EP0816689B1 - Hydraulic control system - Google Patents

Hydraulic control system Download PDF

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Publication number
EP0816689B1
EP0816689B1 EP97110053A EP97110053A EP0816689B1 EP 0816689 B1 EP0816689 B1 EP 0816689B1 EP 97110053 A EP97110053 A EP 97110053A EP 97110053 A EP97110053 A EP 97110053A EP 0816689 B1 EP0816689 B1 EP 0816689B1
Authority
EP
European Patent Office
Prior art keywords
pressure
line
valve
throttle
return
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
EP97110053A
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German (de)
French (fr)
Other versions
EP0816689A1 (en
Inventor
Rudolf Oberingenieur Brunner
Martin Dipl.-Ing. Univ. Heusser
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
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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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66C—CRANES; LOAD-ENGAGING ELEMENTS OR DEVICES FOR CRANES, CAPSTANS, WINCHES, OR TACKLES
    • B66C13/00—Other constructional features or details
    • B66C13/18—Control systems or devices
    • 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
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant 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
    • F15B2211/405—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
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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

Definitions

  • the invention relates to a hydraulic control device according to the preamble of Claim 1.
  • the inflow regulator is additionally attached valve components acting on each proportional directional control valve, which is the normal control cycle of the inlet controller in certain operating conditions change. This either avoids an excessive quantity requirement a directional control valve that stops the largest load moving consumer in an uncontrolled manner, or achieves the speed of a consumer in favor of speed of another consumer who needs priority at this point in time being affected.
  • These additional components are automatically influenced in Dependence on changes in the pressure difference between the supply pressure and the highest load pressure.
  • the invention has for its object a hydraulic control device of the beginning to create the kind that is structurally simple at times Increased load torque for a hoist and an extended one for the hoist Area of application.
  • the speed is at uniformly reduced to all consumers whose proportional directional control valves downstream of the throttle.
  • the amount limitation given when the throttle is engaged adapt exactly to the respective application.
  • the switching valve brings the quantity-limiting in its blocking position Throttle to the effect.
  • the check valve ensures that when engaged the throttle isolates the pressure relief valve and the maximum provided Pressure is usable. If the switching valve is switched to the through position, then the throttle is bypassed and the pressure medium takes the path via the line loop, where the maximum quantity controlled by the three-way controller is the maximum Allows consumer speed. Every consumer will find out about his Inlet controller allocated the required amount regardless of the load, which depends on the Adjustment of the proportional directional control valve.
  • the inlet regulator maintains the pressure difference Constant regardless of load via the proportional directional control valve.
  • the pressure relief valve however limits the pressure that can then be used. and therefore the size the liftable loads.
  • Manufacturing and assembly technology is the intermediate plate downstream according to claim 4 of the housing or housings installed in the battery arrangement, its or its consumers there is no need to limit movement speed or pressure.
  • the switching valve with which the throttle in the pump line can be bypassed, is expediently actuated magnetically, on the control side during operation the control device.
  • the switching valve it is also possible for the switching valve to be dependent on the load pressure to adjust.
  • FIG. 1 shows a block diagram of a hydraulic control device S for Hoist like a mobile crane, with which, for example, even in special application situations a lifting cage is manipulated.
  • the control device S has individual, block-shaped housings 1, 3 and at least one Intermediate plate 2, which is combined in a battery assembly 4 (control block) are.
  • the housings 1 are proportional directional control valves P1, P2, P3 with their inlet regulators Z and other components.
  • the housings 1, 3 and the intermediate plates 2 are screwed together on their connection sides, so that all consumers V, e.g. Hydraulic motors or hydraulic cylinders, to a common pump line P are connected.
  • a common one runs in the battery arrangement 4 Return line R to a tank 6.
  • the pressure supply takes place, for example via a pump 5, e.g. a constant pump.
  • Each proportional directional control valve P1, P2, P3 is connected to the pump line via a connection line 7 containing the inlet regulator Z. P connected. Return connecting lines 8 lead from the return line R. to the proportional directional control valves P1, P2, P3.
  • Each consumer V is over two (or only one) working lines A, B to the associated proportional directional control valve P1, P2, P3 connected and used for moving, e.g. Lifting a load L.
  • the inlet regulator Z is a two-way regulator, which works like a pressure compensator in the closing direction via a control line 9 with the pending at the proportional directional control valve P1 Pressure and in the opening direction via a control line 10 with that from one of the working lines A, B derived load pressure and acted upon by a control spring 11 becomes.
  • the control line 10 is via a control line branch 12 and a shuttle valve 13 connected to a common load pressure control line 14 through the housing 1 and the intermediate plate 2 extends into the housing 3. Because of the shuttle valves 13, the load pressure control line 14 carries the currently highest load pressure.
  • a three-way controller D of conventional design is arranged, one as a pressure compensator Working control piston 15 has the aperture of the passage of a connecting channel 16 monitored between the pump line P and the return line R. and depending on its current position, more or less or none at all Drain the pressure medium from the pump line P into the return line R.
  • the control piston 15 is in the opening direction of the three-way controller (to reduce the pressure in the Pump line P) is acted upon by the pressure in the pump line via a control line 17 (Opening side of the three-way controller).
  • the control piston 15 On the closing side and in the closing direction of the three-way controller, on the other hand, the control piston 15 is controlled by a control spring 18 and pressurized in a control line 19 via a damping system C is connected to the load pressure control line 14.
  • a damping throttle 20 is contained, which by means of two opposing Check valves 21 and 23 can be bypassed in each flow direction. Between the damping throttle 20 and the nearest shuttle valve 13 in the Load pressure control line 14, an aperture 24 is provided. That in the opening direction of the Three-way regulator D (reducing the pressure in the pump line P) opening a check valve 21 is biased with a spring 22 in the closing direction and that higher than that other check valve 23, which may not be biased at all.
  • a quantity-limiting throttle 25 is located in the intermediate plate 2 in the pump line P. arranged, the passage cross section is expediently adjustable.
  • the throttle 25 is bypassed in the pump line P by a line loop 26 in which a Switching valve 27, e.g. a 2/2-way solenoid valve is included, which by means of a Switching magnet 28 between that shown in Fig.1 and held by a spring Locking position and a passage position a is adjustable, in which the throttle 25 bypassed becomes.
  • the switching valve 27 is in the embodiment shown with a check valve equipped, that in the direction of flow to the proportional directional control valves P2, P3 blocks.
  • the proportional directional control valve P1 is located in the housing 1 e.g. upstream of the intermediate plate 2 and is through the throttle 25 or the switching valve 27 not affected.
  • a pressure limiting device is also provided, the one Bypass line 29 between the line loop 26 and the return line R and an expediently adjustable pressure relief valve 30 arranged therein contains. Furthermore, in the line loop 26 between the pump line P and the Switch valve 27 on the side facing away from the three-way controller D, a check valve 31 arranged, which blocks in the flow direction to the pressure relief valve 30.
  • the proportional directional control valve receives P1 the according to the load pressure in the control line 19 from Three-way controller D assigned volume flow, possibly with the maximum pressure.
  • the speed of movement of the one controlled with the proportional directional control valve P1 Consumer depends on the deflection of the proportional directional control valve P1.
  • the movement speed is maintained independently of the load by the inflow controller Z.
  • the proportional directional control valves P2 and P3, on the other hand, have a reduced volume Volume flow through the throttle 25, the reduced amount after the Setting the throttle 25 is aimed.
  • the proportional directional control valves P2, P3 is however the maximum pressure can also be used, since the pressure relief valve 30 through the check valve 31 is prevented from responding.
  • the speed of movement the consumer, which is controlled by means of the proportional directional control valve P2, P3, is no longer just from the deflection of the respective proportional directional control valve P2 or P3 depending, but is limited by the throttle 25. With consumers can therefore also handle large loads (the maximum pressure can be used) via the Load torque limit to be taken into account at maximum speed, however be moved slowly without endangering the safety of the system or the hoist.
  • the throttle 25 is bypassed and also stands for the proportional directional control valves P2 and P3 the maximum Volume flow available.
  • the pressure relief valve 30 limits the usable pressure, so that, for example, a greater load than that for the maximum Movement speed of the consumer V would be permissible, not to be lifted at all can.
  • intermediate plates 2 each with one To provide throttle 25 and a switching valve 27.
  • These intermediate plates 2 can be distributed between the housings 1 in order to be individually tailored to individual consumers an even larger battery arrangement than that shown.
  • these Intermediate plates 2 could be differently set chokes 25 or different set pressure relief valves 30 may be provided.
  • the pressure relief valve 30 and the check valve 31 and also the throttle 25 to integrate directly into the switching valve 27 and this more complex switching valve directly to put in the pump line P.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Automation & Control Theory (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Control And Safety Of Cranes (AREA)

Abstract

Upstream of each proportional path control valve in a connecting conduit (7) to the pump conduit (P) is arranged a feed regulator (Z), which is controllable from the load pressure of the corresponding user and the feed pressure of the proportional path control valve. A three-way regulator (D) common to all users (V) is fitted between the pump conduit and the return flow conduit (R) and is controllable by the pump pressure and the highest load pressure. In the pump conduit between the three-way regulator and at least one proportional path control valve (P1,P2,P3) of the group of users, a quantity limiting throttle (25) is selectively by-passable by a pressure limiting device (29,30,31).

Description

Die Erfindung betrifft eine hydraulische Steuervorrichtung gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control device according to the preamble of Claim 1.

Gemäß DE-C-42 43 973 ist beim Zulaufregler eines Proportional-Wegesteuerventils eine lastdruckabhängig eingreifende Mengenreduziervorrichtung vorgesehen, um die Zulaufregler-Menge bzw. die Bewegungsgeschwindigkeit des Verbrauchers zu reduzieren. Lastabhängig werden die Stoßfaktoren in einem mit der Steuervorrichtung ausgestatteten Hebezeug reduziert, um die Überlastgrenze dieses Hebezeugs zumindest zeitweise auszudehnen. Damit kann beim Eingreifen der Mengenreduziervorrichtung eine größere Last als die bei maximaler Geschwindigkeit zulässige Last innerhalb des normalen Bewegungsbereiches nur langsam oder eine kleine Last langsam, jedoch weiter nach außen bewegt werden als mit maximal möglicher Geschwindigkeit. Innerhalb der bezüglich der maximalen Geschwindigkeit festgelegten Überlastgrenze werden ohne Ansprechen der Mengenreduziervorrichtung die zulässigen Lasten mit maximaler Geschwindigkeit bewegt. Insgesamt läßt sich das Hebezeug so besser ausnutzen. Jedoch ist der bauliche Aufwand groß.According to DE-C-42 43 973 there is one in the inlet regulator of a proportional directional control valve Intervening quantity reducing device depending on the load pressure is provided in order to control the quantity of the inflow regulator or to reduce the speed of movement of the consumer. The impact factors in a vehicle equipped with the control device are dependent on the load Hoist reduced to the overload limit of this hoist at least temporarily expand. This means that a larger one can intervene when the quantity reduction device is engaged Load as the load allowed at maximum speed within the normal range of motion only slowly or a small load slowly, but further out be moved than at the maximum possible speed. Within the regarding the maximum speed set overload limit without response the quantity reducing device the permissible loads at maximum speed emotional. Overall, the hoist can be used better. However, the structural Big effort.

Bei einer aus WO90/02882 bekannten Steuervorrichtung sind zusätzlich auf den Zulaufregler jedes Proportional-Wegesteuerventils einwirkende Ventilkomponenten vorgesehen, die das normale Regelspiel des Zulaufreglers bei bestimmten Betriebszuständen verändern. Damit wird entweder vermieden, daß bei einem exzessiven Mengenbedarf eines Wegesteuerventils der die größte Last bewegende Verbraucher unkontrolliert anhält, oder erreicht daß die Geschwindigkeit eines Verbrauchers zugunsten der Geschwindigkeit eines anderen, zu diesem Zeitpunkt Priorität benötigenden Verbrauchers beeinflußt wird. Die Einflußnahme dieser zusätzlichen Komponenten erfolgt selbsttätig in Abhängigkeit von Veränderungen der Druckdifferenz zwischen dem Zuführdruck und dem höchsten Lastdruck.In the case of a control device known from WO90 / 02882, the inflow regulator is additionally attached valve components acting on each proportional directional control valve, which is the normal control cycle of the inlet controller in certain operating conditions change. This either avoids an excessive quantity requirement a directional control valve that stops the largest load moving consumer in an uncontrolled manner, or achieves the speed of a consumer in favor of speed of another consumer who needs priority at this point in time being affected. These additional components are automatically influenced in Dependence on changes in the pressure difference between the supply pressure and the highest load pressure.

Weiterer Stand der Technik ist enthalten in einem Artikel der Fachzeitschrift "Hydraulics und Pneumatics, USA, 39 (1986), Oktober, Nr. 10, S. 47 bis 57. Further state of the art is contained in an article of the journal "Hydraulics and Pneumatics, USA, 39 (1986), October, No. 10, pp. 47 to 57.

Der Erfindung liegt die Aufgabe zugrunde, eine hydraulische Steuervorrichtung der eingangs genannten Art zu schaffen, die auf baulich einfache Weise eine zeitweise Lastmomentvergrößerung bei einem Hebezeug und für das Hebezeug einen erweiterten Einsatzbereich ermöglicht.The invention has for its object a hydraulic control device of the beginning to create the kind that is structurally simple at times Increased load torque for a hoist and an extended one for the hoist Area of application.

Die gestellte Aufgabe wird erfindungsgemäß mit den Merkmalen des Patentanspruchs 1 gelöst.The object is achieved according to the invention with the features of patent claim 1 solved.

Wird die Drossel in der Pumpenleitung nicht umgangen, dann ist die Geschwindigkeit bei allen Verbrauchern gleichförmig verringert, deren Proportional-Wegesteuerventile sich stromab der Drossel befinden. Stromauf der Drossel angeschlossene Verbraucher sind mit der maximalen Geschwindigkeit und dem maximalen Druck steuerbar. Wird mit der Drossel die Geschwindigkeit beispielsweise auf ein Viertel der maximalen Geschwindigkeit reduziert, dann kann eine um ca. 10% höhere Last langsamer bewegt werden bzw. kann eine kleinere Last weiter nach außen bewegt werden als mit maximaler Geschwindigkeit. Dadurch ergeben sich für das Hebezeug eine Lastmomentvergrößerung und ein erweiterter Einsatzbereich. Wichtig ist, daß bei verringerter Geschwindigkeit und Einflußnahme der Drossel dennoch der maximale Druck nutzbar ist, d.h., daß mit einem Mobilkran dann größere Lasten (als bei maximaler Geschwindigkeit) gehoben und mit der verringerten Geschwindigkeit auch weit nach außen bewegt werden können. Hingegen ist bei Umgehung der Drossel die maximale Bewegungsgeschwindigkeit der Verbraucher möglich (maximale Menge), wobei allerdings die Druckbegrenzungsvorrichtung den nutzbaren Druck beschränkt, so daß dann nur kleinere Lasten bewegbar sind. Mit anderen Worten wird bei gedrosselter Geschwindigkeit eine hohe Kraft und bei hoher Geschwindigkeit eine verringerte Kraft zur Verfügung stellt, bzw. steht die maximale Kraft nur bei gedrosseltem Volumenstrom zur Verfügung, und zwar weitgehend unabhängig davon, wie weit das jeweilige lastunabhängig arbeitende Proportional-Wegesteuerventil verstellt wird.If the throttle in the pump line is not bypassed, the speed is at uniformly reduced to all consumers whose proportional directional control valves downstream of the throttle. Are consumers connected upstream of the choke controllable at maximum speed and pressure. Will with the Throttle the speed to a quarter of the maximum speed, for example reduced, then a load that is about 10% higher can be moved more slowly or a smaller load can be moved further out than at maximum speed. This results in an increase in the load torque for the hoist and a extended area of application. It is important that with reduced speed and influence the throttle the maximum pressure can still be used, i.e. that with a mobile crane then larger loads (than at maximum speed) lifted and with the reduced Speed can also be moved far out. However, is bypassing the throttle, the maximum movement speed of the consumer possible (maximum amount), but the pressure limiting device usable pressure is limited, so that only smaller loads can be moved. With others Words become high power at reduced speed and high speed provides a reduced force, or is the maximum force only available if the volume flow is restricted, and largely independently how far the respective proportional directional control valve, which works independently of the load is adjusted.

Gemäß Anspruch 2 läßt sich die bei Eingriffnahme der Drossel gegebene Mengenbegrenzung exakt an den jeweiligen Anwendungsfall anpassen.According to claim 2, the amount limitation given when the throttle is engaged adapt exactly to the respective application.

Das Schaltventil bringt gemäß Anspruch 3 in seiner Sperrstellung die mengenbegrenzende Drossel zur Wirkung. Das Rückschlagventil stellt sicher, daß bei Eingriffnahme der Drossel das Druckbegrenzungsventil isoliert und der maximale, zur Verfügung gestellte Druck nutzbar ist. Ist das Schaltventil in die Durchgangstellung geschaltet, dann wird die Drossel umgangen und das Druckmittel nimmt den Weg über die Leitungsschleife, wobei die maximale und vom Dreiwege-Regler eingesteuerte Menge die maximale Geschwindigkeit der Verbraucher ermöglicht. Jedem Verbraucher wird dabei über seinen Zulaufregler lastunabhängig die gerade notwendige Menge zugeteilt, die sich nach der Verstellung des Proportional-Wegesteuerventils richtet. Der Zulaufregler hält die Druckdifferenz über das Proportional-Wegesteuerventil lastunabhängig konstant. Das Druckbegrenzungsventil begrenzt allerdings den dann nutzbaren Druck. und somit die Größe der hebbaren Lasten.The switching valve brings the quantity-limiting in its blocking position Throttle to the effect. The check valve ensures that when engaged the throttle isolates the pressure relief valve and the maximum provided Pressure is usable. If the switching valve is switched to the through position, then the throttle is bypassed and the pressure medium takes the path via the line loop, where the maximum quantity controlled by the three-way controller is the maximum Allows consumer speed. Every consumer will find out about his Inlet controller allocated the required amount regardless of the load, which depends on the Adjustment of the proportional directional control valve. The inlet regulator maintains the pressure difference Constant regardless of load via the proportional directional control valve. The pressure relief valve however limits the pressure that can then be used. and therefore the size the liftable loads.

Herstellungs- und montagetechnisch ist gemäß Anspruch 4 die Zwischenplatte stromab des oder der Gehäuse in der Batterieanordnung eingebaut, dessen oder deren Verbraucher weder in der Bewegungsgeschwindigkeit noch im Druck begrenzt zu werden brauchen.Manufacturing and assembly technology is the intermediate plate downstream according to claim 4 of the housing or housings installed in the battery arrangement, its or its consumers there is no need to limit movement speed or pressure.

Gemäß Anspruch 5 werden Druckschwingungen im System, auf die der Dreiwegeregler ansprechen könnte, rasch und wirksam abgedämpft. Die beiden Rückschlagventile kooperieren mit der Dämpfdrossel auf optimale Weise. Die Dämpfdrossel läßt sich dank der beiden Rückschlagventile relativ stramm einstellen, weil diese auch bei kaltem Druckmittel das Regelspiel des Dreiwegereglers ermöglichen. Das im Schließsinn höher vorgespannte Rückschlagventil öffnet zweckmäßigerweise in der Richtung, in der der Dreiwegeregler bei seinem Regelspiel den Druck in der Pumpenleitung verringert, wobei die Vorspannung dieses Rückschlagventils einen wichtigen Beitrag zur Dämpfung von Druckschwankungen leistet.According to claim 5 pressure fluctuations in the system to which the three-way controller could respond quickly and effectively dampened. The two check valves cooperate with the damping throttle in an optimal way. The damping throttle can be thanks of the two non-return valves should be set relatively tight because they are cold Pressure medium allow the control play of the three-way controller. The higher in the closing sense biased check valve expediently opens in the direction in which the Three-way controller during its control cycle reduces the pressure in the pump line, whereby the bias of this check valve makes an important contribution to damping Pressure fluctuations.

Gemäß Anspruch 6 ist bei dem Dämpfungssystem eine zusätzliche Blende in der Lastdruck-Steuerleitung vorgesehen.According to claim 6 is an additional aperture in the damping system Load pressure control line provided.

Das Schaltventil, mit dem wahlweise die Drossel in der Pumpenleitung umgehbar ist, wird zweckmäßigerweise magnetisch betätigt, und zwar steuerseitig während des Betriebs der Steuervorrichtung. Es ist aber auch möglich, das Schaltventil lastdruckabhängig zu verstellen.The switching valve, with which the throttle in the pump line can be bypassed, is expediently actuated magnetically, on the control side during operation the control device. However, it is also possible for the switching valve to be dependent on the load pressure to adjust.

Anhand der Zeichnung wird eine Ausführungsform des Erfindungsgegenstandes erläutert. Fig. 1 zeigt in einem Blockschaltbild eine hydraulische Steuervorrichtung S für ein Hebezeug wie einen Mobilkran, mit dem beispielsweise auch in besonderen Anwendungssituationen ein Hubkorb manipuliert wird.An embodiment of the subject matter of the invention is explained with the aid of the drawing. Fig. 1 shows a block diagram of a hydraulic control device S for Hoist like a mobile crane, with which, for example, even in special application situations a lifting cage is manipulated.

Die Steuervorrichtung S weist einzelne, blockförmige Gehäuse 1, 3 und wenigstens eine Zwischenplatte 2 auf, die in einer Batterieanordnung 4 (Steuerblock) zusammengefaßt sind. In den Gehäusen 1 sind Proportional-Wegesteuerventile P1, P2, P3 mit ihren Zulaufreglern Z und weiteren Komponenten untergebracht. Die Gehäuse 1, 3 und die Zwischenplatten 2 sind an ihren Anschlußseiten miteinander verschraubt, so daß alle Verbraucher V, z.B. Hydraulikmotoren oder Hydraulikzylinder, an eine gemeinsame Pumpenleitung P angeschlossen sind. Ferner verläuft in der Batterieanordnung 4 eine gemeinsame Rücklaufleitung R zu einem Tank 6. Die Druckversorgung erfolgt beispielsweise über eine Pumpe 5, z.B. eine Konstantpumpe. Jedes Proportional-Wegesteuerventil P1, P2, P3 ist über eine den Zulaufregler Z enthaltende Anschlußleitung 7 an die Pumpenleitung P angeschlossen. Von der Rücklaufleitung R führen Rücklauf-Anschlußleitungen 8 zu den Proportional-Wegesteuerventilen P1, P2, P3. Jeder Verbraucher V ist über zwei (oder nur eine) Arbeitsleitungen A, B an das zugehörige Proportional-Wegesteuerventil P1, P2, P3 angeschlossen und dient zum Bewegen, z.B. Heben, einer Last L.The control device S has individual, block-shaped housings 1, 3 and at least one Intermediate plate 2, which is combined in a battery assembly 4 (control block) are. In the housings 1 are proportional directional control valves P1, P2, P3 with their inlet regulators Z and other components. The housings 1, 3 and the intermediate plates 2 are screwed together on their connection sides, so that all consumers V, e.g. Hydraulic motors or hydraulic cylinders, to a common pump line P are connected. Furthermore, a common one runs in the battery arrangement 4 Return line R to a tank 6. The pressure supply takes place, for example via a pump 5, e.g. a constant pump. Each proportional directional control valve P1, P2, P3 is connected to the pump line via a connection line 7 containing the inlet regulator Z. P connected. Return connecting lines 8 lead from the return line R. to the proportional directional control valves P1, P2, P3. Each consumer V is over two (or only one) working lines A, B to the associated proportional directional control valve P1, P2, P3 connected and used for moving, e.g. Lifting a load L.

Der Zulaufregler Z ist ein Zweiwegeregler, der nach Art einer Druckwaage in Schließrichtung über eine Steuerleitung 9 mit dem am Proportional-Wegesteuerventil P1 anstehenden Druck und in Öffnungsrichtung über eine Steuerleitung 10 mit dem aus einer der Arbeitsleitungen A, B abgeleiteten Lastdruck und von einer Regelfeder 11 beaufschlagt wird. Die Steuerleitung 10 ist über einen Steuerleitungszweig 12 und ein Wechselventil 13 an eine gemeinsame Lastdruck-Steuerleitung 14 angeschlossen, die durch die Gehäuse 1 und die Zwischenplatte 2 bis in das Gehäuse 3 verläuft. Aufgrund der Wechselventile 13 führt die Lastdruck-Steuerleitung 14 den momentan höchsten Lastdruck.The inlet regulator Z is a two-way regulator, which works like a pressure compensator in the closing direction via a control line 9 with the pending at the proportional directional control valve P1 Pressure and in the opening direction via a control line 10 with that from one of the working lines A, B derived load pressure and acted upon by a control spring 11 becomes. The control line 10 is via a control line branch 12 and a shuttle valve 13 connected to a common load pressure control line 14 through the housing 1 and the intermediate plate 2 extends into the housing 3. Because of the shuttle valves 13, the load pressure control line 14 carries the currently highest load pressure.

Im Gehäuse 3 ist ein Dreiwegeregler D üblicher Bauart angeordnet, der einen als Druckwaage arbeitenden Regelkolben 15 besitzt, der blendenartig den Durchgang eines Verbindungskanals 16 zwischen der Pumpenleitung P und der Rücklaufleitung R überwacht und in Abhängigkeit von seiner momentanen Stellung mehr oder weniger oder gar kein Druckmittel aus der Pumpenleitung P in die Rücklaufleitung R abläßt. Der Regelkolben 15 wird in Öffnungsrichtung des Dreiwegereglers (zur Verringerung des Drucks in der Pumpenleitung P) über eine Steuerleitung 17 mit dem Druck in der Pumpenleitung beaufschlagt (Öffnungsseite des Dreiwegereglers). An der Schließseite und in Schließrichtung des Dreiwegereglers wird hingegen der Regelkolben 15 von einer Regelfeder 18 und mit dem Druck in einer Steuerleitung 19 beaufschlagt, die über ein Dämpfungssystem C an die Lastdruck-Steuerleitung 14 angeschlossen ist.In the housing 3, a three-way controller D of conventional design is arranged, one as a pressure compensator Working control piston 15 has the aperture of the passage of a connecting channel 16 monitored between the pump line P and the return line R. and depending on its current position, more or less or none at all Drain the pressure medium from the pump line P into the return line R. The control piston 15 is in the opening direction of the three-way controller (to reduce the pressure in the Pump line P) is acted upon by the pressure in the pump line via a control line 17 (Opening side of the three-way controller). On the closing side and in the closing direction of the three-way controller, on the other hand, the control piston 15 is controlled by a control spring 18 and pressurized in a control line 19 via a damping system C is connected to the load pressure control line 14.

Im Dämpfungssystem C ist eine Dämpfdrossel 20 enthalten, die mittels zweier gegensinniger Rückschlagventile 21 und 23 in jeweils einer Strömungsrichtung umgehbar ist. Zwischen der Dämpfdrossel 20 und dem nächstliegenden Wechselventil 13 in der Lastdruck-Steuerleitung 14 ist eine Blende 24 vorgesehen. Das in Öffnungsrichtung des Dreiwegereglers D (Verringern des Drucks in der Pumpenleitung P) öffnende eine Rückschlagventil 21 ist mit einer Feder 22 im Schließsinn vorgespannt und zwar höher als das andere Rückschlagventil 23, das gegebenenfalls überhaupt nicht vorgespannt ist.In the damping system C, a damping throttle 20 is contained, which by means of two opposing Check valves 21 and 23 can be bypassed in each flow direction. Between the damping throttle 20 and the nearest shuttle valve 13 in the Load pressure control line 14, an aperture 24 is provided. That in the opening direction of the Three-way regulator D (reducing the pressure in the pump line P) opening a check valve 21 is biased with a spring 22 in the closing direction and that higher than that other check valve 23, which may not be biased at all.

In der Zwischenplatte 2 ist in der Pumpenleitung P eine mengenbegrenzende Drossel 25 angeordnet, deren Durchgangsquerschnitt zweckmäßigerweise verstellbar ist. Die Drossel 25 wird in der Pumpenleitung P durch eine Leitungsschleife 26 umgangen, in der ein Schaltventil 27, z.B. ein 2/2-Wege-Magnetschaltventil, enthalten ist, das mittels eines Schaltmagneten 28 zwischen der in Fig.1 gezeigten und durch eine Feder gehaltenen Sperrstellung und einer Durchgangsstellung a verstellbar ist, in der die Drossel 25 umgangen wird. Das Schaltventil 27 ist bei der gezeigten Ausführungsform mit einem Rückschlagventil ausgestattet, das in Strömungsrichtung zu den Proportional-Wegesteuerventilen P2, P3 sperrt. Das Proportional-Wegesteuerventil P1 im Gehäuse 1 befindet sich z.B. stromauf der Zwischenplatte 2 und wird durch die Drossel 25 bzw. das Schaltventil 27 nicht beeinflußt.A quantity-limiting throttle 25 is located in the intermediate plate 2 in the pump line P. arranged, the passage cross section is expediently adjustable. The throttle 25 is bypassed in the pump line P by a line loop 26 in which a Switching valve 27, e.g. a 2/2-way solenoid valve is included, which by means of a Switching magnet 28 between that shown in Fig.1 and held by a spring Locking position and a passage position a is adjustable, in which the throttle 25 bypassed becomes. The switching valve 27 is in the embodiment shown with a check valve equipped, that in the direction of flow to the proportional directional control valves P2, P3 blocks. The proportional directional control valve P1 is located in the housing 1 e.g. upstream of the intermediate plate 2 and is through the throttle 25 or the switching valve 27 not affected.

In der Zwischenplatte 2 ist ferner eine Druckbegrenzungsvorrichtung vorgesehen, die eine Beipaßleitung 29 zwischen der Leitungsschleife 26 und der Rücklaufleitung R sowie ein darin angeordnetes, zweckmäßigerweise einstellbares, Druckbegrenzungsventil 30 enthält. Ferner ist in der Leitungsschleife 26 zwischen der Pumpenleitung P und dem Schaltventil 27 auf dessen dem Dreiwegeregler D abgewandter Seite ein Rückschlagventil 31 angeordnet, das in Strömungsrichtung zum Druckbegrenzungsventil 30 sperrt.In the intermediate plate 2, a pressure limiting device is also provided, the one Bypass line 29 between the line loop 26 and the return line R and an expediently adjustable pressure relief valve 30 arranged therein contains. Furthermore, in the line loop 26 between the pump line P and the Switch valve 27 on the side facing away from the three-way controller D, a check valve 31 arranged, which blocks in the flow direction to the pressure relief valve 30.

In der gezeigten Stellung des Schaltventils 27 gemäß Fig. 1 erhält das Proportional-Wegesteuerventil P1 den nach Maßgabe des Lastdrucks in der Steuerleitung 19 vom Dreiwegeregler D zugeteilten Volumenstrom, gegebenenfalls mit dem maximalen Druck. Die Bewegungsgeschwindigkeit des mit dem Proportional-Wegesteuerventils P1 gesteuerten Verbrauchers richtet sich nach der Auslenkung des Proportional-Wegesteuerventils P1. Die Bewegungsgeschwindigkeit wird lastunabhängig durch den Zulaufregler Z aufrechterhalten.In the position of the switching valve 27 shown in FIG. 1, the proportional directional control valve receives P1 the according to the load pressure in the control line 19 from Three-way controller D assigned volume flow, possibly with the maximum pressure. The speed of movement of the one controlled with the proportional directional control valve P1 Consumer depends on the deflection of the proportional directional control valve P1. The movement speed is maintained independently of the load by the inflow controller Z.

Die Proportional-Wegesteuerventile P2 und P3 erhalten hingegen einen mengenreduzierten Volumenstrom über die Drossel 25, wobei sich die reduzierte Menge nach der Einstellung der Drossel 25 richtet. Für die Proportional-Wegesteuerventile P2, P3 ist jedoch ebenfalls der maximale Druck nutzbar, da das Druckbegrenzungsventil 30 durch das Rückschlagventil 31 am Ansprechen gehindert ist. Die Bewegungsgeschwindigkeit der Verbraucher, die mittels der Proportional-Wegesteuerventils P2, P3 gesteuert wird, ist nicht mehr nur von der Auslenkung des jeweiligen Proportional-Wegesteuerventils P2 oder P3 abhängig, sondern wird nach oben durch die Drossel 25 begrenzt. Mit den Verbrauchern können somit auch große Lasten (der maximale Druck ist nutzbar) über die bei maximaler Geschwindigkeit zu berücksichtigende Lastmomentgrenze hinaus, jedoch langsam bewegt werden, ohne die Sicherheit des Systems bzw. des Hebezeugs zu gefährden.The proportional directional control valves P2 and P3, on the other hand, have a reduced volume Volume flow through the throttle 25, the reduced amount after the Setting the throttle 25 is aimed. For the proportional directional control valves P2, P3 is however the maximum pressure can also be used, since the pressure relief valve 30 through the check valve 31 is prevented from responding. The speed of movement the consumer, which is controlled by means of the proportional directional control valve P2, P3, is no longer just from the deflection of the respective proportional directional control valve P2 or P3 depending, but is limited by the throttle 25. With consumers can therefore also handle large loads (the maximum pressure can be used) via the Load torque limit to be taken into account at maximum speed, however be moved slowly without endangering the safety of the system or the hoist.

Wird das Schaltventil 27 umgestellt in seine Schaltstellung a, dann ist die Drossel 25 umgangen und steht auch für die Proportional-Wegesteuerventile P2 und P3 der maximale Volumensstrom zur Verfügung. Allerdings begrenzt das Druckbegrenzungsventil 30 den nutzbaren Druck, so daß beispielsweise eine größere Last, als sie für die maximale Bewegungsgeschwindigkeit des Verbrauchers V zulässig wäre, gar nicht gehoben werden kann.If the switching valve 27 is switched to its switching position a, the throttle 25 is bypassed and also stands for the proportional directional control valves P2 and P3 the maximum Volume flow available. However, the pressure relief valve 30 limits the usable pressure, so that, for example, a greater load than that for the maximum Movement speed of the consumer V would be permissible, not to be lifted at all can.

Für besondere Anforderungen ist es denkbar, mehrere Zwischenplatten 2 jeweils mit einer Drossel 25 und einem Schaltventil 27 vorzusehen. Diese Zwischenplatten 2 können zwischen den Gehäusen 1 verteilt sein, um individuell auf einzelne der Verbraucher in einer sogar größeren Batterieanordnung als der gezeigten einwirken zu können. In diesen Zwischenplatten 2 könnten unterschiedlich eingestellte Drosseln 25 bzw. unterschiedlich eingestellte Druckbegrenzungsventile 30 vorgesehen sein. Ferner ist es denkbar, das Druckbegrenzungsventil 30 und das Rückschlagventil 31 und auch die Drossel 25 direkt in das Schaltventil 27 zu integrieren und dieses komplexere Schaltventil direkt in die Pumpenleitung P zu setzen.For special requirements, it is conceivable to use several intermediate plates 2 each with one To provide throttle 25 and a switching valve 27. These intermediate plates 2 can be distributed between the housings 1 in order to be individually tailored to individual consumers an even larger battery arrangement than that shown. In these Intermediate plates 2 could be differently set chokes 25 or different set pressure relief valves 30 may be provided. It is also conceivable the pressure relief valve 30 and the check valve 31 and also the throttle 25 to integrate directly into the switching valve 27 and this more complex switching valve directly to put in the pump line P.

Claims (6)

  1. Hydraulic control device (S), in particular for a lifting appliance, fitted as a mobile crane, for a group of consumers (V) which are connected in parallel, each via a proportional directional control valve (P1, P2, P3), to a pump line (P) and a return line (R), with an inflow controller (Z) which is arranged upstream of each proportional directional control valve and which is capable of being loaded with the load pressure of the associated consumer and the inflow pressure of the proportional directional control valve, and with a three-way controller (D), common to all the consumers (V), which is located between the pump line (P) and the return line (R) and which is capable of being loaded with the pump pressure and the highest available load pressure, characterized in that a quantity-limiting throttle (25), which is selectively bypassable by way of a line loop (26), is arranged in the pump line (P) between the three-way controller (D) and at least one proportional directional control valve (P1, P2, P3), a pressure-limiting device (29, 30) being provided between the line loop (26) and the return line (R).
  2. Hydraulic control device according to Claim 1, characterized in that the throttle (25) is designed adjustably.
  3. Hydraulic control device according to Claim 1, characterized in that in the pump line (P) the line loop (26) bypassing the throttle (25) comprises a switching valve (27), preferably a 2/2-way solenoid switching valve, in that the pressure-limiting device has a drainage line (29) which on the side of the switching valve (27) facing away from the three-way controller (D) connects the line loop (26) to the return line (R) and contains a pressure-limiting valve (30), preferably an adjustable pressure-limiting valve, and in that a non-return valve (31), shutting off in the direction of the pressure-limiting valve (30), is arranged in the line loop (26) between the drainage line (29) and the pump line (P).
  4. Hydraulic control device according to at least one of Claims 1 to 3, characterized in that each proportional directional control valve (P1, P2, P3), together with its inflow controller (Z), is contained in a block-shaped housing (1), in that the housings (1) are placed with their connection sides one against the other in a battery-like manner, in that the throttle (25), together with the switching valve (27), the pressure-limiting valve (30) and the non-return valve (31), is contained in an intermediate plate (2), and in that the intermediate plate (2) is capable of being attached selectively to the connection side of each housing (1).
  5. Hydraulic control device according to Claim 1, characterized in that the three-way controller (D) has a pressure balance diaphragm piston (15) which is capable of being subjected, on the opening side and in the opening direction of the three-way controller (D), to the pump pressure and, on the closing side and in the closing direction, to the highest load pressure and to a regulating spring (18), and in that a damping system (C) for pressure oscillations is arranged in a load-pressure control line (14) on the closing side and consists of a damping throttle (20) and of two non-return valves (21, 23) which bypass the damping throttle (20) in opposite directions and of which one non-return valve (21), preferably the non-return valve opening in the opening direction of the three-way controller (D), is prestressed in a closing direction to a greater extent than the other non-return valve (23).
  6. Hydraulic control device according to Claim 5, characterized in that a diaphragm (24) is provided in the load-pressure control line (14) on that side of the damping system (C) which faces away from the three-way controller (D).
EP97110053A 1996-07-02 1997-06-19 Hydraulic control system Expired - Lifetime EP0816689B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE29611525U 1996-07-02
DE29611525U DE29611525U1 (en) 1996-07-02 1996-07-02 Hydraulic control device

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EP0816689A1 EP0816689A1 (en) 1998-01-07
EP0816689B1 true EP0816689B1 (en) 2000-12-06

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EP (1) EP0816689B1 (en)
AT (1) ATE197984T1 (en)
DE (2) DE29611525U1 (en)
DK (1) DK0816689T3 (en)
ES (1) ES2153623T3 (en)

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CN111677713B (en) * 2020-05-19 2022-05-10 徐州徐工随车起重机有限公司 Confluence proportion multi-way reversing valve for straight-arm lorry-mounted crane and working method

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SE8803181D0 (en) 1988-09-09 1988-09-09 Atlas Copco Ab HYDRAULIC DRIVING SYSTEM WITH A PRIORITY FUNCTION FOR HYDRAULIC MOTORS
DE4243973C1 (en) 1992-12-23 1994-07-07 Heilmeier & Weinlein Hydraulic control device

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ATE197984T1 (en) 2000-12-15
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DE29611525U1 (en) 1996-09-05
ES2153623T3 (en) 2001-03-01
EP0816689A1 (en) 1998-01-07

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