EP1245834B1 - Priority hydraulic control device - Google Patents

Priority hydraulic control device Download PDF

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Publication number
EP1245834B1
EP1245834B1 EP20020005603 EP02005603A EP1245834B1 EP 1245834 B1 EP1245834 B1 EP 1245834B1 EP 20020005603 EP20020005603 EP 20020005603 EP 02005603 A EP02005603 A EP 02005603A EP 1245834 B1 EP1245834 B1 EP 1245834B1
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EP
European Patent Office
Prior art keywords
pressure
control device
hydraulic control
working circuit
secondary 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.)
Expired - Lifetime
Application number
EP20020005603
Other languages
German (de)
French (fr)
Other versions
EP1245834A1 (en
Inventor
Gottfried Olbrich
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP1245834A1 publication Critical patent/EP1245834A1/en
Application granted granted Critical
Publication of EP1245834B1 publication Critical patent/EP1245834B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/022—Flow-dividers; Priority valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • 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
    • F15B2211/6055—Load sensing circuits having valve means between output member and the load sensing circuit using pressure relief 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the invention is based on a hydraulic control device according to the closer defined in the preamble of claim 1 Sort of out.
  • A1 is a hydraulic control device with a first working group of load pressure sensing Directional valves and a second control circuit with neutral circulation known in which the distribution of the currents from a pump to both working groups of a working as a pressure compensator Throttle valve is controlled.
  • the throttle valve is located in one Connection between a pump connection or a Pressure medium source to a continuation connection, to the one behind the other the second working group or the secondary working group connected.
  • the flow resistance in Neutral position of the two working groups or control circuits keeps the throttle valve open.
  • a priority working group, called primary working circuit, which with load-pressure-sensing Directional valves in a design with closed center is trained, can be so with the subordinate supplied Working group or secondary working group combine that Energy losses are kept low and versatile adjustments possible are.
  • the throttle valve is in a connection plate of the primary working circuit accommodated, wherein the connection plate a has inlet connection connected to the pressure medium source, of which an inlet channel, bypassing the actual Throttle valve to an opening in a flange the connection plate leads.
  • the throttle valve has three connections and a pressure compensator with two control edges and three qualitatively distinguishable positions on
  • a first position of the pressure compensator slide is the Connection from the pressure medium source to the secondary working circuit and a connection between the pressure medium source and a return line closed.
  • the pressure compensator slide adjusted in the axial direction is from a certain adjustment the connection between the pressure medium source and the secondary working cycle by a first control edge released, indicating a second position of the throttle valve equivalent.
  • With increasing adjustment of the pressure compensator slide in the direction of a third position of the throttle valve will connect from the second control edge between the pressure medium source and a return line to released to a tank.
  • the second position is the normal one Working position of the throttle valve, in which the primary working circle the required pressure medium quantity receives and the remaining quantity flows to the secondary workgroup.
  • the throttle valve has a pressure limiting function for both Working groups.
  • the disadvantage here is that the secondary working group in normal operation in certain operating conditions the entire subsidized Pressure medium flow, even if the valves in this Working group not on the full flow of the pressure medium source are designed.
  • the valves can malfunction in the control one connected to the secondary working group Consumer occur.
  • Such malfunctions occur in particular then, when tongue-led to secondary work Pressure medium flow in the neutral circulation is too large. This leads to excessive pressure drop within the directional control valve block, the unwanted movement speeds of a consumer supplied via the secondary working group Episode has.
  • connection between the pressure medium source and the secondary working group a facility for Rules of the pressure medium supplied to the secondary working group has the advantage that when the connection is open between the pressure medium source and the secondary working circuit a current control for the continuation or a the amount of pressure medium supplied to the secondary working group is adjustable or limited. This is achieved in an advantageous manner that a in the Secondary working group prevailing pressure within certain Pressure drop areas is maintained, which at the same time Movement speeds of over the secondary work circle supplied consumers in a simple way within certain limits.
  • the Device for regulating the secondary working group supplied Pressure medium quantity an orifice, on the regulated to the secondary working pressure medium flow is set and limited. This ensures that the pressure medium quantity from a certain preset Value is limited or cut off and the supply of a impermissibly large pressure medium flow to the secondary working circuit is avoided. It is particularly advantageous that the embodiment of the invention without complicated constructive To apply measures in already developed systems can.
  • FIG. 1 shows an embodiment of the hydraulic control device in a highly simplified circuit design shown and 2 shows a longitudinal section through a connection plate of the hydraulic control device according to FIG. 1.
  • FIG. 1 shows a hydraulic control device 1 with two of a pressure medium source 2, which is designed as a fixed displacement pump acted upon Working groups 3, 4, whereby a primary working group 3 is connected directly to the pressure medium source 2 and a secondary working circuit 4 or a supply of pressure medium to the secondary working circuit 4 via a throttle valve 5 is controlled.
  • Secondary workgroup 4 has a neutral circulation in a so-called "open center” Execution in such a way that in a certain switching position a directional control valve 6 a secondary working circle. 4 via a forwarding 7 supplied pressure medium flow over a return line 8 a pressure medium tank or tank. 9 is forwarded.
  • the throttle valve 5 is in a directional control valve block 10 of the primary working circuit 3 arranged and a pump supply 11 and one of them branching line 12 with the pressure medium source 2 connected.
  • FIG 2 is a part of a structural design the directional control valve block 10 of the primary working circuit 3 in one Longitudinal section shown, wherein the throttle valve 5 with a Pressure compensator slide 13 and a first pressure chamber 14 and a second pressure chamber 15 is executed.
  • the first pressure room 14 and the second pressure chamber 15 are of the directional control valve block 10 and the connection plate of the primary working circuit 3 and the Ends of the pressure compensator valve is limited, with the pressure chamber 14 a first control line 16 and the pressure chamber 15 a ' second control line 17 leads.
  • the first control line 16 branches from the pump supply line 11 from, so that in the first pressure chamber 14, the pump inlet pressure pending.
  • the second control line 17 is provided with a throttle 19 Mistake. This ensures that the pressure in the pressure chamber 15th by a between this and another return line 21 arranged pressure relief valve 20 are limited can.
  • the arrangement of the throttle 19 in the second control line 17 a dynamic stabilization of Pressure compensator slide 13 achieved, especially in pressure fluctuations an attenuation of the response of the pressure compensator valve 13 causes.
  • the damping stops because the pressure medium volume of the second pressure chamber 15, the a force acting on the pressure compensator slide 13 return spring 22 receives, by throttling the throttle 19 only in can exchange a limited speed.
  • the second control line 17 is of a so-called Mittenanschl with a shuttle valve 23, which is between a Pressure tap line 18 and an additional control line 24 is arranged and evaluated the incoming pressure signals and the highest applied pressure signal to the second Pressure chamber 15 forwards.
  • the additional control line 24 stands with another shuttle valve 25 of the primary working group 3 in connection. This means that the shuttle valve 23 responds to an incoming pressure signal and the larger Pressure signal via the center tap to the as a control element formed pressure compensator slide 13 and in the second spring-side Pressure chamber 15 leads.
  • a prioritization of the pressure medium supply between the Primary working group 3 and the secondary working group 4 is about controlling the working as a pressure compensator throttle valve 5, wherein in a connection between the pressure medium source 2 and the secondary working group 4, a device 26 for regulating the the secondary working circuit 4 supplied pressure medium quantity switched is.
  • the device 26 is provided with a metering orifice fixed flow area and two control control edges 27, 31 formed, wherein the orifice of the first control edge 27th downstream of the pressure compensator slide 13, via the also the connection between the pressure medium source 2 and the secondary working circuit 4 is lockable.
  • the orifice is through the annular space between a shoulder 29 on the pressure compensator slide 13 and the hole in which the pressure compensator slide formed, wherein the paragraph 29 by a Ring groove 28 is separated from the control edge 27.
  • the pressure compensator slide 13 has a second control edge 31 for controlling a pressure medium flow from the pressure medium source 2 in the further return line 21.
  • the first Control edge 27 and the second control edge 31 are such in the axial direction of the pressure compensator slide 13 at this provided that at an axial adjustment of the pressure compensator slide 13 due to a pressure gradient applied to this first the connection between the pressure medium source 2 and the secondary working circle 4 and with an increasing adjustment the pressure compensator slide 13 and the connection between the pressure medium source 2 and the further return line 21 is opened.
  • the regulation of the pressure medium flow from the pressure medium source 2 to the secondary working group 4 takes place from an interaction between the flow area of the orifice on the heel 29 and set by the pressure compensator 5 via the orifice plate Pressure gradient.
  • This pressure difference acts as a differential pressure on the two front sides of the pressure compensator slide 13.
  • the pressure compensator slide 13 is against the return spring 22 postponed.
  • This direction of movement of the pressure compensator slide 13 causes the pressure medium flow in the direction the metering orifice flows, is reduced, since the second control edge 31, the connection between the pressure medium source 2 and the further return line 21 releases or further opens.
  • the pressure in the pump supply 11 drops and it turns again the control pressure gradient.
  • the geometric configuration of the device 26 or their Orifice plate may vary depending on the particular application arbitrarily, with the height of the boundary of the pressure medium flow in each case depending on the throttle parameter the orifice is determined.
  • the present Embodiment provides the size of paragraph 29 or whose diameter is the throttle parameter of the metering orifice.
  • the pressure medium source 2 can handle, is the Pressure medium flow to the forwarding 7 limited.
  • the Pressure balance slide 13 such that a reduced pressure medium flow to the directional control valve 6 of the secondary working circuit 4th flows.
  • the excess pressure medium flow flows over the Pressure compensator slide 13 and the further return line 21 to the tank 9 back.
  • one of the directional valves 32A to 320 of the primary working group behaves the hydraulic control device 1 as in a load-sensing parallel connection. Is the pressure in primary workgroup 3 compared to the pressure in the secondary working circuit 4, the higher load pressure in the hydraulic control device 1, so the directional control valve 32A, 32B or 32C primarily supplied with pressure medium, wherein the downstream secondary working circuit 4 only the residual pressure medium flow, via the control edge 27 of the pressure compensator slide 13 throttled flows.

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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)

Description

Stand der TechnikState of the art

Die Erfindung geht von einer hydraulischen Steuereinrichtung gemäß der im Oberbegriff des Patentanspruches 1 näher definierten Art aus.The invention is based on a hydraulic control device according to the closer defined in the preamble of claim 1 Sort of out.

Aus der DE 36 29 471 A1 ist eine hydraulische Steuereinrichtung mit einem ersten Arbeitskreis aus lastdruckfühlenden Wegeventilen und einem zweiten Steuerkreis mit Neutralumlauf bekannt, bei der die Aufteilung der Ströme von einer Pumpe zu beiden Arbeitskreisen von einem als Druckwaage arbeitenden Drosselventil gesteuert wird. Das Drosselventil liegt in einer Verbindung zwischen einem Pumpenanschluß bzw. einer Druckmittelquelle zu einem Weiterlaufanschluß, an den hintereinander der zweite Arbeitskreis bzw. der Sekundärarbeitskreis angeschlossen ist. Der Durchflußwiderstand in Neutralstellung der beiden Arbeitskreise bzw. Steuerkreise hält das Drosselventil offen. Ein vorrangig versorgter Arbeitskreis, genannt Primärarbeitskreis, der mit lastdruckfühlenden Wegeventilen in einer Bauart mit geschlossener Mitte ausgebildet ist, läßt sich derart mit dem nachrangig versorgten Arbeitskreis bzw. Sekundärarbeitskreis kombinieren, daß Energieverluste niedrig gehalten werden und vielseitige Anpassungen möglich sind. From DE 36 29 471 A1 is a hydraulic control device with a first working group of load pressure sensing Directional valves and a second control circuit with neutral circulation known in which the distribution of the currents from a pump to both working groups of a working as a pressure compensator Throttle valve is controlled. The throttle valve is located in one Connection between a pump connection or a Pressure medium source to a continuation connection, to the one behind the other the second working group or the secondary working group connected. The flow resistance in Neutral position of the two working groups or control circuits keeps the throttle valve open. A priority working group, called primary working circuit, which with load-pressure-sensing Directional valves in a design with closed center is trained, can be so with the subordinate supplied Working group or secondary working group combine that Energy losses are kept low and versatile adjustments possible are.

Das Drosselventil ist in einer Anschlußplatte des Primärarbeitskreises untergebracht, wobei die Anschlußplatte einen mit der Druckmittelquelle verbundenen Zulaufanschluß aufweist, von dem ein Zulaufkanal unter Umgehung des eigentlichen Drosselventils zu einer Öffnung in einer Flanschfläche der Anschlußplatte führt. Das Drosselventil weist drei Anschlüsse und einen Druckwaagenschieber mit zwei Steuerkanten und drei qualitativ voneinander unterscheidbare Stellungen aufThe throttle valve is in a connection plate of the primary working circuit accommodated, wherein the connection plate a has inlet connection connected to the pressure medium source, of which an inlet channel, bypassing the actual Throttle valve to an opening in a flange the connection plate leads. The throttle valve has three connections and a pressure compensator with two control edges and three qualitatively distinguishable positions on

In einer ersten Stellung des Druckwaagenschiebers ist die Verbindung von der Druckmittelquelle zu dem Sekundärarbeitskreis sowie eine Verbindung zwischen der Druckmittelquelle und einer Rücklaufleitung geschlossen. Wird der Druckwaagenschieber in axialer Richtung verstellt, wird ab einem bestimmten Verstellweg die Verbindung zwischen der Druckmittelquelle und dem Sekundärarbeitskreis durch eine erste Steuerkante freigegeben, was einer zweiten Stellung des Drosselventils entspricht. Mit zunehmendem Verstellweg des Druckwaagenschieber in Richtung einer dritten Stellung des Drosselventiles wird von der zweiten Steuerkante eine Verbindung zwischen der Druckmittelquelle und einer Rücklaufleitung zu einem Tank freigegeben. Die zweite Stellung ist die normale Arbeitsstellung des Drosselventils, in der der Primärarbeitskreis die geforderte Druckmittelmenge erhält und die Restmenge dem Sekundärarbeitskreis zufließt. In der dritten Stellung hat das Drosselventil eine Druckbegrenzungsfunktion für beide Arbeitskreise. In a first position of the pressure compensator slide is the Connection from the pressure medium source to the secondary working circuit and a connection between the pressure medium source and a return line closed. Will the pressure compensator slide adjusted in the axial direction, is from a certain adjustment the connection between the pressure medium source and the secondary working cycle by a first control edge released, indicating a second position of the throttle valve equivalent. With increasing adjustment of the pressure compensator slide in the direction of a third position of the throttle valve will connect from the second control edge between the pressure medium source and a return line to released to a tank. The second position is the normal one Working position of the throttle valve, in which the primary working circle the required pressure medium quantity receives and the remaining quantity flows to the secondary workgroup. In the third position the throttle valve has a pressure limiting function for both Working groups.

Nachteilig dabei ist, daß dem Sekundärarbeitskreis im Normalbetrieb in bestimmten Betriebszuständen die gesamte geförderte Druckmittelmenge zufließt, auch wenn die Ventile in diesem Arbeitskreis nicht auf den vollen Förderstrom der Druckmittelquelle ausgelegt sind. Bei einer Überschreitung des Nennstromes der Ventile können Fehlfunktionen bei der Ansteuerung eines an dem Sekundärarbeitskreis angeschlossenen Verbrauchers auftreten. Derartige Fehlfunktionen treten insbesondere dann auf, wenn der dem Sekundärarbeitskreis zunge-führte Druckmittelstrom im Neutralumlauf zu groß wird. Dies führt zu einem zu starken Druckabfall innerhalb des Wegeventilblocks, der unerwünschte Bewegungsgeschwindigkeiten eines über den Sekundärarbeitskreis versorgten Verbrauchers zur Folge hat.The disadvantage here is that the secondary working group in normal operation in certain operating conditions the entire subsidized Pressure medium flow, even if the valves in this Working group not on the full flow of the pressure medium source are designed. When exceeding the rated current the valves can malfunction in the control one connected to the secondary working group Consumer occur. Such malfunctions occur in particular then, when tongue-led to secondary work Pressure medium flow in the neutral circulation is too large. This leads to excessive pressure drop within the directional control valve block, the unwanted movement speeds of a consumer supplied via the secondary working group Episode has.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße hydraulische Steuereinrichtung der eingangs beschriebenen Art mit den Merkmalen des Patentanspruches 1, bei der die Verbindung zwischen der Druckmittelquelle und dem Sekundärarbeitskreis eine Einrichtung zum Regeln einer dem Sekundärarbeitskreis zugeführten Druckmittelmenge aufweist, hat den Vorteil, daß bei geöffneter Verbindung zwischen der Druckmittelquelle und dem Sekundärarbeitskreis eine Stromregelung für den Weiterlauf bzw. eine dem Sekundärarbeitskreis zugeführte Druckmittelmenge geregelt einstellbar bzw. begrenzbar ist. Damit wird in vorteilhafter Weise erreicht, daß ein in dem Sekundärarbeitskreis vorherrschender Druck innerhalb bestimmter Druckabfallbereiche gehalten wird, womit gleichzeitig Bewegungsgeschwindigkeiten von über den Sekundärarbeitskreis versorgten Verbrauchern auf einfache Art und Weise innerhalb bestimmter Grenzen gehalten werden können.The inventive hydraulic control device of the above described type with the features of claim 1, in which the connection between the pressure medium source and the secondary working group a facility for Rules of the pressure medium supplied to the secondary working group has the advantage that when the connection is open between the pressure medium source and the secondary working circuit a current control for the continuation or a the amount of pressure medium supplied to the secondary working group is adjustable or limited. This is achieved in an advantageous manner that a in the Secondary working group prevailing pressure within certain Pressure drop areas is maintained, which at the same time Movement speeds of over the secondary work circle supplied consumers in a simple way within certain limits.

In einer vorteilhaften Ausgestaltung der Erfindung weist die Einrichtung zum Regeln der dem Sekundärarbeitskreis zugeführten Druckmittelmenge eine Meßblende auf, über die der dem Sekundärarbeitskreis zugeführte Druckmittelstrom geregelt eingestellt und begrenzt wird. Dadurch ist gewährleistet, daß die Druckmittelmenge ab einem bestimmten voreingestellten Wert begrenzt bzw. abgeschnitten wird und die Zuführung eines unzulässig großen Druckmittelstromes zu dem Sekundärarbeitskreis vermieden wird. Besonders vorteilhaft ist dabei, daß die Ausgestaltung der Erfindung ohne aufwendige konstruktive Maßnahmen in bereits entwickelten Systemen Anwendung finden kann.In an advantageous embodiment of the invention, the Device for regulating the secondary working group supplied Pressure medium quantity an orifice, on the regulated to the secondary working pressure medium flow is set and limited. This ensures that the pressure medium quantity from a certain preset Value is limited or cut off and the supply of a impermissibly large pressure medium flow to the secondary working circuit is avoided. It is particularly advantageous that the embodiment of the invention without complicated constructive To apply measures in already developed systems can.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject The invention are the description, the drawing and the claims removed.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel der hydraulischen Steuereinrichtung dargestellt und wird in der nachfolgenden Beschreibung näher erläutert. In the drawing is an embodiment of the hydraulic Control device shown and will in the following Description explained in more detail.

Es zeigen Figur 1 ein Ausführungsbeispiel der hydraulischen Steuereinrichtung in einer stark vereinfacht dargestellten Schaltungsausführung und
Figur 2 einen Längsschnitt durch eine Anschlußplatte der hydraulischen Steuereinrichtung nach Fig. 1.1 shows an embodiment of the hydraulic control device in a highly simplified circuit design shown and
2 shows a longitudinal section through a connection plate of the hydraulic control device according to FIG. 1.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in Figur 1 dargestellte Ausführungsbeispiel zeigt eine hydraulische Steuereinrichtung 1 mit zwei von einer Druckmittelquelle 2, welche als Konstantpumpe ausgebildet ist, beaufschlagbaren Arbeitskreisen 3, 4, wobei ein Primärarbeitskreis 3 direkt mit der Druckmittelquelle 2 verbunden ist und ein Sekundärarbeitskreis 4 bzw. eine Zufuhr von Druckmittel zu dem Sekundärarbeitskreis 4 über ein Drosselventil 5 gesteuert wird.The embodiment shown in Figure 1 shows a hydraulic control device 1 with two of a pressure medium source 2, which is designed as a fixed displacement pump acted upon Working groups 3, 4, whereby a primary working group 3 is connected directly to the pressure medium source 2 and a secondary working circuit 4 or a supply of pressure medium to the secondary working circuit 4 via a throttle valve 5 is controlled.

In dem Primärarbeitskreis 3 wird ein variabler Lastdruck in Verbraucheranschlüssen 6A bis GE abgetastet und in einer Regelung weiterverarbeitet, so daß der Primärarbeitskreis 3 als ein lastfühlendes System bzw. als ein sogenanntes "load sensing"-System ausgebildet ist. Der Sekundärarbeitskreis 4 weist einen Neutralumlauf in einer sogenannten "open center" Ausführung dergestalt auf, daß in einer bestimmten Schaltstellung eines Wegeventils 6 ein dem Sekundärarbeitskreis 4 über eine Weiterleitung 7 zugeführter Druckmittelstrom über eine Rücklaufleitung 8 einem Druckmittelbehälter bzw. Tank 9 zugeleitet wird. In the primary working circuit 3, a variable load pressure in Load connections 6A to GE sampled and in a scheme further processed, so that the primary working group 3 as a load-sensing system or as a so-called "load sensing" system is trained. Secondary workgroup 4 has a neutral circulation in a so-called "open center" Execution in such a way that in a certain switching position a directional control valve 6 a secondary working circle. 4 via a forwarding 7 supplied pressure medium flow over a return line 8 a pressure medium tank or tank. 9 is forwarded.

Das Drosselventil 5 ist in einem Wegeventilblock 10 des Primärarbeitskreises 3 angeordnet und über eine Pumpenzuleitung 11 und eine davon abzweigende Leitung 12 mit der Druckmittelquelle 2 verbunden.The throttle valve 5 is in a directional control valve block 10 of the primary working circuit 3 arranged and a pump supply 11 and one of them branching line 12 with the pressure medium source 2 connected.

In der Figur 2 ist ein Teil einer konstruktiven Ausgestaltung des Wegeventilblockes 10 des Primärarbeitskreises 3 in einem Längsschnitt dargestellt, wobei das Drosselventil 5 mit einem Druckwaagenschieber 13 und einem ersten Druckraum 14 und einem zweiten Druckraum 15 ausgeführt ist. Der erste Druckraum 14 und der zweite Druckraum 15 sind von dem Wegeventilblock 10 bzw. der Anschlußplatte des Primärarbeitskreises 3 und den Enden des Druckwaagenschiebers begrenzt, wobei zum Druckraum 14 eine erste Steuerleitung 16 und zum Druckraum 15 eine' zweite Steuerleitung 17 führt.In the figure 2 is a part of a structural design the directional control valve block 10 of the primary working circuit 3 in one Longitudinal section shown, wherein the throttle valve 5 with a Pressure compensator slide 13 and a first pressure chamber 14 and a second pressure chamber 15 is executed. The first pressure room 14 and the second pressure chamber 15 are of the directional control valve block 10 and the connection plate of the primary working circuit 3 and the Ends of the pressure compensator valve is limited, with the pressure chamber 14 a first control line 16 and the pressure chamber 15 a ' second control line 17 leads.

Die erste Steuerleitung 16 zweigt von der Pumpenzuleitung 11 ab, so daß in dem ersten Druckraum 14 der Pumpenzulaufdruck ansteht. Die zweite Steuerleitung 17 ist mit einer Drossel 19 versehen. Diese stellt sicher, daß der Druck im Druckraum 15 durch ein zwischen diesem und einer weiteren Rücklaufleitung 21 angeordnetes Druckbegrenzungsventil 20 begrenzt werden kann.The first control line 16 branches from the pump supply line 11 from, so that in the first pressure chamber 14, the pump inlet pressure pending. The second control line 17 is provided with a throttle 19 Mistake. This ensures that the pressure in the pressure chamber 15th by a between this and another return line 21 arranged pressure relief valve 20 are limited can.

Darüber hinaus wird über die Anordnung der Drossel 19 in der zweiten Steuerleitung 17 eine dynamische Stabilisierung des Druckwaagenschiebers 13 erreicht, die insbesondere bei Druckschwankungen eine Dämpfung des Ansprechverhaltens des Druckwaagenschiebers 13 bewirkt. Die Dämpfung stellt sich ein, da sich das Druckmittelvolumen des zweiten Druckraumes 15, der eine auf den Druckwaagenschieber 13 einwirkende Rückstellfeder 22 aufnimmt, durch die Drosselung der Drossel 19 nur in einer begrenzten Geschwindigkeit austauschen kann.In addition, the arrangement of the throttle 19 in the second control line 17 a dynamic stabilization of Pressure compensator slide 13 achieved, especially in pressure fluctuations an attenuation of the response of the pressure compensator valve 13 causes. The damping stops, because the pressure medium volume of the second pressure chamber 15, the a force acting on the pressure compensator slide 13 return spring 22 receives, by throttling the throttle 19 only in can exchange a limited speed.

Die zweite Steuerleitung 17 geht von einem sogenannten Mittenanschlüß eines Wechselventils 23 aus, das zwischen einer Druckabgriffsleitung 18 und einer zusätzlichen Steuerleitung 24 angeordnet ist und die ankommenden Drucksignale bewertet und das jeweils höchste anliegende Drucksignal zu dem zweiten Druckraum 15 weiterleitet. Die zusätzliche Steuerleitung 24 steht mit einem weiteren Wechselventil 25 des Primärarbeitskreises 3 in Verbindung. Das bedeutet, daß das Wechselventil 23 auf ein eingehendes Drucksignal reagiert und das größere Drucksignal über den Mittenabgriff zu dem als Regelelement ausgebildeten Druckwaagenschieber 13 bzw. in den zweiten federseitigen Druckraum 15 führt.The second control line 17 is of a so-called Mittenanschlüß a shuttle valve 23, which is between a Pressure tap line 18 and an additional control line 24 is arranged and evaluated the incoming pressure signals and the highest applied pressure signal to the second Pressure chamber 15 forwards. The additional control line 24 stands with another shuttle valve 25 of the primary working group 3 in connection. This means that the shuttle valve 23 responds to an incoming pressure signal and the larger Pressure signal via the center tap to the as a control element formed pressure compensator slide 13 and in the second spring-side Pressure chamber 15 leads.

Eine Priorisierung der Druckmittelversorgung zwischen dem Primärarbeitskreis 3 und dem Sekundärarbeitskreis 4 wird über das als Druckwaage arbeitende Drosselventil 5 gesteuert, wobei in eine Verbindung zwischen der Druckmittelquelle 2 und dem Sekundärarbeitskreis 4 eine Einrichtung 26 zum Regeln der dem Sekundärarbeitskreis 4 zugeführten Druckmittelmenge geschaltet ist. Die Einrichtung 26 ist mit einer Meßblende mit festem Durchflußquerschnitt und zwei Regelsteuerkanten 27, 31 ausgebildet, wobei die Meßblende der ersten Steuerkante 27 des Druckwaagenschiebers 13 nachgeordnet ist, über die auch die Verbindung zwischen der Druckmittelquelle 2 und dem Sekundärarbeitskreis 4 sperrbar ist. Die Meßblende wird durch den ringförmigen Freiraum zwischen einem Absatz 29 am Druckwaagenschieber 13 und der Bohrung, in der sich der Druckwaagenschieber befindet, gebildet, wobei der Absatz 29 durch eine Ringnut 28 von der Steuerkante 27 getrennt ist.A prioritization of the pressure medium supply between the Primary working group 3 and the secondary working group 4 is about controlling the working as a pressure compensator throttle valve 5, wherein in a connection between the pressure medium source 2 and the secondary working group 4, a device 26 for regulating the the secondary working circuit 4 supplied pressure medium quantity switched is. The device 26 is provided with a metering orifice fixed flow area and two control control edges 27, 31 formed, wherein the orifice of the first control edge 27th downstream of the pressure compensator slide 13, via the also the connection between the pressure medium source 2 and the secondary working circuit 4 is lockable. The orifice is through the annular space between a shoulder 29 on the pressure compensator slide 13 and the hole in which the pressure compensator slide formed, wherein the paragraph 29 by a Ring groove 28 is separated from the control edge 27.

An den Absatz 29 des Druckwaagenschiebers 13 schließt sich ein Ringraum 30 der Weiterleitung 7 an, von dem die Druckabgriffsleitung 18 zu dem Wechselventil 23 abzweigt, so daß ein Lastdruck in der Verbindung zwischen der Druckmittelquelle 2 und dem Sekundärarbeitskreis 4 in der Weiterleitung 7 stromab der Meßblende der Einrichtung 26 dem Wechselventil 23 zugeführt werden kann.At paragraph 29 of the pressure compensator slide 13 closes an annular space 30 of the forwarding 7, from which the pressure tapping line 18 branches off to the shuttle valve 23, so that a Load pressure in the connection between the pressure medium source 2 and the secondary working circuit 4 in the forwarding 7 downstream the metering orifice of the device 26 is supplied to the shuttle valve 23 can be.

Weiter weist der Druckwaagenschieber 13 eine zweite Steuerkante 31 zum Steuern eines Druckmittelstromes von der Druckmittelquelle 2 in die weitere Rücklaufleitung 21 auf. Die erste Steuerkante 27 und die zweite Steuerkante 31 sind derart in axialer Richtung des Druckwaagenschiebers 13 an diesem vorgesehen, daß bei einer axialen Verstellung des Druckwaagenschiebers 13 aufgrund eines an diesem anliegenden Druckgefälles zuerst die Verbindung zwischen der Druckmittelquelle 2 und dem Sekundärarbeitskreis 4 und bei einer zunehmenden Verstellung des Druckwaagenschiebers 13 auch die Verbindung zwischen der Druckmittelquelle 2 und der weiteren Rücklaufleitung 21 geöffnet wird.Next, the pressure compensator slide 13 has a second control edge 31 for controlling a pressure medium flow from the pressure medium source 2 in the further return line 21. The first Control edge 27 and the second control edge 31 are such in the axial direction of the pressure compensator slide 13 at this provided that at an axial adjustment of the pressure compensator slide 13 due to a pressure gradient applied to this first the connection between the pressure medium source 2 and the secondary working circle 4 and with an increasing adjustment the pressure compensator slide 13 and the connection between the pressure medium source 2 and the further return line 21 is opened.

Mit dieser Abstimmung des Abstandes der Steuerkanten 27, 31 zueinander bzw. der mit den beiden Steuerkanten 27, 31 korrespondierenden Gehäusekanten in Verbindung mit der Meßblende am Absatz 29 wird die Stromregelung der Druckmittelmenge von der Druckmittelquelle 2 zu dem Sekundärarbeitskreis 4 vorgenommen und ein maximaler Druckmittelstrom eingestellt. Damit wird die dem Sekundärarbeitskreis 4 zugeführte Druckmittelmenge auf einen zulässigen oberen Wert begrenzt. Der darüber hinausgehende Druckmittelstrom wird, soweit er nicht vom Primärarbeitskreis benötigt wird, dem Tank 9 zugeführt.With this vote of the distance of the control edges 27, 31 to each other or with the two control edges 27, 31 corresponding Housing edges in conjunction with the orifice plate at paragraph 29, the flow control of the pressure medium quantity of the pressure medium source 2 made to the secondary working circuit 4 and set a maximum pressure medium flow. In order to is the secondary working circuit 4 supplied amount of pressure medium limited to a permissible upper value. The above Outgoing pressure medium flow is, as far as it is not from the primary working group is needed, the tank 9 fed.

Die Regelung des Druckmittelstromes von der Druckmittelquelle 2 zu dem Sekundärarbeitskreis 4 erfolgt aus einem Zusammenspiel zwischen dem Durchflußquerschnitt der Meßblende am Absatz 29 und dem von der Druckwaage 5 über die Meßblende eingestellten Druckgefälle. Dieses Druckgefälle wirkt als Differenzdruck auf die beiden Stirnseiten des Druckwaagenschiebers 13. Im Falle eines zu großen Druckmittelstromes steigt das Druckgefälle an. Daraus resultieren wiederum unterschiedliche Drücke an den beiden Stirnseiten des Druckwaagenschiebers 13, und der Druckwaagenschieber 13 wird gegen die Rückstellfeder 22 verschoben. Diese Bewegungsrichtung des Druckwaagenschiebers 13 führt dazu, daß der Druckmittelstrom, der in Richtung der Meßblende strömt, verringert wird, da die zweite Steuerkante 31 die Verbindung zwischen der Druckmittelquelle 2 und der weiteren Rücklaufleitung 21 freigibt oder weiter öffnet. Der Druck in der Pumpenzuleitung 11 sinkt und es stellt sich wieder das Regeldruckgefälle ein.The regulation of the pressure medium flow from the pressure medium source 2 to the secondary working group 4 takes place from an interaction between the flow area of the orifice on the heel 29 and set by the pressure compensator 5 via the orifice plate Pressure gradient. This pressure difference acts as a differential pressure on the two front sides of the pressure compensator slide 13. In the case of too large pressure medium flow that increases Pressure gradient on. This in turn results in different ones Press on the two end faces of the pressure compensator slide 13, and the pressure compensator slide 13 is against the return spring 22 postponed. This direction of movement of the pressure compensator slide 13 causes the pressure medium flow in the direction the metering orifice flows, is reduced, since the second control edge 31, the connection between the pressure medium source 2 and the further return line 21 releases or further opens. The pressure in the pump supply 11 drops and it turns again the control pressure gradient.

Die geometrische Ausgestaltung der Einrichtung 26 bzw. deren Meßblende kann in Abhängigkeit des jeweilig vorliegenden Anwendungsfalles beliebig erfolgen, wobei die Höhe der Begrenzung des Druckmittelstromes jeweils in Abhängigkeit des Drosselparameters der Meßblende bestimmt wird. Im vorliegenden Ausführungsbeispiel stellt die Größe des Absatzes 29 bzw. dessen Durchmesser den Drosselparameter der Meßblende dar.The geometric configuration of the device 26 or their Orifice plate may vary depending on the particular application arbitrarily, with the height of the boundary of the pressure medium flow in each case depending on the throttle parameter the orifice is determined. In the present Embodiment provides the size of paragraph 29 or whose diameter is the throttle parameter of the metering orifice.

Wenn die vorbeschriebene hydraulische Steuereinrichtung beispielsweise für ein Hubwerk eines Traktors verwendet wird und ein Regelventil für das Hubwerk nicht den vollen Pümpenförderstrom der Druckmittelquelle 2 verarbeiten kann, wird der Druckmittelstrom zu der Weiterleitung 7 begrenzt. Wird keines der Wegeventile 6 bzw. 32A bis 32C des Primärarbeitskreises 3 und des Sekundärarbeitskreises 4 betätigt, so stellt sich der Druckwaagenschieber 13 derart ein, daß ein reduzierter Druckmittelstrom zu dem Wegeventil 6 des Sekundärarbeitskreises 4 fließt. Der überschüssige Drucianittelstrom fließt über den Druckwaagenschieber 13 und der weiteren Rücklaufleitung 21 zu dem Tank 9 zurück.For example, if the above-described hydraulic control device is used for a hoist of a tractor and a control valve for the hoist not the full Pümpenförderstrom the pressure medium source 2 can handle, is the Pressure medium flow to the forwarding 7 limited. Will not the directional control valves 6 and 32A to 32C of the primary working group 3rd and the secondary working group 4 is actuated, then the Pressure balance slide 13 such that a reduced pressure medium flow to the directional control valve 6 of the secondary working circuit 4th flows. The excess pressure medium flow flows over the Pressure compensator slide 13 and the further return line 21 to the tank 9 back.

Bei einer Betätigung des Wegeventils 6 des Sekundärarbeitskreises 4 bleibt die Versorgung des Sekundärarbeitskreises 4 mit einer Druckmittelmenge gleich, da das Wegeventil 6 den geregelten Druckmittelstrom selbst auf Druck bringt und dessen angeschlossenen Verbraucher versorgt.Upon actuation of the directional control valve 6 of the secondary working circuit 4 remains the supply of secondary work 4 with a pressure medium amount equal because the directional control valve 6 the regulated pressure medium flow itself puts pressure on and its powered consumers.

Wenn eines der Wegeventile 32A bis 320 des Primärarbeitskreises betätigt wird, verhält sich die hydraulische Steuereinrichtung 1 wie bei einer lastfühlenden Parallelschaltung. Ist der Druck im Primärarbeitskreis 3 im Vergleich zu dem Druck in dem Sekundärarbeitskreis 4 der höhere Lastdruck in der hydraulischen Steuereinrichtung 1, so wird das Wegeventil 32A, 32B oder 32C vorrangig mit Druckmittel versorgt, wobei dem nachgeschalteten Sekundärarbeitskreis 4 lediglich der Restdruckmittelstrom, über die Steuerkante 27 des Druckwaagenschiebers 13 abgedrosselt zufließt.If one of the directional valves 32A to 320 of the primary working group is actuated, behaves the hydraulic control device 1 as in a load-sensing parallel connection. Is the pressure in primary workgroup 3 compared to the pressure in the secondary working circuit 4, the higher load pressure in the hydraulic control device 1, so the directional control valve 32A, 32B or 32C primarily supplied with pressure medium, wherein the downstream secondary working circuit 4 only the residual pressure medium flow, via the control edge 27 of the pressure compensator slide 13 throttled flows.

Ist der Druck in dem Primärarbeitskreis 3 der niedrigere Lastdruck, so ist die Versorgung des Primärarbeitskreises mit einer ausreichenden Druckmittelmenge ohnehin gewährleistet.Is the pressure in the primary working circuit 3 the lower Load pressure, so is the supply of primary work with Ensures a sufficient amount of pressure medium anyway.

Erreicht der an die Federseite der Druckwaage 5 gemeldete Lastdruck einen am Druckbegrenzungsventil 20 eingestellten Grenzwert, so hält das Druckbegrenzungsventil den federseitig auf den Druckwaagenschieber 13 wirkenden Druck im Zusammenspiel mit der Düse 19 auf dem Grenzwert. Der Druck in der Pumpenzuleitung steigt nur um das Druckäquivalent der Regelfeder 22 über diesen Grenzwert an, so daß sich eine Druckbegrenzung für die Steuereinrichtung ergibt. Alle geförderte Druckmittelmerige, die zu einer Druckerhöhung im System führen würde, fließt über die Steuerkante 31 des Druckwaagenschiebers 13 direkt zum Tank zurück.Reached to the spring side of the pressure compensator 5 reported Load pressure one set on the pressure relief valve 20 Limit value, the pressure relief valve holds the spring side acting on the pressure compensator slide 13 pressure in interaction with the nozzle 19 at the limit. The pressure in the Pump supply increases only by the pressure equivalent of the control spring 22 above this limit, so that there is a pressure limit for the controller results. All sponsored Pressure medium remarks, which lead to an increase in pressure in the system would, flows over the control edge 31 of the pressure compensator slide 13 directly back to the tank.

Claims (12)

  1. Hydraulic control device (1), with at least two working circuits (3, 4) capable of being acted upon by a pressure-medium source (2), in a primary working circuit (3) supplied as priority with pressure medium a variable load pressure being sensed in consumer connections (6A to 6E) and being further processed in an automatic control, and a secondary working circuit (4) having a neutral circulation, prioritization of the pressure-medium supply between the primary working circuit (3) and the secondary working circuit (4) being controllable via a throttle valve (5) operating as a pressure balance and having a pressure-balance slide (13), the primary working circuit (3) being connected directly to the pressure-medium source (2), and a feed of pressure medium to the secondary working circuit (4) being controlled via the throttle valve (5), characterized in that the connection between the pressure-medium source (2) and the secondary working circuit (4) has a device (26) for regulating a pressure-medium quantity fed to the secondary working circuit (4).
  2. Hydraulic control device according to Claim 1, characterized in that the device (26) has a measuring diaphragm.
  3. Hydraulic control device according to Claim 2, characterized in that the device (26) has two regulating control edges.
  4. Hydraulic control device according to Claim 2 or 3, characterized in that the measuring diaphragm directly follows a first control edge (27) of the pressure-balance slide (13), via which control edge the connection between the pressure-medium source (2) and the secondary working circuit (4) can be shut off.
  5. Hydraulic control device according to one of Claims 2 to 4, characterized in that the measuring diaphragm constitutes a combination of an annular groove (28) with a corresponding shoulder (29) on the pressure-balance slide (13).
  6. Hydraulic control device according to one of Claims 2 to 5, characterized in that a load pressure in the connection between the pressure-medium source (2) and the secondary working circuit (4) can be fed to a shuttle valve (23) via a pressure pick-up line (18) branching off downstream of the measuring diaphragm.
  7. Hydraulic control device according to Claim 6, characterized in that the pressure-medium stream of the pressure pick-up line (18) can be fed via the shuttle valve (23) to a pressure space (15) of the throttle valve (5) in which a spring-loaded end of the pressure-balance slide (13) is arranged.
  8. Hydraulic control device according to Claim 7, characterized in that a pressure-limiting valve (20) is connected to the spring-loaded pressure space (15) in order to limit a maximum load pressure in the secondary working circuit (4).
  9. Hydraulic control device according to Claim 8, characterized in that a throttle (19) for setting a pressure gradient is provided between the shuttle valve (23) and the spring-loaded pressure space (15).
  10. Hydraulic control device according to one of Claims 1 to 9, characterized in that the pressure-balance slide (13) has a second control edge (31) for controlling a pressure-medium stream from the pressure-medium source (2) into a return line (21).
  11. Hydraulic control device according to Claim 10, characterized in that the first control edge (27) and the second control edge (31) are arranged on the pressure-balance slide (13) in such a way that, in the event of an axial adjustment of the pressure-balance slide (13) counter to its spring, first the connection between the pressure-medium source (2) and the secondary working circuit (4) is opened and, in the event of increasing adjustment, the connection between the pressure-medium source (2) and the return line (21) is also opened.
  12. Hydraulic control device according to one of Claims 7 to 11, characterized in that the throttle valve (5) has a pressure space (14) which is connected to the pressure-medium source (2) and which is delimited by an end of the pressure-balance slide (13) which faces away from the spring-loaded end and a housing (10) surrounding the pressure-balance slide (13).
EP20020005603 2001-03-29 2002-03-12 Priority hydraulic control device Expired - Lifetime EP1245834B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10115650 2001-03-29
DE2001115650 DE10115650A1 (en) 2001-03-29 2001-03-29 Hydraulic control device

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EP1245834B1 true EP1245834B1 (en) 2005-09-14

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Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITMO20020332A1 (en) 2002-11-15 2004-05-16 Studio Tecnico 6M Srl FLUID DYNAMIC CIRCUIT FOR THE SUPPLY OF PRIMARY AND AUXILIARY USERS WITH PREDEFINED PRIORITIES.
DE102004048684A1 (en) 2004-10-06 2006-04-13 Bosch Rexroth Ag Hydraulic control arrangement
DE102006008940A1 (en) * 2006-02-23 2007-08-30 Robert Bosch Gmbh Hydraulic control arrangement for actuating multiple consumers, has input pressure balance provided in pressure medium flow path between pump and one of two consumers
DE102020210441A1 (en) 2020-08-17 2022-02-17 Hawe Hydraulik Se Proportional spool valve with a pressure relief valve, pressure relief valve and hydraulic system

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Publication number Priority date Publication date Assignee Title
DE3629471A1 (en) * 1986-08-29 1988-03-03 Bosch Gmbh Robert Hydraulic control arrangement
DE4237932C2 (en) * 1992-11-10 1997-12-11 Hydraulik Ring Gmbh Volume flow control for automotive hydraulics, in particular for steering devices of motor vehicles

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