranordnung gemäß einem der vorhergehenden Patentansprüche zugeordnet ist.Control block for controlling a plurality of consumers, wherein each consumer is associated with a control arrangement according to one of the preceding claims.
EP06007227A 2005-04-05 2006-04-05 Hydraulic control device and control block Not-in-force EP1710446B1 (en)

Applications Claiming Priority (2)

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DE102005015689 2005-04-05
DE102005022891A DE102005022891A1 (en) 2005-04-05 2005-05-18 Hydraulic control arrangement and control block

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DE102009047035A1 (en) 2009-11-24 2011-06-09 Technische Universität Dresden Hydraulic control system for controlling one or more consumer loads, has directional valve, where each consumer load is assigned to directional valve during insert of two-way valves
DE102011114241A1 (en) * 2011-06-09 2012-12-13 Sms Meer Gmbh Hydraulic drive unit for plunger of hydraulic cylinders of powder press, has hydraulic pressure accumulators that are equipped for providing hydraulic operating pressures from hydraulic pressure source to hydraulic cylinders
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EP3553325A1 (en) * 2018-04-13 2019-10-16 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
EP3561313A1 (en) * 2018-04-13 2019-10-30 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
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WO2021141874A1 (en) * 2020-01-08 2021-07-15 Sun Hydraulics, Llc Flow control valve with load-sense signal generation
US11072418B2 (en) 2018-04-13 2021-07-27 The Boeing Company Hydraulic system for an aircraft
CN116164003A (en) * 2023-03-07 2023-05-26 浙江大学 Load port independent control valve for distributed hydraulic system and control method thereof

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WO2009062564A1 (en) * 2007-11-14 2009-05-22 Hydac Filtertechnik Gmbh Hydraulic valve device
US8479769B2 (en) 2007-11-14 2013-07-09 Hydac Filtertechnik Gmbh Hydraulic valve device
DE102009047035A1 (en) 2009-11-24 2011-06-09 Technische Universität Dresden Hydraulic control system for controlling one or more consumer loads, has directional valve, where each consumer load is assigned to directional valve during insert of two-way valves
DE102011114241A1 (en) * 2011-06-09 2012-12-13 Sms Meer Gmbh Hydraulic drive unit for plunger of hydraulic cylinders of powder press, has hydraulic pressure accumulators that are equipped for providing hydraulic operating pressures from hydraulic pressure source to hydraulic cylinders
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EP3561313A1 (en) * 2018-04-13 2019-10-30 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
CN110374944A (en) * 2018-04-13 2019-10-25 波音公司 Aircraft hydraulic system and application method with double slide valve
EP3553325A1 (en) * 2018-04-13 2019-10-16 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
US10526071B2 (en) 2018-04-13 2020-01-07 The Boeing Company Hydraulic systems and methods to control a member
US10711809B2 (en) 2018-04-13 2020-07-14 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
US10723441B2 (en) 2018-04-13 2020-07-28 The Boeing Company High-speed-deployed, drum-brake, inertia disk for rack and pinion rotational inerter
US10737764B2 (en) 2018-04-13 2020-08-11 The Boeing Company Base flight control member orientation mechanism and control
US10793261B2 (en) 2018-04-13 2020-10-06 The Boeing Company Electro-mechanically biased supercritical flight control surface loading to reduce high pressure actuation cycles
US10947997B2 (en) 2018-04-13 2021-03-16 The Boeing Company Aircraft hydraulic system with a dual spool valve and methods of use
US11072418B2 (en) 2018-04-13 2021-07-27 The Boeing Company Hydraulic system for an aircraft
WO2021141874A1 (en) * 2020-01-08 2021-07-15 Sun Hydraulics, Llc Flow control valve with load-sense signal generation
US11274752B2 (en) 2020-01-08 2022-03-15 Sun Hydraulics, Llc Flow control valve with load-sense signal generation
CN116164003A (en) * 2023-03-07 2023-05-26 浙江大学 Load port independent control valve for distributed hydraulic system and control method thereof

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DE102005022891A1 (en) 2006-10-12
ATE418683T1 (en) 2009-01-15
DE502006002405D1 (en) 2009-02-05
EP1710446B1 (en) 2008-12-24

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