EP1598560B1 - Hydraulic valve assembly - Google Patents

Hydraulic valve assembly Download PDF

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Publication number
EP1598560B1
EP1598560B1 EP05009870A EP05009870A EP1598560B1 EP 1598560 B1 EP1598560 B1 EP 1598560B1 EP 05009870 A EP05009870 A EP 05009870A EP 05009870 A EP05009870 A EP 05009870A EP 1598560 B1 EP1598560 B1 EP 1598560B1
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EP
European Patent Office
Prior art keywords
valve
pressure
control
control valve
working
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
EP05009870A
Other languages
German (de)
French (fr)
Other versions
EP1598560A1 (en
Inventor
Knud Meldgaard Jensen
Carl Christian Dixen
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Danfoss Power Solutions ApS
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Sauer Danfoss ApS
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Publication of EP1598560A1 publication Critical patent/EP1598560A1/en
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Publication of EP1598560B1 publication Critical patent/EP1598560B1/en
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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
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to 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
    • F15B2211/30—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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/565—Control of a downstream pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves

Definitions

  • the invention relates to a hydraulic valve assembly having a control valve module comprising a supply connection arrangement with a high-pressure connection and a low-pressure connection and a working connection arrangement with two working connections and a control valve between the supply connection arrangement and the working connection arrangement.
  • valve arrangement is made DE 102 16 958 B3 known.
  • the valve arrangement serves to supply a hydraulic load, for example a motor, which is connected to the working connections, with hydraulic fluid under pressure.
  • a hydraulic load for example a motor
  • At the consumer return compensation valves are provided which ensure that the consumer and then; if it works in the sliding mode, is controlled exclusively by the control valve.
  • DE 198 00 721 shows a control device for a hydraulic motor, which is designed as a hydraulic cylinder.
  • a series circuit of a compensation valve and a load-holding valve is provided at the output of the consumer, which is connected to a working port.
  • the load-holding valve is opened by a pressure at the other working port.
  • hydraulic consumers are designed as motors, either as hydraulic cylinders or as rotary motors, then in many cases a so-called "sliding operation" can not be avoided.
  • the motor is loaded by an external force in the direction of movement.
  • this may be a load that is to be lowered.
  • a rotary motor that drives a vehicle such a situation may occur when the vehicle rolls down an inclined plane. In all cases, it must be ensured that the movement of the motor takes place exclusively under the control of the control valve.
  • the return compensation valves are used for this purpose.
  • EP 0 515 692 A1 a hydraulic system with a controllable hydraulic pump and several consumers is described.
  • each hydraulic consumer is controlled via an associated spool.
  • pressure compensation valves are arranged in the inflow direction, which interrupt the inflow to the consumer, if the driving pressure is lower than the load pressure of the system.
  • the invention has for its object to improve the control behavior of the valve assembly.
  • control valve module between the control valve and at least one working port has a return compensation valve.
  • a load-holding valve is arranged, which can be opened by means of a pressure at the other working connection.
  • the return compensation valve can throttle the flow of hydraulic fluid flowing from a working port to the control valve. As a rule, however, it is not readily able to prevent this liquid flow. Now, when placing a load holding valve between the consumer and the work port, the consumer is assured, i. you can actually "lock” it in a position you are in, even if there is an external load on the consumer.
  • the first control input of at least the return compensation valve which is connected in series with the load-holding valve, is connected via a counterpressure valve to the low-pressure connection.
  • the back pressure valve is electrically activated
  • the control valve is electrically activated and the back pressure valve and the control valve respond to the same electrical signal.
  • a Electrical activation can also be a hydraulic, a mechanical or other power-activated activation use. So you can also simultaneously activate the back pressure valve with the deflection of the control valve, so that it is ensured that the load-holding valve opens as soon as this is necessary. But without a corresponding activation of the control valve, this is not required, so that the back pressure valve can remain inactive.
  • back pressure valve is arranged in the control valve module. This is associated with the use of multiple control valve modules each control valve and thus each connected load its own back pressure valve. This allows each consumer to control individually.
  • the return compensation valve is directly connected to an output of the control valve. This keeps a pressure drop at the lowest, practically achievable value. The consumer is then controlled solely by the control valve.
  • the return compensation valve has two control inputs, one of which is connected to a Lastfühltechnisch and a second with a point between the control valve and the scrublaufkompensationsventil, wherein the first control input is connected via a suction valve to the low pressure port.
  • the return compensation valve closes or stronger by the pressure at the second control input throttles when the pressure between the return compensation valve and the control valve increases.
  • the return compensation valve is applied in the opening direction or in the direction of reduced throttling when the pressure in the load-sensing line increases. This behavior is known per se from a return compensation valve.
  • the return compensation valve has a valve element which is controlled by the pressures at the two control inputs.
  • This valve element is often designed as a slide.
  • a suction valve By now connecting the load-sensing line to the low-pressure connection via a suction valve, a relatively fast reaction of the return-compensation valve to changes in the surrounding pressures is made possible.
  • the return compensation valve can namely draw in hydraulic fluid, if this should be necessary.
  • the suction valve is preferably designed as a check valve, which opens to the first control input, so that the pressure in the load-sensing line can not easily drain to the low-pressure connection, a Nachsaugen at too low pressure but is possible.
  • the first control input can be connected to the low-pressure connection via a check valve arranged in the slide of the control valve. This ensures a mobility of the valve element of the return compensation valve in both directions. From the second control input is a supply of hydraulic fluid is not critical, because there is always a sufficient supply of liquid.
  • the first control input is made possible by the connection to the low-pressure connection the return compensation valve can either draw in hydraulic fluid through the suction valve or can discharge through the check valve, which is connectable to the low pressure port. A discharge of hydraulic fluid through the first control input is required only if the slide is in a corresponding position anyway.
  • the check valve opens into a path in the slide, which is connectable to the low pressure port.
  • This is a structurally relatively simple solution that keeps the construction costs for the control valve low.
  • each work connection is associated with a return compensation valve.
  • the burden on the consumer can therefore be in both directions. In each direction, the consumer is then still controlled exclusively via the control valve.
  • each first control input is connected via a throttle with a pressure control valve, wherein the pressure control valves are adjustable to different pressures. This provides a simple way to operate the consumer in different directions in different ways.
  • a tap between the throttle and the pressure control valve of each remindlaufkompensationsventils is connected to a shuttle valve whose output is connected to an input of a control valve upstream flow compensation valve is.
  • the flow compensation valve can then form a proportional valve together with the control valve.
  • the flow compensation valve ensures that there is always a constant pressure across the control valve, so that the amount of liquid controlled by the control valve depends exclusively on the opening cross-section, which is released by the control valve.
  • the pressure at the flow compensating valve is then controlled by the respective maximum pressure in the load-sensing lines.
  • the control valve has a slide which is displaceable in two working positions and a neutral position, wherein between the neutral position and each working position, a blocking position is provided.
  • the two working positions serve to drive the consumer in one direction or the other.
  • In the neutral position both outputs of the control valve are connected to the tank, so that no "false" signals can arise, which may open the load-holding valve.
  • a blocking is provided between the neutral position and the two working positions, in which the path from the supply terminal assembly to the working connection arrangement is actually interrupted.
  • a hydraulic valve arrangement 1 has a control valve module 2, which has a high-pressure connection P and a low-pressure connection T.
  • the high-pressure port P and the low-pressure port T together form a supply port arrangement.
  • the control valve module 2 on two working ports A, B, which together form a working connection arrangement.
  • there is a load sensing port LS which reports the highest occurring load pressure so that the supply pressure can be adjusted to the load pressure.
  • the control valve module 2 is shown here as a box. It is realized in a coherent housing.
  • a control valve 3 is arranged, which is designed as a slide valve.
  • the control valve 3 has a slide 4, which can be displaced by a drive 5 in different positions.
  • the drive 5 can be hydraulically controlled on the one hand via a pilot line 6.
  • an electrical control via a control line 7 is possible.
  • the slide 4 In the illustrated position, the slide 4 is in a so-called neutral position s, in which the two working ports A, B are connected to a tank line 8, which leads to the low pressure port T. In the neutral position, a consumer connected to the working ports A, B is blocked due to valves described below.
  • the slider 4 is movable in a first working position 1 and in a second working position r.
  • In the working position r of the working port A is connected to the high pressure port P.
  • In the working position 1 of the working port B is connected to the high pressure port P.
  • a blocking position u1, u2 is provided in each case, in which a connection between the working ports A, B and the high-pressure port P is interrupted.
  • the two working positions 1, r are, as is usual with slide valves, not to be understood as discrete positions.
  • the slide 4 can still be moved to different sized flow cross sections for the hydraulic fluid from the high pressure port P to one of the two working ports A, B and other of the two working ports B, A to the tank port T (meter-out) release ,
  • a flow compensation valve 9 is arranged between the high pressure port P and the control valve 3.
  • the flow compensation valve 9 is acted upon in the opening direction by the force of a spring 10 and the pressure in a control line 11 and in the closing direction by a pressure at a point 12 between the flow compensation valve 9 and the control valve 3.
  • the flow compensation valve 9 ensures that the pressure on the control valve 3 remains constant, so that the pressure from the high pressure port P to one of the two working ports A, B flowing amount of liquid is determined solely by the size of the released by the slide 4 flow cross-section.
  • the flow compensation valve 9 and the control valve 3 thus together form a load-independent valve, which may possibly also be referred to as a proportional valve.
  • the working port A is connected via a working line 13 and the working port B is connected via a working line 14 to the control valve.
  • a return compensation valve 15 is arranged in the working line 13 in the working line 13.
  • a return compensation valve 16 is arranged in the working line 14. Both return compensation valves 15, 16 have the same structure in principle. They are therefore explained together. Both return compensation valves 15, 16 are disposed within the control valve module 2 and the control valve 3 is relatively close together. In other words, close the two scrublaufkompensationsventile 15, 16 directly to the control valve 3, so that virtually no or only an extremely small pressure loss is observed between the return compensation valves 15, 16 and the control valve 3.
  • Each control valve 15, 16 has a first control input 17a, 17b.
  • the letter a is used for reference numerals associated with the return compensation valve 15.
  • the letter b is used for reference numerals associated with the return compensation valve 16.
  • the control input 17a, 17b communicates with a load sensing line 18a, 18b.
  • the load sensing line 18a, 18b is at a corresponding deflection of the slide 4, which causes a connection to the pressure port P, provided with the same pressure as the portion of the working line 13, 14 between the return compensation valve 15, 16 and the control valve.
  • a pressure acts on a second control input 20a, 20b, which is connected to a portion of the working line 13, 14 between the geartownkompensationsventil 15, 16 and the control valve 3.
  • the control valve 3 establishes in each working position 1, r of the slide 4, a supply path 21 a, 21 b, which forms a connection between the output of the flow compensation valve 9 and the corresponding working line 13, 14. From the supply path 21a, 21b branches off a control path 22a, 22b, which opens into the corresponding load-sensing line 18a, 18b.
  • the slider 4 depending on its position for each working position 1, r a return path 23 a, 23 b, through which the not connected to the flow compensation valve 9 working line 13, 14 is connected to the tank line 8.
  • a return path 23a, 23b opens a discharge path 24a, 24b, in which a to the tank line 8 out opening check valve 25a, 25b is arranged.
  • the relief path 24a, 24b comes into connection with the load-sensing line 18a, 18b.
  • the two load-sensing lines 18a, 18b are connected to one another by a shuttle valve 26 whose output is connected to a further shuttle valve 27, which passes on the highest pressure prevailing in a hydraulic system, in which the valve arrangement 1 is arranged, to a load-sensing port LS.
  • a throttle 28a, 28b is provided for each load-sensing line 18a, 18b.
  • the two pressure control valves 29a, 29b are connected to a counter-pressure valve 30 shown only schematically, which can be activated in the illustrated embodiment via an electric drive 31. But it can also act automatically, in another embodiment.
  • the drive 31 is connected to the control line 7, so that the control valve 3 and the back pressure valve 30 can be activated together with the same control signal.
  • the back pressure valve 30 is connected to the low pressure port T. It ensures that in the respective load-sensing line 18a, 18b in each case a predetermined minimum pressure prevails.
  • a hydraulic consumer in the form of a hydraulic cylinder 32 is connected to the two working ports A, B.
  • On the cylinder acts an external force represented by an arrow 33.
  • a load-holding valve 34 is arranged, which is acted upon in the opening direction by the pressure at the working port A and the pressure at its input and in the closing direction by the force of a spring 35.
  • a check valve 36 is arranged, which opens to the cylinder 32 out.
  • the load-holding valve 34 is able to completely close the line between the cylinder 32 and the control valve module 2.
  • the remindierskompensationsventile 15, 16 are not necessarily able to cause a complete interruption of the working lines 13, 14.
  • the two load-sensing lines 18a, 18b are each connected via a suction valve 37a, 37b to the tank line.
  • the Nachsaugventile 37a, 37b are designed as check valves, which open to the first control input 17a, 17b out.
  • valve assembly now works as follows:
  • the working line 13 is supplied with pressure from the high-pressure port P.
  • the load-sensing line 18a is supplied with pressure. Since the same pressure is present at the two control inputs 17a, 20a of the return compensation valve 15, this is turned on by the spring 19a.
  • the cylinder 32 is now pressurized in its upper working space 38. In this case, hydraulic fluid is displaced from the lower working space 39. This is possible because the pressure at the working port A has opened the load-holding valve 34.
  • the pressure control valves 29a, 29b ensure that the pressure in the load sensing lines 18a, 18b does not exceed a predetermined value. If this is the case, then hydraulic fluid is discharged to the low-pressure port T through the back pressure valve 30.
  • the back pressure valve 30 ensures in any case that sufficient pressure for actuating the load-holding valve 34 is present.
  • the respective highest pressure from the two load-sensing lines 18a, 18b is applied via the control line 11 to the flow compensation valve 9, which accordingly opens exactly as far as the pressure in the load-sensing lines 18a, 18b requires.
  • the load-holding valve 34 relieved in the present embodiment, in which this is done with the aid of the back pressure valve, to the environment.
  • this load-holding valve it is also possible to relieve this load-holding valve to the working line 14, to hermetically close the load-holding valve or to relieve it to a connected proportional valve or to the tank.
  • the spool of the control valve 3 may cause a flow control or a mixed pressure flow control instead of the pressure control shown.
  • the arrangement of the two remindlaufkompensationsventile 15, 16 in the immediate vicinity of the control valve 3 within the control valve module 2 has the advantage that the risk of leakage is significantly reduced compared to an external unit or a flanged unit containing the remindlaufkompensationsventile 15, 16.
  • there may always be a pressure loss in the wiring which would have to be corrected by the spring 19a, 19b.
  • the return compensation valves 15, 16 so close to the control valve 3 arranges, as in the present embodiment, then one has virtually no pressure loss, so that one has complete control over the tolerances and always achieves a uniform performance.
  • the aftercare valves 37a, 37b and the return valves 25a, 25b allow the spool (or other valve member) in the return compensation valves 15, 16 to react extremely quickly.
  • the slider can namely suck in or displace oil without having to overcome significant resistance here.

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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)
  • Multiple-Way Valves (AREA)

Abstract

The hydraulic valve arrangement (1) has a control valve module (2) with a high-pressure connection (P) and a low pressure connection (T). There are also a working connection arrangement with two working connections (A,B) and a control valve (3). The control valve module has a backflow compensation valve (15, 16) between the control valve and at least one working connection.

Description

Die Erfindung betrifft eine hydraulische Ventilanordnung mit einem Steuerventilmodul, das eine Versorgungsanschlußanordnung mit einem Hochdruckanschluß und einem Niederdruckanschluß und eine Arbeitsanschlußanordnung mit zwei Arbeitsanschlüssen sowie ein Steuerventil zwischen der Versorgungsanschlußanordnung und der Arbeitsanschlußanordnung aufweist.The invention relates to a hydraulic valve assembly having a control valve module comprising a supply connection arrangement with a high-pressure connection and a low-pressure connection and a working connection arrangement with two working connections and a control valve between the supply connection arrangement and the working connection arrangement.

Eine derartige Ventilanordnung ist aus DE 102 16 958 B3 bekannt. Die Ventilanordnung dient dazu, einen hydraulischen Verbraucher, beispielsweise einen Motor, der an die Arbeitsanschlüsse angeschlossen ist, mit Hydraulikflüssigkeit unter Druck zu versorgen. Am Verbraucher sind Rücklaufkompensationsventile vorgesehen, die dafür sorgen, daß der Verbraucher auch dann; wenn er im schiebenden Betrieb arbeitet, ausschließlich vom Steuerventil gesteuert wird.Such a valve arrangement is made DE 102 16 958 B3 known. The valve arrangement serves to supply a hydraulic load, for example a motor, which is connected to the working connections, with hydraulic fluid under pressure. At the consumer return compensation valves are provided which ensure that the consumer and then; if it works in the sliding mode, is controlled exclusively by the control valve.

DE 198 00 721 zeigt eine Steuervorrichtung für einen hydraulischen Motor, der als hydraulischer Zylinder ausgebildet ist. Zur Steuerung einer Senkbewegung ist am Ausgang des Verbrauchers eine Reihenschaltung aus einem Kompensationsventil und einem Lasthalteventil vorgesehen, das mit einem Arbeitsanschluß verbunden ist. Das Lasthalteventil wird dabei durch einen Druck am anderen Arbeitsanschluß aufgesteuert. DE 198 00 721 shows a control device for a hydraulic motor, which is designed as a hydraulic cylinder. To control a lowering movement, a series circuit of a compensation valve and a load-holding valve is provided at the output of the consumer, which is connected to a working port. The load-holding valve is opened by a pressure at the other working port.

Wenn hydraulische Verbraucher als Motoren ausgebildet sind, sei es als hydraulische Zylinder oder als Rotationsamotoren, dann ist in vielen Fällen ein sogenannter "schiebender Betrieb" nicht zu vermeiden. In einer derartigen Situation wird der Motor durch eine äußere Kraft in Bewegungsrichtung belastet. Bei einem Zylinder kann dies beispielsweise eine Last sein, die abgesenkt werden soll. Bei einem Rotationsmotor, der ein Fahrzeug antreibt, kann eine derartige Situation auftreten, wenn das Fahrzeug eine schiefe Ebene hinabrollt. In allen Fällen muß man sicherstellen, daß die Bewegung des Motors ausschließlich unter der Regie des Steuerventils erfolgt. Hierzu dienen die Rücklaufkompensationsventile.If hydraulic consumers are designed as motors, either as hydraulic cylinders or as rotary motors, then in many cases a so-called "sliding operation" can not be avoided. In such a situation, the motor is loaded by an external force in the direction of movement. For example, in the case of a cylinder, this may be a load that is to be lowered. In a rotary motor that drives a vehicle, such a situation may occur when the vehicle rolls down an inclined plane. In all cases, it must be ensured that the movement of the motor takes place exclusively under the control of the control valve. The return compensation valves are used for this purpose.

Der Aufbau eines derartigen Lasthalteventils ergibt sich beispielsweise aus EP 0 197 467 A2 .The structure of such a load-holding valve results, for example EP 0 197 467 A2 ,

Bei einer Ventilanordnung der eingangs genannten Art ist es allerdings schwierig, die Rücklaufkompensationsventile "richtig" einzustellen, so daß der Verbraucher in der gewünschten Weise betrieben werden kann.In a valve arrangement of the type mentioned, however, it is difficult to set the return compensation valves "right", so that the consumer can be operated in the desired manner.

In EP 0 515 692 A1 wird ein Hydrauliksystem mit einer regelbaren Hydraulikpumpe und mehreren Verbrauchern beschrieben. Bei diesem wird jeder Hydraulikverbraucher über einen zugeordneten Steuerschieber angesteuert. In den zum Verbraucher gerichteten Arbeitsleitungen sind in Zuflußrichtung Druckkompensationsventile angeordnet, die den Zufluß zum Verbraucher unterbrechen, falls deren Ansteuerdruck niedriger als der Lastdruck des Systems ist.In EP 0 515 692 A1 a hydraulic system with a controllable hydraulic pump and several consumers is described. In this, each hydraulic consumer is controlled via an associated spool. In the direction of the consumer working lines pressure compensation valves are arranged in the inflow direction, which interrupt the inflow to the consumer, if the driving pressure is lower than the load pressure of the system.

In US 4 569 272 wird ein Hydraulikversorgungssystem zur Ansteuerung eines hydraulischen Verbrauchers beschrieben, bei dem in den Arbeitsleitungen Abflußsperrventile vorgesehen sind, die öffnen, wenn in der jeweils anderen Arbeitsleitung ein Druck angelegt wird.In US 4 569 272 a hydraulic supply system for controlling a hydraulic load is described, in which the drain lines are provided drain check valves, which open when a pressure is applied in the other working line.

In US 3 589 387 wird eine integrierte Hydrauliksteuereinheit beschrieben, die variabel aus mehreren unterschiedlichen Standardmodulen zusammengesetzt werden kann.In US Pat. No. 3,589,387 An integrated hydraulic control unit is described, which can be variably composed of several different standard modules.

In EP 0 197 467 A2 ist ein Bremssperrventil für hydraulische Arbeitszylinder beschrieben, welches neben seiner Drosselfunktion und seiner Funktion als gesteuertes Rückschlagventil zusätzlich das Hydraulikmedium bei nicht druckbeaufschlagtem Steueranschluß abdichtet.In EP 0 197 467 A2 a brake check valve for hydraulic cylinder is described, which in addition to its throttle function and its function as a controlled check valve additionally seals the hydraulic fluid at not pressurized control port.

Der Erfindung liegt die Aufgabe zugrunde, das Steuerverhalten der Ventilanordnung zu verbessern.The invention has for its object to improve the control behavior of the valve assembly.

Diese Aufgabe wird bei einer Ventilanordnung der eingangs genannten Art dadurch gelöst, daß das Steuerventilmodul zwischen dem Steuerventil und mindestens einem Arbeitsanschluß ein Rücklaufkompensationsventil aufweist.This object is achieved with a valve arrangement of the type mentioned above in that the control valve module between the control valve and at least one working port has a return compensation valve.

Man verlagert also das Rücklaufkompensationsventil von einer Position am Verbraucher, d.h. am Motor, in eine Position innerhalb des Steuerventilmoduls. Damit erreicht man, daß das Steuerventil wesentlich genauer mit dem Rücklaufkompensationsventil zusammenarbeiten kann, weil zwischen dem Steuerventil und dem Rücklaufkompensationsventil praktisch keine Druckverluste mehr auftreten. Sollten sie in einer kleinen Größenordnung auftreten, dann sind sie bekannt und konstant. Diese Druckverluste können, wenn man das Rücklaufkompensationsventil unmittelbar am Verbraucher anordnet, von Installation zu Installation höchst unterschiedlich sein. Deswegen benötigt ein Monteur ein gewisses Geschick, um die Vorspannkraft des Rücklaufkompensationsventils auf einen richtigen Wert so einzustellen, daß tatsächlich die gewünschte Steuerung durch das Steuerventil erreicht wird. Wenn man derartige Druckverluste nicht mehr berücksichtigen muß, dann ist der Aufbau wesentlich einfacher und man erhält sozusagen automatisch ein besseres Steuerverhalten der Ventilanordnung. Darüber hinaus erreicht man eine kostengünstige Fertigung. Die Ventilanordnung baut platzsparend. Die Gefahr einer Leckage wird im Verhältnis zu einer externen Anordnung des Rücklaufkompensationsventils oder einer angeflanschten Anordnung des Rücklaufkompensationsventils vermindert.So you move the return compensation valve from a position on the consumer, ie the engine, in a position within the control valve module. This ensures that the control valve can work much more accurately with the return compensation valve, because between the control valve and the return compensation valve virtually no pressure losses occur more. If they occur on a small scale, then they are known and constant. These pressure drops can be very different from installation to installation by placing the return compensation valve directly on the load. Therefore, a fitter requires a certain skill to set the biasing force of the return compensation valve to a proper value so as to actually achieve the desired control by the control valve. If you do not have to consider such pressure losses, then the structure is much easier and you get, so to speak, automatically a better control behavior of the valve assembly. In addition, you can achieve a cost-effective production. The valve assembly saves space. The risk of leakage is in relation to an external arrangement of the return compensation valve or a flanged Arrangement of the return compensation valve reduced.

Dabei ist vom Steuerventil aus gesehen jenseits des Rücklaufkompensationsventils ein Lasthalteventil angeordnet, das mit Hilfe eines Drucks am anderen Arbeitsanschluß aufsteuerbar ist. Das Rücklaufkompensationsventil kann den von einem Arbeitsanschluß zum Steuerventil fließenden Strom von Hydraulikflüssigkeit zwar drosseln. Es ist in der Regel aber nicht ohne weiteres in der Lage, diesen Flüssigkeitsstrom zu unterbinden. Wenn man nun ein Lasthalteventil zwischen dem Verbraucher und dem Arbeitsanschluß anordnet, dann ist der Verbraucher gesichert, d.h. man kann ihn tatsächlich in einer eingenommenen Position "verriegeln", und zwar auch dann, wenn eine äußere Last auf den Verbraucher wirkt.In this case, viewed from the control valve, beyond the return compensation valve, a load-holding valve is arranged, which can be opened by means of a pressure at the other working connection. Although the return compensation valve can throttle the flow of hydraulic fluid flowing from a working port to the control valve. As a rule, however, it is not readily able to prevent this liquid flow. Now, when placing a load holding valve between the consumer and the work port, the consumer is assured, i. you can actually "lock" it in a position you are in, even if there is an external load on the consumer.

Weiterhin ist der erste Steuereingang zumindest des Rücklaufkompensationsventils, das mit dem Lasthalteventil in Reihe geschaltet ist, über ein Gegendruckventil mit dem Niederdruckanschluß verbunden. Dadurch ist es möglich, in der Lastfühlleitung im störungsfreien Betrieb immer einen Druck aufrechtzuerhalten, der zum Öffnen des Lasthalteventils erforderlich ist. Letztendlich muß der vom Gegendruckventil erzeugbare Druck nur so groß sein, daß er das Offenhalten des Lasthalteventils ermöglicht.Furthermore, the first control input of at least the return compensation valve, which is connected in series with the load-holding valve, is connected via a counterpressure valve to the low-pressure connection. This makes it possible to always maintain a pressure in the load-sensing line in trouble-free operation, which pressure is required to open the load-holding valve. Ultimately, the pressure generated by the back pressure valve must only be so great that it allows keeping open the load-holding valve.

Darüber hinaus ist das Gegendruckventil elektrisch aktivierbar, das Steuerventil ist elektrisch aktivierbar und das Gegendruckventil und das Steuerventil reagieren auf das gleiche elektrische Signal. Anstelle einer elektrischen Aktivierung kann man auch eine hydraulische, eine mechanische oder eine andere hilfskraftbewirkte Aktivierung verwenden. Man kann also mit der Auslenkung des Steuerventils gleichzeitig auch das Gegendruckventil aktivieren, so daß sichergestellt ist, daß das Lasthalteventil öffnet, sobald dies erforderlich ist. Ohne eine entsprechende Aktivierung des Steuerventils ist dies aber nicht erforderlich, so daß das Gegendruckventil unaktiviert bleiben kann.In addition, the back pressure valve is electrically activated, the control valve is electrically activated and the back pressure valve and the control valve respond to the same electrical signal. Instead of a Electrical activation can also be a hydraulic, a mechanical or other power-activated activation use. So you can also simultaneously activate the back pressure valve with the deflection of the control valve, so that it is ensured that the load-holding valve opens as soon as this is necessary. But without a corresponding activation of the control valve, this is not required, so that the back pressure valve can remain inactive.

Es ist von Vorteil, wenn das Gegendruckventil im Steuerventilmodul angeordnet ist. Damit ist bei der Verwendung von mehreren Steuerventilmodulen jedem Steuerventil und damit jedem angeschlossenen Verbraucher ein eigenes Gegendruckventil zugeordnet. Damit läßt sich jeder Verbraucher individuell ansteuern.It is advantageous if the back pressure valve is arranged in the control valve module. This is associated with the use of multiple control valve modules each control valve and thus each connected load its own back pressure valve. This allows each consumer to control individually.

Vorzugsweise ist das Rücklaufkompensationsventil unmittelbar mit einem Ausgang des Steuerventils verbunden. Dadurch hält man einen Druckverlust auf dem niedrigsten, praktisch zu erzielenden Wert. Der Verbraucher wird dann also ausschließlich über das Steuerventil gesteuert.Preferably, the return compensation valve is directly connected to an output of the control valve. This keeps a pressure drop at the lowest, practically achievable value. The consumer is then controlled solely by the control valve.

Vorzugsweise weist das Rücklaufkompensationsventil zwei Steuereingänge auf, von denen ein erster mit einer Lastfühlleitung und ein zweiter mit einem Punkt zwischen dem Steuerventil und dem Rücklaufkompensationsventil verbunden ist, wobei der erste Steuereingang über ein Saugventil mit dem Niederdruckanschluß verbunden ist. Mit einem derartigen Aufbau wird zunächst erreicht, daß das Rücklaufkompensationsventil durch den Druck am zweiten Steuereingang schließt oder stärker drosselt, wenn der Druck zwischen dem Rücklaufkompensationsventil und dem Steuerventil ansteigt. In ähnlicher Weise wird das Rücklaufkompensationsventil in Öffnungsrichtung oder in Richtung auf eine verminderte Drosselung beaufschlagt, wenn der Druck in der Lastfühlleitung ansteigt. Dieses Verhalten ist von einem Rücklaufkompensationsventil an sich bekannt. Das Rücklaufkompensationsventil weist ein Ventilelement auf, das durch die Drücke an den beiden Steuereingängen gesteuert wird. Dieses Ventilelement ist vielfach als Schieber ausgebildet. Dadurch, daß man nun die Lastfühlleitung über ein Saugventil mit dem Niederdruckanschluß verbindet, ermöglicht man eine relativ schnelle Reaktion des Rücklaufkompensationsventils auf Änderungen in den umgebenden Drücken. Das Rücklaufkompensationsventil kann nämlich Hydraulikflüssigkeit nachsaugen, wenn dies erforderlich werden sollte. Das Saugventil ist dabei vorzugsweise als Rückschlagventil ausgebildet, das zum ersten Steuereingang hin öffnet, so daß der Druck in der Lastfühlleitung nicht ohne weiteres zum Niederdruckanschluß abfließen kann, ein Nachsaugen bei zu geringem Druck aber möglich ist.Preferably, the return compensation valve has two control inputs, one of which is connected to a Lastfühlleitung and a second with a point between the control valve and the Rücklaufkompensationsventil, wherein the first control input is connected via a suction valve to the low pressure port. With such a structure is first achieved that the return compensation valve closes or stronger by the pressure at the second control input throttles when the pressure between the return compensation valve and the control valve increases. Similarly, the return compensation valve is applied in the opening direction or in the direction of reduced throttling when the pressure in the load-sensing line increases. This behavior is known per se from a return compensation valve. The return compensation valve has a valve element which is controlled by the pressures at the two control inputs. This valve element is often designed as a slide. By now connecting the load-sensing line to the low-pressure connection via a suction valve, a relatively fast reaction of the return-compensation valve to changes in the surrounding pressures is made possible. The return compensation valve can namely draw in hydraulic fluid, if this should be necessary. The suction valve is preferably designed as a check valve, which opens to the first control input, so that the pressure in the load-sensing line can not easily drain to the low-pressure connection, a Nachsaugen at too low pressure but is possible.

Auch ist von Vorteil, wenn der erste Steuereingang über ein im Schieber des Steuerventils angeordnetes Rückschlagventil mit dem Niederdruckanschluß verbindbar ist. Damit stellt man eine Bewegbarkeit des Ventilelements des Rücklaufkompensationsventils in beide Richtungen sicher. Vom zweiten Steuereingang her ist eine Versorgung mit Hydraulikflüssigkeit unkritisch, weil hier immer ein ausreichender Flüssigkeitsvorrat vorhanden ist. Am ersten Steuereingang hingegen wird durch die Verbindung zum Niederdruckanschluß ermöglicht, daß das Rücklaufkompensationsventil entweder Hydraulikflüssigkeit nachsaugen kann durch das Saugventil oder abgeben kann durch das Rückschlagventil, das mit dem Niederdruckanschluß verbindbar ist. Eine Abgabe von Hydraulikflüssigkeit über den ersten Steuereingang ist ohnehin nur dann erforderlich, wenn sich der Schieber in einer entsprechenden Position befindet.It is also advantageous if the first control input can be connected to the low-pressure connection via a check valve arranged in the slide of the control valve. This ensures a mobility of the valve element of the return compensation valve in both directions. From the second control input is a supply of hydraulic fluid is not critical, because there is always a sufficient supply of liquid. On the other hand, the first control input is made possible by the connection to the low-pressure connection the return compensation valve can either draw in hydraulic fluid through the suction valve or can discharge through the check valve, which is connectable to the low pressure port. A discharge of hydraulic fluid through the first control input is required only if the slide is in a corresponding position anyway.

Vorzugsweise mündet das Rückschlagventil in einen Pfad im Schieber, der mit dem Niederdruckanschluß verbindbar ist. Dies ist eine konstruktiv relativ einfache Lösung, die den baulichen Aufwand für das Steuerventil gering hält.Preferably, the check valve opens into a path in the slide, which is connectable to the low pressure port. This is a structurally relatively simple solution that keeps the construction costs for the control valve low.

Vorzugsweise ist jedem Arbeitsanschluß ein Rücklaufkompensationsventil zugeordnet. Die Belastung des Verbrauchers kann also in beide Richtungen erfolgen. In jede Richtung wird der Verbraucher dann immer noch ausschließlich über das Steuerventil gesteuert.Preferably, each work connection is associated with a return compensation valve. The burden on the consumer can therefore be in both directions. In each direction, the consumer is then still controlled exclusively via the control valve.

Hierbei ist bevorzugt, daß jeder erste Steuereingang über eine Drossel mit einem Druckregelventil verbunden ist, wobei die Druckregelventile auf unterschiedliche Drücke einstellbar sind. Damit hat man auf einfache Weise die Möglichkeit, den Verbraucher in unterschiedliche Richtungen auf unterschiedliche Weise zu betreiben.It is preferred that each first control input is connected via a throttle with a pressure control valve, wherein the pressure control valves are adjustable to different pressures. This provides a simple way to operate the consumer in different directions in different ways.

Hierbei ist bevorzugt, daß ein Abgriff zwischen der Drossel und dem Druckregelventil jedes Rücklaufkompensationsventils mit einem Wechselventil verbunden ist, dessen Ausgang mit einem Eingang eines dem Steuerventil vorgeschalteten Vorlaufkompensationsventils verbunden ist. Das Vorlaufkompensationsventil kann dann mit dem Steuerventil zusammen ein Proportionalventil bilden. Das Vorlaufkompensationsventil sorgt dafür, daß über das Steuerventil immer ein konstanter Druck ansteht, so daß die vom Steuerventil gesteuerte Flüssigkeitsmenge ausschließlich von dem Öffnungsquerschnitt abhängt, der vom Steuerventil freigegeben wird. Der Druck am Vorlaufkompensationsventil wird dann vom jeweils höchstens Druck in den Lastfühlleitungen gesteuert.It is preferred that a tap between the throttle and the pressure control valve of each Rücklaufkompensationsventils is connected to a shuttle valve whose output is connected to an input of a control valve upstream flow compensation valve is. The flow compensation valve can then form a proportional valve together with the control valve. The flow compensation valve ensures that there is always a constant pressure across the control valve, so that the amount of liquid controlled by the control valve depends exclusively on the opening cross-section, which is released by the control valve. The pressure at the flow compensating valve is then controlled by the respective maximum pressure in the load-sensing lines.

Vorzugsweise weist das Steuerventil einen Schieber auf, der in zwei Arbeitsstellungen und eine Neutralstellung verlagerbar ist, wobei zwischen der Neutralstellung und jeder Arbeitsstellung eine Sperrstellung vorgesehen ist. Die beiden Arbeitsstellungen dienen dazu, den Verbraucher in die eine oder in die andere Richtung anzutreiben. In der Neutralstellung sind beide Ausgänge des Steuerventils mit Tank verbunden, so daß keine "falschen" Signale entstehen können, die eventuell das Lasthalteventil öffnen. Um einen definierten Übergang zwischen der Neutralstellung und dem Antrieb in die eine oder andere Richtung zu bewirken, ist zwischen der Neutralstellung und den beiden Arbeitsstellungen eine Blockierung vorgesehen, in der der Weg von der Versorgungsanschlußanordnung zur Arbeitsanschlußanordnung tatsächlich unterbrochen ist.Preferably, the control valve has a slide which is displaceable in two working positions and a neutral position, wherein between the neutral position and each working position, a blocking position is provided. The two working positions serve to drive the consumer in one direction or the other. In the neutral position, both outputs of the control valve are connected to the tank, so that no "false" signals can arise, which may open the load-holding valve. In order to effect a defined transition between the neutral position and the drive in one or the other direction, a blocking is provided between the neutral position and the two working positions, in which the path from the supply terminal assembly to the working connection arrangement is actually interrupted.

Die Erfindung wird im folgenden anhand eines bevorzugten Ausführungsbeispiels in Verbindung mit der Zeichnung beschrieben. Hierin zeigt:

die einzige Figur
eine schematische Darstellung einer hydraulischen Ventilanordnung.
The invention will be described below with reference to a preferred embodiment in conjunction with the drawings. Hereby shows:
the only figure
a schematic representation of a hydraulic valve assembly.

Eine hydraulische Ventilanordnung 1 weist ein Steuerventilmodul 2 auf, das einen Hochdruckanschluß P und einen Niederdruckanschluß T aufweist. Der Hochdruckanschluß P und der Niederdruckanschluß T bilden zusammen eine Versorgungsanschlußanordnung. Ferner weist das Steuerventilmodul 2 zwei Arbeitsanschlüsse A, B auf, die zusammen einen Arbeitsanschlußanordnung bilden. Schließlich gibt es einen Lastfühlanschluß LS, der den höchsten vorkommenden Lastdruck meldet, so daß der Versorgungsdruck an den Lastdruck angepaßt werden kann. Das Steuerventilmodul 2 ist hier als Kasten dargestellt. Es wird in einem zusammenhängenden Gehäuse realisiert.A hydraulic valve arrangement 1 has a control valve module 2, which has a high-pressure connection P and a low-pressure connection T. The high-pressure port P and the low-pressure port T together form a supply port arrangement. Further, the control valve module 2 on two working ports A, B, which together form a working connection arrangement. Finally, there is a load sensing port LS which reports the highest occurring load pressure so that the supply pressure can be adjusted to the load pressure. The control valve module 2 is shown here as a box. It is realized in a coherent housing.

Zwischen der Versorgungsanschlußanordnung P, T und der Arbeitsanschlußanordnung A, B ist ein Steuerventil 3 angeordnet, das als Schieberventil ausgebildet ist. Das Steuerventil 3 weist einen Schieber 4 auf, der durch einen Antrieb 5 in unterschiedliche Stellungen verlagert werden kann. Der Antrieb 5 kann einerseits über eine Pilotleitung 6 hydraulisch angesteuert werden. Andererseits ist auch eine elektrische Ansteuerung über eine Steuerleitung 7 möglich.Between the supply connection arrangement P, T and the working connection arrangement A, B, a control valve 3 is arranged, which is designed as a slide valve. The control valve 3 has a slide 4, which can be displaced by a drive 5 in different positions. The drive 5 can be hydraulically controlled on the one hand via a pilot line 6. On the other hand, an electrical control via a control line 7 is possible.

In der dargestellten Position befindet sich der Schieber 4 in einer sogenannten Neutralstellung s, bei der die beiden Arbeitsanschlüsse A, B mit einer Tankleitung 8 verbunden sind, die zum Niederdruckanschluß T führt. In der Neutralstellung ist ein an den Arbeitsanschlüssen A, B angeschlossener Verbraucher aufgrund von nachstehend beschriebenen Ventilen blockiert.In the illustrated position, the slide 4 is in a so-called neutral position s, in which the two working ports A, B are connected to a tank line 8, which leads to the low pressure port T. In the neutral position, a consumer connected to the working ports A, B is blocked due to valves described below.

Der Schieber 4 ist in einer ersten Arbeitsstellung 1 und in eine zweite Arbeitsstellung r verfahrbar. In der Arbeitsstellung r wird der Arbeitsanschluß A mit dem Hochdruckanschluß P verbunden. In der Arbeitsstellung 1 wird der Arbeitsanschluß B mit dem Hochdruckanschluß P verbunden.The slider 4 is movable in a first working position 1 and in a second working position r. In the working position r of the working port A is connected to the high pressure port P. In the working position 1 of the working port B is connected to the high pressure port P.

Zwischen der Schwimmstellung s und den beiden Arbeitsstellungen 1, r des Schiebers 4 ist jeweils eine Sperrstellung u1, u2 vorgesehen, in der eine Verbindung zwischen den Arbeitsanschlüssen A, B und dem Hochdruckanschluß P unterbrochen ist.Between the floating position s and the two working positions 1, r of the slider 4, a blocking position u1, u2 is provided in each case, in which a connection between the working ports A, B and the high-pressure port P is interrupted.

Die beiden Arbeitsstellungen 1, r sind, wie dies bei Schieberventilen üblich ist, nicht als diskrete Positionen zu verstehen. In jeder Arbeitsstellung 1, r kann der Schieber 4 noch verschoben werden, um unterschiedlich große Strömungsquerschnitte für die Hydraulikflüssigkeit vom Hochdruckanschluß P zu einem der beiden Arbeitsanschlüsse A, B und von anderen der beiden Arbeitsanschlüsse B, A zum Tankanschluß T (meter-out) freizugeben.The two working positions 1, r are, as is usual with slide valves, not to be understood as discrete positions. In each working position 1, r, the slide 4 can still be moved to different sized flow cross sections for the hydraulic fluid from the high pressure port P to one of the two working ports A, B and other of the two working ports B, A to the tank port T (meter-out) release ,

Zwischen dem Hochdruckanschluß P und dem Steuerventil 3 ist ein Vorlaufkompensationsventil 9 angeordnet. Das Vorlaufkompensationsventil 9 wird in Öffnungsrichtung von der Kraft einer Feder 10 und dem Druck in einer Steuerleitung 11 und in Schließrichtung von einem Druck an einen Punkt 12 zwischen dem Vorlaufkompensationsventil 9 und dem Steuerventil 3 beaufschlagt. Wie weiter unten näher erläutert werden wird, sorgt das Vorlaufkompensationsventil 9 dafür, daß der Druck über das Steuerventil 3 konstant bleibt, so daß die vom Hochdruckanschluß P zu einem der beiden Arbeitanschlüsse A, B fließende Flüssigkeitsmenge ausschließlich durch die Größe des vom Schieber 4 freigegebenen Strömungsquerschnitts bestimmt wird. Das Vorlaufkompensationsventil 9 und das Steuerventil 3 bilden also zusammen ein lastunabhängiges Ventil, das man gegebenenfalls auch als Proportionalventil bezeichnen kann.Between the high pressure port P and the control valve 3, a flow compensation valve 9 is arranged. The flow compensation valve 9 is acted upon in the opening direction by the force of a spring 10 and the pressure in a control line 11 and in the closing direction by a pressure at a point 12 between the flow compensation valve 9 and the control valve 3. As will be explained in more detail below, the flow compensation valve 9 ensures that the pressure on the control valve 3 remains constant, so that the pressure from the high pressure port P to one of the two working ports A, B flowing amount of liquid is determined solely by the size of the released by the slide 4 flow cross-section. The flow compensation valve 9 and the control valve 3 thus together form a load-independent valve, which may possibly also be referred to as a proportional valve.

Der Arbeitsanschluß A ist über eine Arbeitsleitung 13 und der Arbeitsanschluß B ist über eine Arbeitsleitung 14 mit dem Steuerventil verbunden. In der Arbeitsleitung 13 ist ein Rücklaufkompensationsventil 15 angeordnet. In der Arbeitsleitung 14 ist ein Rücklaufkompensationsventil 16 angeordnet. Beide Rücklaufkompensationsventile 15, 16 haben im Prinzip den gleichen Aufbau. Sie werden daher gemeinsam erläutert. Beide Rücklaufkompensationsventile 15, 16 sind innerhalb des Steuerventilmoduls 2 angeordnet und zwar dem Steuerventil 3 relativ eng benachbart. Mit anderen Wort schließen sich die beiden Rücklaufkompensationsventile 15, 16 unmittelbar an das Steuerventil 3 an, so daß zwischen den Rücklaufkompensationsventilen 15, 16 und dem Steuerventil 3 praktisch kein oder nur ein außerordentlich kleiner Druckverlust zu beobachten ist.The working port A is connected via a working line 13 and the working port B is connected via a working line 14 to the control valve. In the working line 13, a return compensation valve 15 is arranged. In the working line 14, a return compensation valve 16 is arranged. Both return compensation valves 15, 16 have the same structure in principle. They are therefore explained together. Both return compensation valves 15, 16 are disposed within the control valve module 2 and the control valve 3 is relatively close together. In other words, close the two Rücklaufkompensationsventile 15, 16 directly to the control valve 3, so that virtually no or only an extremely small pressure loss is observed between the return compensation valves 15, 16 and the control valve 3.

Jedes Steuerventil 15, 16 weist einen ersten Steuereingang 17a, 17b auf. Der Buchstabe a wird für Bezugszeichen verwendet, die dem Rücklaufkompensationsventil 15 zugeordnet sind. Der Buchstabe b wird für Bezugszeichen verwendet, die dem Rücklaufkompensationsventil 16 zugeordnet sind. Der Steuereingang 17a, 17b steht mit einer Lastfühlleitung 18a, 18b in Verbindung. Die Lastfühlleitung 18a, 18b wird bei einer entsprechenden Auslenkung des Schiebers 4, die eine Verbindung zum Druckanschluß P bewirkt, mit dem gleichen Druck versehen wie der Abschnitt der Arbeitsleitung 13, 14 zwischen dem Rücklaufkompensationsventil 15, 16 und dem Steuerventil 3.Each control valve 15, 16 has a first control input 17a, 17b. The letter a is used for reference numerals associated with the return compensation valve 15. The letter b is used for reference numerals associated with the return compensation valve 16. The control input 17a, 17b communicates with a load sensing line 18a, 18b. The load sensing line 18a, 18b is at a corresponding deflection of the slide 4, which causes a connection to the pressure port P, provided with the same pressure as the portion of the working line 13, 14 between the return compensation valve 15, 16 and the control valve. 3

In die gleiche Richtung wie der Druck am ersten Steuereingang 17a, 17b wirkt die Kraft einer Feder 19a, 19b. Der Druck am ersten Steuereingang 17a, 17b und die Kraft der Feder 19a, 19b wirken in eine Richtung, in der die Rücklaufkompensationsventile 15, 16 öffnen, d.h. ihren Strömungsquerschnitt vergrößern.In the same direction as the pressure at the first control input 17a, 17b acts the force of a spring 19a, 19b. The pressure at the first control input 17a, 17b and the force of the spring 19a, 19b act in a direction in which the return compensation valves 15, 16 open, i. increase their flow cross-section.

In die entgegengesetzte Richtung wirkt ein Druck an einem zweiten Steuereingang 20a, 20b, der mit einem Abschnitt der Arbeitsleitung 13, 14 zwischen dem Rücklaufkompensationsventil 15, 16 und dem Steuerventil 3 verbunden ist.In the opposite direction, a pressure acts on a second control input 20a, 20b, which is connected to a portion of the working line 13, 14 between the Rücklaufkompensationsventil 15, 16 and the control valve 3.

Das Steuerventil 3 richtet in jeder Arbeitsstellung 1, r des Schiebers 4 einen Versorgungspfad 21a, 21b ein, der eine Verbindung zwischen dem Ausgang des Vorlaufkompensationsventils 9 und der entsprechenden Arbeitsleitung 13, 14 bildet. Von dem Versorgungspfad 21a, 21b zweigt ein Steuerpfad 22a, 22b ab, der in die entsprechende Lastfühlleitung 18a, 18b mündet.The control valve 3 establishes in each working position 1, r of the slide 4, a supply path 21 a, 21 b, which forms a connection between the output of the flow compensation valve 9 and the corresponding working line 13, 14. From the supply path 21a, 21b branches off a control path 22a, 22b, which opens into the corresponding load-sensing line 18a, 18b.

Außerdem richtet der Schieber 4 in Abhängigkeit von seiner Stellung für jede Arbeitsstellung 1, r einen Rücklaufpfad 23a, 23b ein, durch den die nicht mit dem Vorlaufkompensationsventil 9 verbundene Arbeitsleitung 13, 14 mit der Tankleitung 8 verbunden wird. In den Rücklaufpfad 23a, 23b mündet ein Entlastungspfad 24a, 24b, in dem ein zur Tankleitung 8 hin öffnendes Rückschlagventil 25a, 25b angeordnet ist. In der entsprechenden Position des Schiebers 4 kommt der Entlastungspfad 24a, 24b in Verbindung mit der Lastfühlleitung 18a, 18b.In addition, the slider 4, depending on its position for each working position 1, r a return path 23 a, 23 b, through which the not connected to the flow compensation valve 9 working line 13, 14 is connected to the tank line 8. In the return path 23a, 23b opens a discharge path 24a, 24b, in which a to the tank line 8 out opening check valve 25a, 25b is arranged. In the corresponding position of the slide 4, the relief path 24a, 24b comes into connection with the load-sensing line 18a, 18b.

Die beiden Lastfühlleitungen 18a, 18b sind durch ein Wechselventil 26 miteinander verbunden, dessen Ausgang mit einem weiteren Wechselventil 27 verbunden ist, das den höchsten in einem hydraulischen System, in dem auch die Ventilanordnung 1 angeordnet ist, herrschenden Druck an einen Lastfühlanschluß LS weitergibt.The two load-sensing lines 18a, 18b are connected to one another by a shuttle valve 26 whose output is connected to a further shuttle valve 27, which passes on the highest pressure prevailing in a hydraulic system, in which the valve arrangement 1 is arranged, to a load-sensing port LS.

Zwischen dem Wechselventil 26 und dem Steuerventil 3 ist für jede Lastfühlleitung 18a, 18b eine Drossel 28a, 28b vorgesehen. Zwischen der Drossel 28a, 28b und dem Wechselventil 26 zweigt eine Leitung mit einem Druckregelventil 29a, 29b ab. Die beiden Druckregelventile 29a, 29b sind mit einem nur schematisch dargestellten Gegendruckventil 30 verbunden, das in der dargestellten Ausgestaltung über einen elektrischen Antrieb 31 aktivierbar ist. Es kann aber auch selbsttätig wirken, in einer anderen Ausgestaltung. Der Antrieb 31 ist mit der Steuerleitung 7 verbunden, so daß das Steuerventil 3 und das Gegendruckventil 30 gemeinsam mit dem gleichen Steuersignal aktiiviert werden können. Das Gegendruckventil 30 ist mit dem Niederdruckanschluß T verbunden. Es sorgt dafür, daß in der jeweiligen Lastfühlleitung 18a, 18b jeweils ein vorbestimmter Mindestdruck herrscht.Between the shuttle valve 26 and the control valve 3, a throttle 28a, 28b is provided for each load-sensing line 18a, 18b. Between the throttle 28a, 28b and the shuttle valve 26 branches off a line with a pressure control valve 29a, 29b. The two pressure control valves 29a, 29b are connected to a counter-pressure valve 30 shown only schematically, which can be activated in the illustrated embodiment via an electric drive 31. But it can also act automatically, in another embodiment. The drive 31 is connected to the control line 7, so that the control valve 3 and the back pressure valve 30 can be activated together with the same control signal. The back pressure valve 30 is connected to the low pressure port T. It ensures that in the respective load-sensing line 18a, 18b in each case a predetermined minimum pressure prevails.

An die beiden Arbeitsanschlüsse A, B ist ein hydraulischer Verbraucher in Form eines hydraulischen Zylinders 32 angeschlossen. Auf den Zylinder wirkt eine durch einen Pfeil 33 dargestellte äußere Kraft. In der zum Arbeitsanschluß B führenden Leitung ist ein Lasthalteventil 34 angeordnet, das in Öffnungsrichtung durch den Druck am Arbeitsanschluß A und den Druck an seinem Eingang und in Schließrichtung durch die Kraft einer Feder 35 beaufschlagt ist. Parallel zum Lasthalteventil 34 ist ein Rückschlagventil 36 angeordnet, das zum Zylinder 32 hin öffnet.To the two working ports A, B, a hydraulic consumer in the form of a hydraulic cylinder 32 is connected. On the cylinder acts an external force represented by an arrow 33. In the line leading to the working port B a load-holding valve 34 is arranged, which is acted upon in the opening direction by the pressure at the working port A and the pressure at its input and in the closing direction by the force of a spring 35. Parallel to the load-holding valve 34, a check valve 36 is arranged, which opens to the cylinder 32 out.

Das Lasthalteventil 34 ist in der Lage, die Leitung zwischen dem Zylinder 32 und dem Steuerventilmodul 2 vollständig zu verschließen. Die Rücklaufkompensationsventile 15, 16 sind nicht unbedingt in der Lage eine vollständige Unterbrechung der Arbeitsleitungen 13, 14 zu bewirken.The load-holding valve 34 is able to completely close the line between the cylinder 32 and the control valve module 2. The Rücklaufkompensationsventile 15, 16 are not necessarily able to cause a complete interruption of the working lines 13, 14.

Die beiden Lastfühlleitungen 18a, 18b sind jeweils über ein Nachsaugventil 37a, 37b mit der Tankleitung verbunden. Die Nachsaugventile 37a, 37b sind als Rückschlagventile ausgebildet, die zum ersten Steuereingang 17a, 17b hin öffnen.The two load-sensing lines 18a, 18b are each connected via a suction valve 37a, 37b to the tank line. The Nachsaugventile 37a, 37b are designed as check valves, which open to the first control input 17a, 17b out.

Die Ventilanordnung arbeitet nun folgendermaßen:The valve assembly now works as follows:

Wenn der Schieber 4 des Steuerventils 3 in die Arbeitsstellung r gebracht wird, dann wird die Arbeitsleitung 13 mit Druck vom Hochdruckanschluß P versorgt. Gleichzeitig wird die Lastfühlleitung 18a mit Druck versorgt. Da nun an den beiden Steuereingängen 17a, 20a des Rücklaufkompensationsventils 15 der gleiche Druck anliegt, wird dieses über die Feder 19a aufgesteuert. Der Zylinder 32 wird nun in seinem oberen Arbeitsraum 38 unter Druck gesetzt. Dabei wird Hydraulikflüssigkeit aus dem unteren Arbeitsraum 39 verdrängt. Dies ist möglich, weil der Druck am Arbeitsanschluß A das Lasthalteventil 34 aufgesteuert hat. Sowohl die Lastfühlleitung 18b als auch der Abschnitt der Arbeitsleitung 14 zwischen dem Rücklaufkompensationsventil 16 und dem Steuerventil 3 sind praktisch drucklos, so daß das Rücklaufkompensationsventil 16 unter der Wirkung der Feder 19b aufsteuert. Die vom Arbeitsraum 39 verdrängte Hydraulikflüssigkeit kann also durch das Steuerventil 3 zum Niederdruckanschluß T abfließen. An dem im Steuerventil vorhandenen, aber nicht näher dargestellten Drosseln baut sich ein Druck auf, der zu einer entsprechenden Druckerhöhung in dem Abschnitt der Arbeitsleitung 14 zwischen dem Rücklaufkompensationsventil 16 und dem Steuerventil 3 führt, der das Rücklaufkompensationsventil 16 stärker drosselt und zwar so, daß ein Gleichgewicht zwischen der Kraft der Feder 19b und dem Druck am zweiten Steuereingang 20b des Rücklaufkompensationsventils 16 hergestellt ist. Das Rücklaufkompensationsventil 16 drosselt also den Rücklauf vom zweiten Arbeitsraum 39 des Hydraulikzylinders 32 so, daß die Steuerung praktisch ausschließlich über das Steuerventil 3 erfolgt.When the slider 4 of the control valve 3 is brought into the working position r, the working line 13 is supplied with pressure from the high-pressure port P. At the same time, the load-sensing line 18a is supplied with pressure. Since the same pressure is present at the two control inputs 17a, 20a of the return compensation valve 15, this is turned on by the spring 19a. The cylinder 32 is now pressurized in its upper working space 38. In this case, hydraulic fluid is displaced from the lower working space 39. This is possible because the pressure at the working port A has opened the load-holding valve 34. Both the load-sensing line 18b and the section of the working line 14 between the return compensation valve 16 and the control valve 3 are practically depressurized, so that the return compensation valve 16 opens under the action of the spring 19b. The displaced from the working space 39 hydraulic fluid can therefore flow through the control valve 3 to the low pressure port T. At the present in the control valve, but not shown throttles, a pressure builds up, which leads to a corresponding increase in pressure in the portion of the working line 14 between the return compensation valve 16 and the control valve 3, which throttles the return compensation valve 16 more so that a Balance between the force of the spring 19b and the pressure at the second control input 20b of the Rücklaufkompensationsventils 16 is made. The return compensation valve 16 thus throttles the return from the second working chamber 39 of the hydraulic cylinder 32 so that the control takes place virtually exclusively via the control valve 3.

In umgekehrter Richtung wird der hydraulische Zylinder 32 dadurch betätigt, daß man das Steuerventil 3 in die Arbeitsstellung 1 bringt. In diesem Fall kann Hydraulikflüssigkeit unter Umgehung des Lasthalteventils 34 über das Rückschlagventil 36 zum Zylinder 32 gelangen. Im "Rücklaufpfad" drosselt dann das Rücklaufkompensationsventil 15 die aus dem ersten Arbeitsraum 38 verdrängte Flüssigkeit so, daß die Betätigung des Zylinders 32 nur durch das Steuerventil 3 gesteuert wird und zwar auch dann, wenn eine Kraft entgegen der Richtung des Pfeiles 33 an dem Zylinder 32 angreifen würde.In the reverse direction of the hydraulic cylinder 32 is actuated by bringing the control valve 3 in the working position 1. In this case, hydraulic fluid, bypassing the load-holding valve 34, can reach the cylinder 32 via the check valve 36. In the "return path" then throttles the return compensation valve 15 displaced from the first working space 38 Liquid so that the operation of the cylinder 32 is controlled only by the control valve 3, even if a force against the direction of the arrow 33 would act on the cylinder 32.

Die Druckregelventile 29a, 29b sorgen in jedem Fall dafür, daß der Druck in den Lastfühlleitungen 18a, 18b einen vorbestimmten Wert nicht übersteigt. Sollte dies der Fall sein, dann wird Hydraulikflüssigkeit zum Niederdruckanschluß T hin abgegeben und zwar über das Gegendruckventil 30. Das Gegendruckventil 30 stellt auf jeden Fall sicher, daß ein ausreichender Druck zur Betätigung des Lasthalteventils 34 vorhanden ist.In any case, the pressure control valves 29a, 29b ensure that the pressure in the load sensing lines 18a, 18b does not exceed a predetermined value. If this is the case, then hydraulic fluid is discharged to the low-pressure port T through the back pressure valve 30. The back pressure valve 30 ensures in any case that sufficient pressure for actuating the load-holding valve 34 is present.

Der jeweils höchste Druck aus den beiden Lastfühlleitungen 18a, 18b wird über die Steuerleitung 11 auf das Vorlaufkompensationsventil 9 gegeben, das dementsprechend genau soweit öffnet, wie es der in den Lastfühlleitungen 18a, 18b anstehende Druck erfordert.The respective highest pressure from the two load-sensing lines 18a, 18b is applied via the control line 11 to the flow compensation valve 9, which accordingly opens exactly as far as the pressure in the load-sensing lines 18a, 18b requires.

Das Lasthalteventil 34 entlastet im vorliegenden Ausführungsbeispiel, bei dem dies mit Hilfe des Gegendruckventils erfolgt, zur Umgebung. Man hat aber bei anderen Ausgestaltungen auch die Möglichkeit, dieses Lasthalteventil zur Arbeitsleitung 14 hin zu entlasten, das Lasthalteventil hermetisch zu verschließen oder zu einem angeschlossenen Proportionalventil oder zum Tank hin zu entlasten.The load-holding valve 34 relieved in the present embodiment, in which this is done with the aid of the back pressure valve, to the environment. However, in other embodiments it is also possible to relieve this load-holding valve to the working line 14, to hermetically close the load-holding valve or to relieve it to a connected proportional valve or to the tank.

Der Schieber des Steuerventils 3 kann anstelle der dargestellten Drucksteuerung auch eine Durchflußsteuerung oder eine gemischte Druck-Durchfluß-Steuerung bewirken.The spool of the control valve 3 may cause a flow control or a mixed pressure flow control instead of the pressure control shown.

Die Anordnung der beiden Rücklaufkompensationsventile 15, 16 in unmittelbarer Nähe des Steuerventils 3 innerhalb des Steuerventilmoduls 2 hat den Vorteil, daß die Gefahr einer Leckage erheblich vermindert wird verglichen mit einer externen Einheit oder einer angeflanschten Einheit, die die Rücklaufkompensationsventile 15, 16 enthält. Bei einer größeren Entfernung vom Steuerventil kann es in der Leitungsführung immer einen Druckverlust geben, der durch die Feder 19a, 19b korrigiert werden müßte. Man weiß aber in der Regel nicht genau, wie groß der Verlust ist. Wenn man hingegen die Rücklaufkompensationsventile 15, 16 so dicht am Steuerventil 3 anordnet, wie im vorliegenden Ausführungsbeispiel, dann hat man praktisch keinen Druckverlust, so daß man eine vollständige Kontrolle über die Toleranzen hat und immer eine gleichmäßige Leistung erreicht.The arrangement of the two Rücklaufkompensationsventile 15, 16 in the immediate vicinity of the control valve 3 within the control valve module 2 has the advantage that the risk of leakage is significantly reduced compared to an external unit or a flanged unit containing the Rücklaufkompensationsventile 15, 16. At a greater distance from the control valve, there may always be a pressure loss in the wiring, which would have to be corrected by the spring 19a, 19b. As a rule, one does not know exactly how big the loss is. If, however, the return compensation valves 15, 16 so close to the control valve 3 arranges, as in the present embodiment, then one has virtually no pressure loss, so that one has complete control over the tolerances and always achieves a uniform performance.

Die Nachsorgventile 37a, 37b und die Rücklaufventile 25a, 25b ermöglichen es, daß der Schieber (oder ein anderes Ventilelement) in den Rücklaufkompensationsventilen 15, 16 außerordentlich schnell reagieren kann. Der Schieber kann nämlich Öl nachsaugen oder verdrängen, ohne daß er hier nennenswerte Widerstände überwinden muß.The aftercare valves 37a, 37b and the return valves 25a, 25b allow the spool (or other valve member) in the return compensation valves 15, 16 to react extremely quickly. The slider can namely suck in or displace oil without having to overcome significant resistance here.

Claims (10)

  1. Hydraulic valve arrangement (1) with a control valve module (2) comprising a supply connection arrangement with a high-pressure connection (P) and a low-pressure connection (T) and a working connection arrangement with two working connections (A, B) as well as a control valve (3) between the supply connection arrangement and the working connection arrangement, the control valve module (2) having a return compensation valve (15, 16) between the control valve (3) and at least one working connection, seen from the control valve (3) a load retaining valve (34) being located at the other side of the return compensation valve (16), which load retaining valve (16) can be opened by means of a pressure at the other working connection (A), the first control inlet (17a, 17b), at least of the return control valve (16), which is connected in series to the load retaining valve (34), being connected to the low-pressure connection (T) via a counter-pressure valve (30), characterised in that the counter-pressure valve (30) is electrically activated, the control valve (3) is electrically activated, and the counter-pressure valve (30) and the control valve (3) react to the same electrical signal.
  2. Valve arrangement according to claim 1, characterised in that the counter-pressure valve (30) is located in the control valve module (2).
  3. Valve arrangement according to claim 1 or 2, characterised in that the return compensation valve (15, 16) is directly connected to an outlet of the control valve (3).
  4. Valve arrangement according to one of the claims 1 to 3, characterised in that the return compensation valve (15, 16) has two control inlets (17a, 17b; 20a, 20b), a first one (17a, 17b) being connected to a load-sensing pipe (18a, 18b) and a second one (20a, 20b) being connected to a point between the control valve (3) and the return compensation valve (15, 16), the first control inlet (17a, 17b) being connected to the low-pressure connection (T) via a suction valve (37a, 37b).
  5. Valve arrangement according to claim 4, characterised in that the first control inlet (17a, 17b) can be connected to the low-pressure connection (T) via a non-return valve (25a, 25b) located in the slide (4) of the control valve (3).
  6. Valve arrangement according to claim 5, characterised in that the non-return valve (25a, 25b) ends in a path in the slide (4), which can be connected to the low-pressure connection (T).
  7. Valve arrangement according to one of the claims 1 to 6, characterised in that a return compensation valve (15, 16) is allocated to each working connection (A, B).
  8. Valve arrangement according to claim 7, characterised in that each first control inlet (17a, 17b) is connected to a pressure control valve (29a, 29b) via a throttle (28a, 28b), the pressure control valves (29a, 29b) being adjustable to different pressures.
  9. Valve arrangement according to claim 8, characterised in that an outlet is connected between the throttle (28a, 28b) and the pressure control valve (29a, 29b) of each return compensation valve (15, 16) to a shuttle valve (26), whose outlet is connected to an inlet of an inlet compensation valve (9) connected in series to the control valve (3).
  10. Valve arrangement according to one of the claims 1 to 9, characterised in that the control valve (3) has a slide (4), which is displaceable into two working positions (l, r) and one floating position (S), a blocking position (u1, u2) being provided between the floating position (S) and each working position (1, r).
EP05009870A 2004-05-19 2005-05-06 Hydraulic valve assembly Not-in-force EP1598560B1 (en)

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CN100354533C (en) 2007-12-12
ATE396340T1 (en) 2008-06-15
DE502005004165D1 (en) 2008-07-03
EP1598560A1 (en) 2005-11-23
CN1699762A (en) 2005-11-23
US7328646B2 (en) 2008-02-12
DE102004025322A1 (en) 2005-12-15

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