EP1635072B1 - Electro-hydraulic control device - Google Patents

Electro-hydraulic control device Download PDF

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Publication number
EP1635072B1
EP1635072B1 EP20050012251 EP05012251A EP1635072B1 EP 1635072 B1 EP1635072 B1 EP 1635072B1 EP 20050012251 EP20050012251 EP 20050012251 EP 05012251 A EP05012251 A EP 05012251A EP 1635072 B1 EP1635072 B1 EP 1635072B1
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EP
European Patent Office
Prior art keywords
line
consumer
pressure
load
tank
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 - Fee Related
Application number
EP20050012251
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German (de)
French (fr)
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EP1635072A1 (en
Inventor
Martin Dipl.-Ing. Heusser
Martin Ascherl
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.)
Hawe Hydraulik GmbH and Co KG
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Hawe Hydraulik GmbH and Co KG
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Publication of EP1635072A1 publication Critical patent/EP1635072A1/en
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Publication of EP1635072B1 publication Critical patent/EP1635072B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14—Energy-recuperation means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves

Definitions

  • the invention relates to an electro-hydraulic control device specified in the preamble of claim 1 Art.
  • each hydro consumer is assigned its own two-way pressure compensator, so that a correct supply of a hydraulic consumer, on whose function it may be necessary, can be ensured.
  • the input section which controls a priority consumer simultaneously, a three-way bias pressure compensator.
  • the circulation two-way pressure compensator is integrated in a three-way flow regulator downstream of the three-way pressure compensator.
  • the three-way bias pressure compensator is structurally complex and expensive. This is disadvantageous in that such input sections are used for many applications, for example on forklifts, and combined with various types of consumer controls and are therefore used in considerable numbers.
  • Known control device are either for the functions lifting and lowering two separate 2/2-proportional pressure control valves provided, wherein the non-pressurized circulation is controlled via a supply line leading to further Hydrovieem, or is provided for each hydraulic consumer, a hydraulic rectifier circuit with four check valves and a single, responsible for the functions lifting and lowering 2/2-way proportional pressure control valve.
  • the load compensation system operates with electrical pressure transducers connected to a superordinate electronic control device, from which the 2/2-way proportional control valve is driven according to the load compensation.
  • a reversible pump is provided which drives a generator as it sinks to generate power. The reversed pump opens the downstream check valve of the rectifier circuit.
  • a hydraulic rectifier circuit with only a 2/2-way proportional control valve for the functions lifting and lowering.
  • a controllable for lowering proportional pressure control valve is arranged, the function builds back pressure, which causes problems with load-freefursenkendem hydraulic consumers.
  • known control device for a plurality of hydraulic consumers includes a single two-way pressure compensator, which alternately controls the non-pressurized circulation or divides the pump delivery flow among the Hydrosedem.
  • the DE 103 08 289 A with older seniority shows in an input section of a control device, a single two-way pressure compensator, which alternately controls either the non-pressurized circulation of the pump delivery flow or adjusts the supply pressure in all parallel-connected, equal hydronic consumption common supply line.
  • the invention has for its object to provide an electro-hydraulic control device of the type mentioned above, which is characterized by a structurally simple, inexpensive and universally combinable input section.
  • the pressure compensators in the input section Due to the parallel or series connection of the pressure compensators in the input section are achieved with only two two-way pressure compensators both the flow distribution function and the function of the non-pressurized circulation for a variety optionally attachable to the input section consumer control devices without consuming three-way pressure compensator. Further, the bias two-way pressure compensator in the input section allows the priority supply of a priority hydraulic consumer without a three-way pressure compensator.
  • the Priority feature may be important for electric lift trucks where too high a hydraulic load is required Load can overwhelm the battery capacity and yet ensure the correct supply to the priority consumer.
  • the input section is a block module designed with a multiplicity of connections, which can be individually equipped with valve components for different applications and the connection of different types of consumers Control devices.
  • the input section is a building block that can be used to construct various types of control devices and is cost-effective, which provides the basic functions of pressureless circulation and delivery flow distribution and also offers the structural requirements of a hydraulic load compensation system.
  • the module block can be composed either in one piece or from several components.
  • a plurality of similar connection patterns are also provided for further control device sections designed as modules.
  • the block module expediently has at least two identical connection patterns of the supply, load pressure and tank line connections, so that further module blocks with corresponding connection patterns can optionally be attached. Also, at least one priority consumer actually gets the priority through the corresponding positioning on the priority page of the entry section.
  • At least one priority consumer and at least one subordinate consumer are provided, separate or pressure-load lines linked via a shuttle valve arrangement may be provided in the inlet section, the pretension two-way pressure compensator at the closing adjustment side being connected to the load pressure line of the priority consumer and the circulation two-way Pressure compensator on the Sch resonateverstellseite either only with the load pressure line at least one subordinate consumer, or optionally with the load pressure from the load pressure lines at least one subordinate consumer or the priority consumer can be acted upon.
  • the priority consumer needs priority, it is powered by the bias two-way pressure compensator the required flow rate allocated, possibly at the expense of subordinate consumers.
  • the input section can also be used for a regeneratively operable control device whose pump is reversible and then drives the hydraulic motor acting as a generator electric motor.
  • a structural difference that is provided from the outset or modifiable in the input section then consists in that at least one tank line connection of the input section via the reversible pump, bypassing both pressure compensators with the tank is connected to displaced by lowering pressure medium on the working as a hydraulic motor pump to promote the tank.
  • a connection control line protected by orifices is provided between the load pressure lines in the input section and connected to the tank connection. In this way, the entire hydraulic load compensation system can be relieved of pressure if necessary.
  • a load pressure line preferably the load pressure line to the closing side of the two-way rotary pressure compensator
  • a pressure command can be generated in the load pressure line (desired pressure drop), which causes a function in at least one control section connected to the input section, for example a lowering function.
  • the priority consumer which is connected with its control device to the input section, a double-acting hydraulic consumer.
  • At least one subordinate consumer connected to the input section can act unilaterally against load Be a hydraulic consumer.
  • several subordinate consumers are connected with their control devices in series to the input section.
  • the inlet section with the two two-way pressure compensators is particularly suitable for lift truck applications for setting up individual electrohydraulic control devices adapted to the respective requirements, but can also be used without restriction for other high-pressure hydraulic control devices in other fields of application.
  • An in Fig. 1 schematically shown input section E for an electro-hydraulic control device S (for example, the Fig. 3 or 4 ) is a one-piece or composed of several components block module 1, for example, with a one-piece block housing 2, in which a plurality of hydraulic (or optionally also electro-hydraulic) components are included, expedient interchangeable.
  • the block module 1 has at least two identical connection patterns with supply line connections 3, 3 ', load pressure line connections 4, 4', tank line connections 5, 5 ', preferably on opposite sides of the block module, and on a third side a pump line connection 6 and a tank line connection 7.
  • a feed pump 8 is connected, which is driven by an electric motor, not shown, in a supply line 9 between the terminals 3, 3 ', a bias two-way pressure compensator W1 is arranged.
  • Two load pressure lines 10, 10 'of the terminals 4, 4' are linked together via a shuttle valve assembly 16. Between the terminals 5, 5 'runs a tank line 11 which is connected to the tank T open to the port 7. From the pump connection 6, a pump line 12 extends to the supply line 9. From the pump line 12, a discharge line 20 branches off to the tank connection 7. In the discharge line 20, a two-way circulation pressure compensator W2 is arranged.
  • the bias two-way pressure compensator W1 is acted upon on its opening control side via a pilot control line 13 with the pressure from the pump line 12, while the closing side 15 is acted upon via a control line 14 from the load pressure line 10 (and a control spring).
  • a center port of the shuttle valve assembly 16 branches off a control line 17 to the closing side 19 of the two-way rotary pressure compensator W2, which is acted upon on its opening control side of a control line 18, which branches off from de drainage line 20.
  • the two two-way pressure compensators W1, W2 are connected in parallel with respect to the pump line 12.
  • the two-way circulation pressure compensator W2 is turned on during operation of the pump 8, so that the flow is conveyed directly into the tank T.
  • the two-way bias pressure balance W1 can remain in the shut-off position shown.
  • the two-way circulation pressure compensator W2 also remains in the shut-off position via the control line 17, so that the delivery flow is delivered to the connection 3.
  • the two-way recirculation pressure compensator W2 as inflow regulator regulates the flow rate required for the port 3 or allows the two-way pressure compensator W1 not required at port 3 part of the flow to port 3 'by
  • the two-way bias pressure balance W1 passes the entire delivery flow to the connection 3 ', whereby, according to the control pressure in the control line 17 from the load pressure line 10', the two-way circulation pressure balance W2 as a Type inlet regulator (in the case of a constant displacement pump) can intervene regulating.
  • the pump 8 can also be speed-controlled and at least partially fulfill an inlet control function.
  • Hydro consumers supplied via port 3 thus always have priority over all consumers connected to port 3 '.
  • Input section E shown differs from that of Fig. 1 in that the load pressure lines 10, 10 'are not linked to each other, but the load pressure line 10 lead only to Schellesstellseite 15 of the two-way bias pressure compensator W1, and the load pressure line 10' only to Schellestellseite 19 of the two-way circulation pressure compensator W2.
  • the discharge line 20 branches off downstream of the two-way bias pressure compensator W1 from the supply line 9 to the two-way circulation pressure compensator W2.
  • the two two-way pressure compensators W1, W2 are connected in series with respect to the pump line 12.
  • the function is similar to that Fig. 1 explained function.
  • electro-hydraulic control device S is supplied from a feed pump 8, which is driven for example by an electric motor M.
  • the input section E or the block module 1 is connected here to a control block module 21 for a priority consumer V1 (double-acting hydraulic consumer), which can be actuated via a multi-way proportional slide valve 24 (with two proportional magnets m4 and m5).
  • the control block module 21 is connected to the terminals 3, 4, 5 of the input section E, for example.
  • the entrance section E in Fig. 3 is opposite to that of Fig. 1 or 2 modified by the load pressure lines 10, 10 'branch off control lines 26, 27 which are connected via a shuttle valve assembly 16' of two check valves and a Wegssteuhertechnisch 28 together.
  • From the connecting line 28 branches off a control line 31 to the discharge line 20 ', in which a pressure relief valve 33 is provided for the system pressure in the load compensation system L of the control device for all consumers.
  • a pressure relief valve 33 is provided for the system pressure in the load compensation system L of the control device for all consumers.
  • Between the control lines 26, 27 extends another connecting line 29, in which two orifices 30 are placed, between which a control line 33 to the discharge line 20 'branches off downstream of the two-way circulation pressure compensator W2.
  • a solenoid valve such as a 2/2-way solenoid valve 34 with an actuating magnet m3, provided to demand at the terminal 4' prevailing load pressure for Drain tank T and, for example, to initiate a lowering function for the consumers V2 and / or V3.
  • the two control block modules 22, 23 for the subordinate consumers V2, V3 contain for the lifting and lowering functions only a 2/2-way proportional control valve 25 and 25 ', depending on the energization of its proportional magnet m1 or m2 the speed controls when lifting or lowering, the lifting or lowering function is indeed controlled by the placed in the input section E 2/2-way solenoid valve 34 within the load compensation system L, the working pressure means, however, is drained directly to the tank T when lowering.
  • Each control block module 22, 23 contains a hydraulic rectifier circuit 35 with an open bridge consisting of three branches 36, 37, 38 and four check valves 39, 40, 41, 42. Between the branches 36, 38 a diagonal 43 is provided, in which the 2 / 2-way proportional control valve 25 (or 25 ') is arranged.
  • the branch 37 is connected to the secondary consumer V2.
  • the branch 36 is connected to the supply line 9 via the non-return valve 39 which opens to the hydraulic consumer V2.
  • the branch 38 is via the check valve 42 'opening to the tank line 11' connected to the tank line 11 '.
  • From the branch 38 branches off a load pressure line 44, in which a further check valve 45, which opens to the load pressure line 10 ", and downstream of the same a diaphragm 46 are provided, and which leads to the load pressure line 10".
  • the check valve 42 includes a valve seat 47, with which a closing member 48 cooperates, which is actuated by a control piston 49 (with respect to the valve seat 47 larger impact area).
  • the control piston 49 is acted upon by a spring 50 and is also acted upon by the pressure prevailing in the load pressure line 44 downstream of the orifice 46 to adjust the closed position of the check valve 42.
  • the branch 38 is connected to one side of the valve seat 47 to the check valve 42, the tank line 11 ', however, on the other side.
  • the 2/2-way solenoid valve 34 could also be installed in the control module block 22 (or 23) between the control line 44 and the tank line 11 ', for example, if only one of the control block modules is provided.
  • the check valve 42 could also be designed differently, provided that it can be actuated by means of the pressure from the control line 44 in the illustrated sense.
  • the load compensation system L is depressurized via the control line 32. Both two-way pressure compensators W1, W2 are in the shut-off positions shown.
  • the two-way circulation pressure balance W2 controls the non-pressurized circulation to the tank, whereby the two-way bias pressure compensator W1 switches to passage.
  • the two-way biasing pressure compensator W1 moves in the direction of the shutoff position, so that the priority consumer V1 is supplied with the required delivery flow.
  • the possibly excess part of the delivery flow is discharged via the discharge line 20 'to the tank T.
  • the two-way circulation pressure compensator W2 adjusted toward the passage position, so that the allocated flow in the supply line 9 via the opening check valve 39, the 2/2-way proportional control valve 25 in the diagonal 43 flows to the branch 38, the check valve 41 opens, and the subordinate consumer V2 acted upon. If, for example, in the case of a constant displacement pump 8, there should still be an excess in the flow, then this can be drained via the two-way circulation pressure compensator to the tank. Even if the load pressure at the load pressure port 4 'should become higher than the load pressure in the load pressure line 10, the priority for the priority consumer V1 is maintained. The prevailing in the control line 44 load pressure of the secondary consumer V2 keeps the check valve 42 closed.
  • the switching magnet m3 is supplied with current, so that not only the load pressure line 44 but also the load pressure line 10 'are relieved.
  • the control piston 49 is displaced by the pressure drop against the force of the spring 50, so that the check valve 42 fully opens.
  • the working pressure medium from the subordinate consumer V2 opens the check valve 40 in the branch 36 and flows with the set by the energization of the proportional solenoid M1 speed and flow controlled by the diagonal 43 and the branch 38 in the tank line 11 '.
  • electro-hydraulic control device S is different from that of Fig. 3 through an integrated regenerative function. This means that electrical energy is generated with the working pressure medium displaced when each subordinate consumer V2, V3 is lowered. For this function, the input section E is modified, and also each control module block 22, 23.
  • the pump 8 ' is a reversible pump, which operates in reverse operation as a hydraulic motor and drives a generator operating as an electric motor MG.
  • the tank-line connection 5 ' is connected via a tank-line branch 11 "to a connection 51 in the pump line 12. No connection is provided between the load-pressure line 10' and the outlet line 20 'or is the connection shut off.
  • the 2/2-way solenoid valve 34 of Fig. 3 is missing or disabled.
  • the priority of the priority consumer V1 is given in each case, irrespective of whether the subordinate consumers are actuated or not, and also regardless of whether the sub-consumer load pressure V2, V3 is higher than the load pressure of the priority consumer. Consumer V1 or not.
  • each subordinate consumer V2 and / or V3 is initiated by the reverse operation of the pump 8 'and the corresponding energization of the proportional magnet m1 or m2, the priority consumer V1 is not actuated.
  • the check valve 42 is opened and the working pressure fluid flows through the pump 8' to the tank T, the motor generator MG generating power.
  • the pump 8 ' is optionally switched to idling reverse operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Description

Die Erfindung betrifft eine elektrohydraulische Steuervorrichtung der im Oberbegriff des Anspruchs 1 angegebenen Art.The invention relates to an electro-hydraulic control device specified in the preamble of claim 1 Art.

Bei der aus EP 607 108 A , Fig. 7, bekannten Steuervorrichtung mit zwei Hydroverbrauchem ist für jeden Hydroverbraucher eine Zweiwege-Druckwaage so geschaltet, dass kein Hydroverbraucher Priorität gegenüber dem anderen hat, sondern der jeweilige Hydroverbraucher mit höherem Lastdruck Priorität gegenüber dem anderen gewinnt. Dies kann zu einer zu hohen hydraulischen Last führen, die bei einem elektrischen Hubstapler die Batteriekapazität überfordert, so dass gegebenenfalls ein Hydroverbraucher nicht korrekt versorgt wird, auf dessen Funktion es besonders ankommt.At the EP 607 108 A Fig. 7, known control device with two Hydroverbrauchem for each consumer a two-way pressure compensator is so switched that no hydraulic consumer has priority over the other, but the respective hydraulic consumer with higher load pressure priority over the other wins. This can lead to an excessive hydraulic load, which overstretches the battery capacity in an electric lift truck, so that, where appropriate, a hydraulic consumer is not correctly supplied, on whose function it is particularly important.

Bei der aus EP 462 590 A , Fig. 1, bekannten Steuervorrichtung für zwei Hydroverbraucher ist jeden Hydroverbraucher eine eigene Zweiwege-Druckwaage zugeordnet, so dass eine korrekte Versorgung eines Hydroverbrauchers, auf dessen Funktion es gegebenenfalls ankommt, sichergestellt werden kann.At the EP 462 590 A 1, known control device for two hydraulic consumers each hydro consumer is assigned its own two-way pressure compensator, so that a correct supply of a hydraulic consumer, on whose function it may be necessary, can be ensured.

Bei der aus DE 298 02 498 U1 bekannten Steuervorrichtung ist in der Eingangssektion, die gleichzeitig einen Prioritäts-Verbraucher steuert, eine Dreiwege-Vorspann-Druckwaage vorgesehen. Die Umlauf-Zweiwege-Druckwaage ist in einen Dreiwege-Stromregler integriert, der der Vorspann-Dreiwege-Druckwaage nachgeordnet ist. Die Dreiwege-Vorspann-Druckwaage ist baulich aufwendig und teuer. Dies ist insofern von Nachteil, als solche Eingangssektionen für viele Einsatzfälle, beispielsweise an Hubstaplern, verwendet und mit verschiedenartigen Verbrauchersteuerungen kombiniert und deshalb in beträchtlichen Stückzahlen eingesetzt werden.At the DE 298 02 498 U1 known control device is provided in the input section, which controls a priority consumer simultaneously, a three-way bias pressure compensator. The circulation two-way pressure compensator is integrated in a three-way flow regulator downstream of the three-way pressure compensator. The three-way bias pressure compensator is structurally complex and expensive. This is disadvantageous in that such input sections are used for many applications, for example on forklifts, and combined with various types of consumer controls and are therefore used in considerable numbers.

Bei der aus DE 41 40 408 A1 bekannten Steuervorrichtung sind entweder für die Funktionen Heben und Senken zwei getrennte 2/2-Proportional-Druckregelventile vorgesehen, wobei der drucklose Umlauf über eine zu weiteren Hydroverbrauchem führende Versorgungsleitung gesteuert wird, oder ist für jeden Hydroverbraucher eine hydraulische Gleichrichterschaltung mit vier Rückschlagventilen und einem einzigen, für die Funktionen Heben und Senken verantwortlichen 2/2-Wege-Proportional-Druckregelventil vorgesehen. Das Lastkompensationssystem arbeitet mit elektrischen Druckaufnehmern, die an eine übergeordnete elektronische Steuervorrichtung angeschlossen sind, aus der das 2/2-Wege-Proportional-Regelventil entsprechend zur Lastkompensation angesteuert wird. Beim Senken wird ein in der Tankleitung angeordnetes Proportional-Druckventil elektrisch geöffnet, das jedoch funktionsbedingt erheblichen Staudruck erzeugt, der beim Senken des lastfreien Hydroverbrauchers die Geschwindigkeit vermindert. Bei einer Ausführungsform ist eine umsteuerbare Pumpe vorgesehen, die beim Senken einen Generator antreibt, um Strom zu erzeugen. Die umgesteuerte Pumpe öffnet das abströmseitige Rückschlagventil der Gleichrichterschaltung.At the DE 41 40 408 A1 Known control device are either for the functions lifting and lowering two separate 2/2-proportional pressure control valves provided, wherein the non-pressurized circulation is controlled via a supply line leading to further Hydroverbrauchem, or is provided for each hydraulic consumer, a hydraulic rectifier circuit with four check valves and a single, responsible for the functions lifting and lowering 2/2-way proportional pressure control valve. The load compensation system operates with electrical pressure transducers connected to a superordinate electronic control device, from which the 2/2-way proportional control valve is driven according to the load compensation. When lowering a arranged in the tank line proportional pressure valve is opened electrically, however, the function causes considerable back pressure, which reduces the speed when lowering the load-free Hydroverbrauchers. In one embodiment, a reversible pump is provided which drives a generator as it sinks to generate power. The reversed pump opens the downstream check valve of the rectifier circuit.

Bei einer aus EP 546 300 A1 bekannten elektrohydraulischen Steuervorrichtung ist bei einer Ausführungsform eine hydraulische Gleichrichterschaltung mit nur einem 2/2-Wege-Proportional-Regelventil für die Funktionen Heben und Senken vorgesehen. In der Tankleitung ist ein zum Senken aufsteuerbares Proportionaldruckregelventil angeordnet, das funktionsbedingt Staudruck aufbaut, der bei lastfrei abzusenkendem Hydroverbraucher Probleme bereitet.At one off EP 546 300 A1 known electro-hydraulic control device is provided in one embodiment, a hydraulic rectifier circuit with only a 2/2-way proportional control valve for the functions lifting and lowering. In the tank line a controllable for lowering proportional pressure control valve is arranged, the function builds back pressure, which causes problems with load-free abzusenkendem hydraulic consumers.

Die aus DE 202 08 577 V, Fig. 3, bekannte Steuervorrichtung für mehrere Hydroverbraucher enthält eine einzige Zweiwege-Druckwaage, die abwechselnd den drucklosen Umlauf steuert oder den Pumpenförderstrom unter den Hydroverbrauchem aufteilt.From DE 202 08 577 V, Fig. 3, known control device for a plurality of hydraulic consumers includes a single two-way pressure compensator, which alternately controls the non-pressurized circulation or divides the pump delivery flow among the Hydroverbrauchem.

Die DE 103 08 289 A mit älterem Zeitrang zeigt in einer Eingangssektion einer Steuervorrichtung eine einzige Zweiwege-Druckwaage, die abwechselnd entweder den drucklosen Umlauf des Pumpenförderstroms steuert oder den Versorgungs-Druck in einer allen parallel geschalteten, gleichrangigen Hydroverbrauchem gemeinsamen Versorgungsleitung einstellt.The DE 103 08 289 A with older seniority shows in an input section of a control device, a single two-way pressure compensator, which alternately controls either the non-pressurized circulation of the pump delivery flow or adjusts the supply pressure in all parallel-connected, equal hydronic consumption common supply line.

Der Erfindung liegt die Aufgabe zugrunde, eine elektrohydraulische Steuervorrichtung der eingangs genannten Art zu schaffen, die sich durch eine baulich einfache, kostengünstige und universell kombinierbare Eingangssektion auszeichnet.The invention has for its object to provide an electro-hydraulic control device of the type mentioned above, which is characterized by a structurally simple, inexpensive and universally combinable input section.

Die gestellte Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst.The stated object is achieved with the features of claim 1.

Durch die Parallel- oder Hintereinanderschaltung der Druckwaagen in der Eingangssektion werden mit nur zwei Zweiwege-Druckwaagen sowohl die Förderstrom-Aufteilfunktion als auch die Funktion des drucklosen Umlaufs für eine Vielfalt wahlweise an die Eingangssektion anbaubarer Verbraucher-Steuervorrichtungen ohne aufwendige Dreiwege-Druckwaage erzielt. Ferner ermöglicht die Vorspann-Zweiwege-Druckwaage in der Eingangssektion die bevorrechtigte Versorgung eines Prioritäts-Hydroverbrauchers ohne Dreiwege-Druckwaage. Die Prioritäts-Funktion kann für elektrische Hubstapler wichtig sein, bei denen eine zu hohe hydraulische Last die Batteriekapazität überfordern kann und dennoch die korrekte Versorgung des Prioritäts-Verbrauchers gewährleistet sein muss.Due to the parallel or series connection of the pressure compensators in the input section are achieved with only two two-way pressure compensators both the flow distribution function and the function of the non-pressurized circulation for a variety optionally attachable to the input section consumer control devices without consuming three-way pressure compensator. Further, the bias two-way pressure compensator in the input section allows the priority supply of a priority hydraulic consumer without a three-way pressure compensator. The Priority feature may be important for electric lift trucks where too high a hydraulic load is required Load can overwhelm the battery capacity and yet ensure the correct supply to the priority consumer.

In Abkehr von dem Prinzip, in der Eingangssektion gleich einen Teil der Steuervorrichtung für einen Verbraucher vorzusehen, ist es zweckmäßig, die Eingangssektion als mit einer Vielfalt von Anschlüssen ausgebildeten Blockmodul zu gestalten, der eine individuelle Bestückung mit Ventilkomponenten für unterschiedliche Einsatzfälle und den Anschluss verschiedenartiger Verbraucher-Steuervorrichtungen zulässt. Die Eingangssektion ist ein zum Aufbauen verschiedenartiger Steuervorrichtungen einsetzbarer und kostengünstiger Baustein, der die Grundfunktionen des drucklosen Umlaufes und der Förderstrom-Aufteilung bereitstellt, und auch die baulichen Voraussetzungen eines hydraulischen Lastkompensationssystems bietet.Contrary to the principle of providing a part of the control device for a consumer in the input section, it is expedient to design the input section as a block module designed with a multiplicity of connections, which can be individually equipped with valve components for different applications and the connection of different types of consumers Control devices. The input section is a building block that can be used to construct various types of control devices and is cost-effective, which provides the basic functions of pressureless circulation and delivery flow distribution and also offers the structural requirements of a hydraulic load compensation system.

Hierbei kann der Modulblock entweder einstückig oder aus mehreren Komponenten zusammengesetzt sein. Vorzugsweise sind mehrere gleichartige Anschlussbilder für ebenfalls als Module ausgebildete, weitere Steuervorrichtungssektionen vorgesehen.In this case, the module block can be composed either in one piece or from several components. Preferably, a plurality of similar connection patterns are also provided for further control device sections designed as modules.

Zweckmäßig hat der Blockmodul zumindest zwei identische Anschlussbilder der Versorgungs-, Lastdruck- und Tankleitungs-Anschlüsse, so dass sich weitere Modulblöcke mit entsprechenden Anschlussbildem wahlweise anbringen lassen. Zumindest ein Prioritäts-Verbraucher erhält auch tatsächlich die Priorität durch die entsprechende Positionierung an der Prioritätsseite der Eingangssektion.The block module expediently has at least two identical connection patterns of the supply, load pressure and tank line connections, so that further module blocks with corresponding connection patterns can optionally be attached. Also, at least one priority consumer actually gets the priority through the corresponding positioning on the priority page of the entry section.

Sind zumindest ein Prioritäts-Verbraucher und wenigstens ein Nachrang-Verbraucher vorgesehen, dann können in der Eingangssektion getrennte oder über eine Wechselventilanordnung verknüpfte Lastdruckleitungen vorgesehen sein, wobei die Vorspann-Zweiwege-Druckwaage an der Schließverstellseite mit der Lastdruckleitung des Prioritätsverbrauchers und die Umlauf-Zweiwege-Druckwaage an der Schließverstellseite entweder nur mit der Lastdruckleitung wenigstens eines Nachrang-Verbrauchers, oder wahlweise mit dem Lastdruck aus den Lastdruckleitungen wenigstens eines Nachrang-Verbrauchers oder des Prioritäts-Verbrauchers beaufschlagbar sind. Solange der Prioritäts-Verbraucher Priorität benötigt, wird ihm von der Vorspann-Zweiwege-Druckwaage der benötigte Förderstrom zugeteilt, gegebenenfalls auf Kosten nachrangiger Verbraucher.If at least one priority consumer and at least one subordinate consumer are provided, separate or pressure-load lines linked via a shuttle valve arrangement may be provided in the inlet section, the pretension two-way pressure compensator at the closing adjustment side being connected to the load pressure line of the priority consumer and the circulation two-way Pressure compensator on the Schließverstellseite either only with the load pressure line at least one subordinate consumer, or optionally with the load pressure from the load pressure lines at least one subordinate consumer or the priority consumer can be acted upon. As long as the priority consumer needs priority, it is powered by the bias two-way pressure compensator the required flow rate allocated, possibly at the expense of subordinate consumers.

Die Eingangssektion ist auch für eine regenerativ betreibbare Steuervorrichtung einsetzbar, deren Pumpe umsteuerbar ist und dann als Hydromotor den als Generator wirkenden Elektromotor antreibt. Ein baulicher Unterschied, der von vornherein oder modifizierbar in der Eingangssektion vorzusehen ist, besteht dann darin, dass zumindest ein Tankleitungsanschluss der Eingangssektion über die umsteuerbare Pumpe unter Umgehung beider Druckwaagen mit dem Tank verbindbar ist, um beim Senken verdrängtes Druckmittel über die als Hydromotor arbeitende Pumpe zum Tank zu fördern.The input section can also be used for a regeneratively operable control device whose pump is reversible and then drives the hydraulic motor acting as a generator electric motor. A structural difference that is provided from the outset or modifiable in the input section, then consists in that at least one tank line connection of the input section via the reversible pump, bypassing both pressure compensators with the tank is connected to displaced by lowering pressure medium on the working as a hydraulic motor pump to promote the tank.

Bei einer bevorzugten Ausführungsform ist in der Eingangssektion eine über Blenden abgesicherte Verbindungssteuerleitung zwischen den Lastdruckleitungen vorgesehen und an den Tankanschluss angeschlossen. Auf diese Weise lässt sich bei Bedarf das gesamte hydraulische Lastkompensationssystem druckentlasten.In a preferred embodiment, a connection control line protected by orifices is provided between the load pressure lines in the input section and connected to the tank connection. In this way, the entire hydraulic load compensation system can be relieved of pressure if necessary.

Eine wichtige Ausführungsform zeichnet sich dadurch aus, dass eine Lastdruckleitung, vorzugsweise die Lastdruckleitung zur Schließstellseite der Zweiwege-Umlauf-Druckwaage, über ein wahlweise betätigbares Magnetventil innerhalb des Lastkompensationssystems zum Tank entlastbar ist. Mittels dieses Ventils kann ein Druckbefehl in der Lastdruckleitung erzeugt werden (gewollter Druckabfall), der in wenigstens einer an die Eingangssektion angeschlossenen Steuersektion eine Funktion bewirkt, beispielsweise eine Senkfunktion. Von Vorteil ist dabei, dass beim Senken kein Staudruck für das Arbeitsmittel entsteht und das aufgesteuerte 2/2 Wege-Magnetventil nur einen kieinen Steuerdruckmitteistrom bewegt. Dies ist für eine SenKfunktion mit geringer oder ohne Last wünschenswert, um zuverlässig die eingestellte Geschwindigkeit zu fahren.An important embodiment is characterized in that a load pressure line, preferably the load pressure line to the closing side of the two-way rotary pressure compensator, can be relieved via a selectively actuated solenoid valve within the load compensation system to the tank. By means of this valve, a pressure command can be generated in the load pressure line (desired pressure drop), which causes a function in at least one control section connected to the input section, for example a lowering function. The advantage here is that when sinking no back pressure for the working fluid is created and the open-ended 2/2 way solenoid valve moves only a kieinen Steuerdruckmitteistrom. This is desirable for a low or no load sensing function to reliably drive the set speed.

Bei einer bevorzugten Ausführungsform ist der Prioritätsverbraucher, der mit seiner Steuervorrichtung an die Eingangssektion angeschlossen ist, ein doppelseitig beaufschlagbarer Hydroverbraucher. Wenigstens ein an die Eingangssektion angeschlossener Nachrang-Verbraucher kann ein gegen Last einseitig beaufschlagbarer Hydroverbraucher sein. Gegebenenfalls sind mehrere Nachrang-Verbraucher mit ihren Steuervorrichtungen in Serie an die Eingangssektion angeschlossen.In a preferred embodiment, the priority consumer, which is connected with its control device to the input section, a double-acting hydraulic consumer. At least one subordinate consumer connected to the input section can act unilaterally against load Be a hydraulic consumer. Optionally, several subordinate consumers are connected with their control devices in series to the input section.

Bei einseitig beaufschlagbaren Nachrang-Hydroverbrauchem ist es zur baulichen Vereinfachung für die Funktionen Heben und Senken zweckmäßig, nur ein für beide Funktionen verantwortliches 2/2-Wege-Proportionalregelventil in einer Diagonale einer hydraulischen Gleichrichterschaltung mit einer offenen Brücke zu verwenden. Um ohne hydroelektrische Druckwandler bei der Lastkompensation auszukommen, zweigt von der Diagonale oder von dem an die Tankleitung angeschlossenen Ast eine Lastdruckleitung ab, die in das hydraulische Lastkompensationssystem integriert ist. Die Funktion Senken wird über die Lastdruckleitung und das z.B. in der Eingangssektion angeordnete 2/2 Wege-Magnetschaltventil gesteuert, wodurch das Rückschlagventil der Gleichrichterschaltung zur Tankleitung öffnet und Arbeitsdruckmittel ohne Staudruck zum Tank ablässt. Falls nur ein Nachrang-Hydroverbraucher an die Eingangssektion angeschlossen sein sollte, könnte das 2/2-Wege-Magnetschaltventil in der Steuervorrichtung dieses Verbrauchers vorgesehen sein.In the case of one-sided action on secondary hydraulic consumption, it is expedient to simplify the functions of raising and lowering to use only one 2/2-way proportional control valve responsible for both functions in a diagonal of a hydraulic rectifier circuit with an open bridge. In order to make do without hydroelectric pressure transducers in the load compensation, branched off from the diagonal or connected to the tank branch a load pressure line, which is integrated into the hydraulic load compensation system. The lowering function is performed via the load pressure line and the e.g. controlled in the input section arranged 2/2 way magnetic switching valve, whereby the check valve of the rectifier circuit opens to the tank line and discharges working pressure fluid without back pressure to the tank. If only a subordinate hydraulic consumer should be connected to the input section, the 2/2-way solenoid valve could be provided in the control device of this consumer.

Um im Fall einer solchen Senksteuerung aus der hydraulischen Gleichrichterschaltung ein staudruckloses Ansprechverhalten zu erzielen, ist es zweckmäßig, wenn das an die Tankleitung angeschlossene Rückschlagventil ein durch einen Steuerkolben zwischen einer Offen- und einer Schließstellung betätigbare Schließglied aufweist, dessen Steuerkolben in Schießrichtung aus der Lastdruckleitung beaufschlagbar oder über die Lastdruckleitung und das kleine, kostengünstige 2/2-Wege-Magnetventil entlastbar ist. Das aufgesteuerte 2/2-Wege-Magnetventil leitet den Senkvorgang ein. Das in der Gleichrichterschaltung enthaltene 2/2-Wege-Proportionalregelventil regelt die Senkgeschwindigkeit über den Beaufschlagungsstrom des Proportionalmagneten.In order to achieve in the case of such a lowering control of the hydraulic rectifier circuit a zero backlash response, it is advantageous if the connected to the tank line check valve actuated by a control piston between an open and a closed position closing member, the control piston acted upon in the firing direction from the load pressure line or via the load pressure line and the small, inexpensive 2/2-way solenoid valve is relieved. The controlled 2/2-way solenoid valve initiates the lowering process. The 2/2-way proportional control valve contained in the rectifier circuit regulates the lowering speed via the application current of the proportional solenoid.

Die Eingangssektion mit den beiden Zweiwege-Druckwaagen ist speziell für Hubstapleranwendungen zum Aufbau individuell an die jeweiligen Anforderungen angepasster elektrohydraulischer Steuervorrichtungen zweckmäßig, lässt sich ohne Einschränkung aber auch für andere Hochdruck-Hydrauliksteuervorrichtungen in anderen Einsatzgebieten einsetzen.The inlet section with the two two-way pressure compensators is particularly suitable for lift truck applications for setting up individual electrohydraulic control devices adapted to the respective requirements, but can also be used without restriction for other high-pressure hydraulic control devices in other fields of application.

Anhand der Zeichnungen werden Ausführungsformen der Erfindung erläutert. Es zeigen:

Fig. 1
ein Blockschaltbild einer Ausführungsform einer Eingangssektion einer elektrohydraulischen Steuervorrichtung,
Fig. 2
ein Blockschaltbild einer anderen Ausführungsform der Eingangssektion,
Fig. 3
ein Blockschaltbild einer die Eingangssektion enthaltenden elektrohydraulischen Steuervorrichtung, und
Fig. 4
ein Blockschaltbild einer weiteren, die modifizierte Eingangssektion enthaltenden elektrohydraulischen Steuervorrichtung, die für teilweisen Regene-rativbetrieb ausgelegt ist.
With reference to the drawings embodiments of the invention will be explained. Show it:
Fig. 1
a block diagram of an embodiment of an input section of an electro-hydraulic control device,
Fig. 2
a block diagram of another embodiment of the input section,
Fig. 3
a block diagram of the input section containing electro-hydraulic control device, and
Fig. 4
a block diagram of another, the modified input section containing electro-hydraulic control device, which is designed for partial regenerative operation.

Eine in Fig. 1 schematisch gezeigte Eingangssektion E für eine elektrohydraulische Steuervorrichtung S (beispielsweise der Fig. 3 oder 4) ist ein einstückiger oder aus mehreren Komponenten zusammengesetzter Blockmodul 1, beispielsweise mit einem einstückigen Blockgehäuse 2, in welchem mehrere hydraulische (oder wahlweise auch elektrohydraulische) Komponenten enthalten sind, zweckmäßig austauschbar. Der Blockmodul 1 hat zumindest zwei identische Anschlussbilder mit Versorgungsleitungsanschlüssen 3, 3', Lastdruckleitungsanschlüssen 4, 4', Tankleitungsanschlüssen 5, 5', vorzugsweise an sich gegenüberliegenden Seiten des Blockmoduls, und an einer dritten Seite einen Pumpenleitungs-Anschluss 6 und einen Tankleitungsanschluss 7. An den Pumpenanschluss 6 wird eine Förderpumpe 8 angeschlossen, die von einem nicht gezeigten Elektromotor angetrieben ist, in einer Versorgungsleitung 9 zwischen den Anschlüssen 3, 3' ist eine Vorspann-Zweiwege-Druckwaage W1 angeordnet. Zwei Lastdruckleitungen 10, 10' von den Anschlüssen 4, 4' sind über eine Wechselventilanordnung 16 miteinander verknüpft. Zwischen den Anschlüssen 5, 5' verläuft eine Tankleitung 11, die mit dem zum Tank T offenen Anschluss 7 verbunden ist. Vom Pumpenanschluss 6 erstreckt sich eine Pumpenleitung 12 zur Versorgungsleitung 9. Von der Pumpenleitung 12 zweigt eine Ablassleitung 20 zum Tankanschluss 7 ab. In der Ablassleitung 20 ist eine Zweiwege-Umlauf-Druckwaage W2 angeordnet.An in Fig. 1 schematically shown input section E for an electro-hydraulic control device S (for example, the Fig. 3 or 4 ) is a one-piece or composed of several components block module 1, for example, with a one-piece block housing 2, in which a plurality of hydraulic (or optionally also electro-hydraulic) components are included, expedient interchangeable. The block module 1 has at least two identical connection patterns with supply line connections 3, 3 ', load pressure line connections 4, 4', tank line connections 5, 5 ', preferably on opposite sides of the block module, and on a third side a pump line connection 6 and a tank line connection 7. To the pump port 6, a feed pump 8 is connected, which is driven by an electric motor, not shown, in a supply line 9 between the terminals 3, 3 ', a bias two-way pressure compensator W1 is arranged. Two load pressure lines 10, 10 'of the terminals 4, 4' are linked together via a shuttle valve assembly 16. Between the terminals 5, 5 'runs a tank line 11 which is connected to the tank T open to the port 7. From the pump connection 6, a pump line 12 extends to the supply line 9. From the pump line 12, a discharge line 20 branches off to the tank connection 7. In the discharge line 20, a two-way circulation pressure compensator W2 is arranged.

Die Vorspann-Zweiwege-Druckwaage W1 wird auf ihrer Öffnungsstellseite über eine Vorsteuerleitung 13 mit dem Druck aus der Pumpenleitung 12 beaufschlagt, während die Schließstellseite 15 über eine Steuerleitung 14 aus der Lastdruckleitung 10 (und eine Regelfeder) beaufschlagt wird. An einem Mittelanschluss der Wechselventilanordnung 16 zweigt eine Steuerleitung 17 zur Schließstellseite 19 der Zweiwege-Umlauf-Druckwaage W2 ab, die auf ihrer Öffnungsstellseite aus einer Steuerleitung 18 beaufschlagt wird, die von de Ablassleitung 20 abzweigt. In der Eingangssektion E in Fig. 1 sind somit die beiden Zweiwege-Druckwaagen W1, W2 bezüglich der Pumpenleitung 12 parallel geschaltet.The bias two-way pressure compensator W1 is acted upon on its opening control side via a pilot control line 13 with the pressure from the pump line 12, while the closing side 15 is acted upon via a control line 14 from the load pressure line 10 (and a control spring). At a center port of the shuttle valve assembly 16 branches off a control line 17 to the closing side 19 of the two-way rotary pressure compensator W2, which is acted upon on its opening control side of a control line 18, which branches off from de drainage line 20. In the entrance section E in Fig. 1 Thus, the two two-way pressure compensators W1, W2 are connected in parallel with respect to the pump line 12.

Funktion:Function:

Liegt kein Lastdruck in den Lastdruckleitungen 10, 10' an, dann wird im Betrieb der Pumpe 8 die Zweiwege-Umlauf-Druckwaage W2 aufgesteuert, so dass der Förderstrom direkt in den Tank T gefördert wird.If no load pressure in the load pressure lines 10, 10 ', then the two-way circulation pressure compensator W2 is turned on during operation of the pump 8, so that the flow is conveyed directly into the tank T.

Liegt in der Lastdruckleitung 10 Lastdruck an, und in der Lastdruckleitung 10' ein niedrigerer oder gar kein Lastdruck, dann kann die Zweiwege-Vorspann-Druckwaage W1 in der dargestellten Absperrstellung bleiben. Über die Steuerleitung 17 bleibt auch die Zweiwege-Umlauf-Druckwaage W2 in der Absperrstellung, so dass der Förderstrom am Anschluss 3 geliefert wird. Nach Maßgabe der Höhe des Lastdrucks in der Lastdruckleitung 10 reguliert, falls die Pumpe 8 eine Konstantpumpe sein sollte, die Zweiwege-Umlauf-Druckwaage W2 als Zulaufregler die gerade notwendige Fördermenge für den Anschluss 3 ein bzw. lässt die Zweiwege-Vorspann-Druckwaage W1 den nicht am Anschluss 3 benötigten Teil des Förderstroms zum Anschluss 3' durchIf there is load pressure in the load pressure line 10 and a lower or no load pressure in the load pressure line 10 ', then the two-way bias pressure balance W1 can remain in the shut-off position shown. The two-way circulation pressure compensator W2 also remains in the shut-off position via the control line 17, so that the delivery flow is delivered to the connection 3. In accordance with the magnitude of the load pressure in the load pressure line 10, if the pump 8 should be a constant displacement pump, the two-way recirculation pressure compensator W2 as inflow regulator regulates the flow rate required for the port 3 or allows the two-way pressure compensator W1 not required at port 3 part of the flow to port 3 'by

Wird der Lastdruck in der Lastdruckleitung 10' höher als der Lastdruck in der Lastdruckleitung 10, so lässt dennoch die Zweiwege-Vorspann-Druckwaage W1 nur den Teil des Förderstroms zum Anschluss 3' durch, der in Abhängigkeit vom Lastdruck in der Lastdruckleitung 10 nicht im Anschluss 3 benötigt wird.If the load pressure in the load pressure line 10 'is higher than the load pressure in the load pressure line 10, nevertheless, the two-way bias pressure balance W1 only the part of the flow to the port 3', which in dependence on the load pressure in the load pressure line 10 not in the connection 3 is needed.

Herrscht in der Lastdruckleitung 10 kein Lastdruck, dann lässt die Zweiwege-Vorspann-Druckwaage W1 den ganzen Förderstrom zum Anschluss 3' durch, wobei, nach Maßgabe des Steuerdrucks in der Steuerleitung 17 aus der Lastdruckleitung 10' die Zweiwege-Umlauf-Druckwaage W2 als eine Art Zulaufregler (im Falle einer Konstantförderpumpe) regelnd eingreifen kann. Die Pumpe 8 kann auch drehzahlgeregelt sein und zumindest teilweise eine Zulaufregelfunktion erfüllen.If no load pressure prevails in the load pressure line 10, then the two-way bias pressure balance W1 passes the entire delivery flow to the connection 3 ', whereby, according to the control pressure in the control line 17 from the load pressure line 10', the two-way circulation pressure balance W2 as a Type inlet regulator (in the case of a constant displacement pump) can intervene regulating. The pump 8 can also be speed-controlled and at least partially fulfill an inlet control function.

Über den Anschluss 3 versorgte Hydroverbraucher haben somit stets Priorität gegenüber jedem am Anschluss 3' angeschlossenen Verbraucher.Hydro consumers supplied via port 3 thus always have priority over all consumers connected to port 3 '.

Die in Fig. 2 gezeigte Eingangssektion E unterscheidet sich von der von Fig. 1 dadurch, dass die Lastdruckleitungen 10, 10' nicht miteinander verknüpft sind, sondern die Lastdruckleitung 10 nur zur Schließstellseite 15 der Zweiwege-Vorspann-Druckwaage W1, und die Lastdruckleitung 10' nur zur Schließstellseite 19 der Zweiwege-Umlauf-Druckwaage W2 führen.In the Fig. 2 Input section E shown differs from that of Fig. 1 in that the load pressure lines 10, 10 'are not linked to each other, but the load pressure line 10 lead only to Schließstellseite 15 of the two-way bias pressure compensator W1, and the load pressure line 10' only to Schließstellseite 19 of the two-way circulation pressure compensator W2.

Die Ablassleitung 20' zweigt stromab der Zweiwege-Vorspann-Druckwaage W1 von der Versorgungsleitung 9 zur Zweiwege-Umlauf-Druckwaage W2 ab. Somit sind die beiden Zweiwege-Druckwaagen W1, W2 bezüglich der Pumpenleitung 12 in Serie geschaltet. Die Funktion ist ähnlich der zu Fig. 1 erläuterten Funktion.The discharge line 20 'branches off downstream of the two-way bias pressure compensator W1 from the supply line 9 to the two-way circulation pressure compensator W2. Thus, the two two-way pressure compensators W1, W2 are connected in series with respect to the pump line 12. The function is similar to that Fig. 1 explained function.

Die in Fig. 3 gezeigte elektrohydraulische Steuervorrichtung S wird aus einer Förderpumpe 8 versorgt, die beispielsweise von einem Elektromotor M antreibbar ist. Die Eingangssektion E bzw. der Blockmodul 1 ist hier verbunden mit einem Steuerblockmodul 21 für einen Prioritäts-Verbraucher V1 (doppelseitig beaufschlagbarer Hydroverbraucher), der über ein Mehrwege-Proportional-Schieberventil 24 (mit zwei Proportionalmagneten m4 und m5) betätigbar ist. Der Steuerblockmodul 21 ist beispielsweise an den Anschlüssen 3, 4, 5 der Eingangssektion E angeschlossen.In the Fig. 3 shown electro-hydraulic control device S is supplied from a feed pump 8, which is driven for example by an electric motor M. The input section E or the block module 1 is connected here to a control block module 21 for a priority consumer V1 (double-acting hydraulic consumer), which can be actuated via a multi-way proportional slide valve 24 (with two proportional magnets m4 and m5). The control block module 21 is connected to the terminals 3, 4, 5 of the input section E, for example.

An die Anschlüsse 3', 4', 5' der Eingangssektion E ist ein weiterer Steuer-Blockmodul 22 für einen Nachrang-Verbraucher V2 (zwei einseitig gegen Last beaufschlagbare Hydroverbraucher) angeschlossen, hinter dem wenigstens ein weiterer Steuerblockmodul 23 für einen Nachrang-Verbraucher V3 (einen einseitig gegen Last betätigbaren Hydroverbraucher) montiert ist.To the terminals 3 ', 4', 5 'of the input section E is another control block module 22 for a subordinate consumer V2 (two unilaterally acted upon load hydraulic consumers) connected behind the at least one further control block module 23 is mounted for a subordinate consumer V3 (a one-sided load actuated hydraulic consumer).

Die Eingangssektion E in Fig. 3 ist gegenüber der von Fig. 1 oder 2 modifiziert, indem von den Lastdruckleitungen 10, 10' Steuerleitungen 26, 27 abzweigen, die über eine Wechselventilanordnung 16' aus zwei Rückschlagventilen und eine Verbindungssteuherleitung 28 miteinander verbunden sind. Von der Verbindungsleitung 28 zweigt eine Steuerleitung 31 zur Ablassleitung 20' ab, in der für alle Verbraucher ein Druckbegrenzungsventil 33 für den Systemdruck im Lastkompensationssystem L der Steuervorrichtung vorgesehen ist. Zwischen den Steuerleitungen 26, 27 verläuft eine weitere Verbindungsleitung 29, in der zwei Blenden 30 platziert sind, zwischen denen eine Steuerleitung 33 zur Ablassleitung 20' stromab der Zweiwege-Umlauf-Druckwaage W2 abzweigt. Schließlich ist zwischen der Steuerleitung 26 und der Ablassleitung 20' stromab der Zweiwege-Umlauf-Druckwaage W2 ein Magnetventil, z.B. ein 2/2-Wege-Magnetventil 34 mit einem Betätigungsmagneten m3, vorgesehen, um bei Bedarf den am Anschluss 4' herrschenden Lastdruck zum Tank T abzulassen und, beispielsweise, für die Verbraucher V2 und/oder V3 eine Senkfunktion einzuleiten.The entrance section E in Fig. 3 is opposite to that of Fig. 1 or 2 modified by the load pressure lines 10, 10 'branch off control lines 26, 27 which are connected via a shuttle valve assembly 16' of two check valves and a Verbindungssteuherleitung 28 together. From the connecting line 28 branches off a control line 31 to the discharge line 20 ', in which a pressure relief valve 33 is provided for the system pressure in the load compensation system L of the control device for all consumers. Between the control lines 26, 27 extends another connecting line 29, in which two orifices 30 are placed, between which a control line 33 to the discharge line 20 'branches off downstream of the two-way circulation pressure compensator W2. Finally, between the control line 26 and the discharge line 20 'downstream of the two-way circulation pressure compensator W2, a solenoid valve, such as a 2/2-way solenoid valve 34 with an actuating magnet m3, provided to demand at the terminal 4' prevailing load pressure for Drain tank T and, for example, to initiate a lowering function for the consumers V2 and / or V3.

Die beiden Steuerblockmodule 22, 23 für die Nachrang-Verbraucher V2, V3 enthalten für die Funktionen Heben und Senken nur ein 2/2-Wege-Proportionalregelventil 25 bzw. 25', das in Abhängigkeit von der Bestromung seines Proportionalmagneten m1 bzw. m2 die Geschwindigkeit beim Heben bzw. Senken regelt, wobei die Funktion Heben bzw. Senken zwar durch das in der Eingangssektion E platzierte 2/2-Wege-Magnetventil 34 innerhalb des Lastkompensationssystems L gesteuert wird, das Arbeitsdruckmittel hingegen beim Senken direkt zum Tank T abgelassen wird.The two control block modules 22, 23 for the subordinate consumers V2, V3 contain for the lifting and lowering functions only a 2/2-way proportional control valve 25 and 25 ', depending on the energization of its proportional magnet m1 or m2 the speed controls when lifting or lowering, the lifting or lowering function is indeed controlled by the placed in the input section E 2/2-way solenoid valve 34 within the load compensation system L, the working pressure means, however, is drained directly to the tank T when lowering.

Jeder Steuerblockmodul 22, 23 enthält eine hydraulische Gleichrichterschaltung 35 mit einer offenen Brücke bestehend aus drei Ästen 36, 37, 38 und vier Rückschlagventilen 39, 40, 41, 42. Zwischen den Ästen 36, 38 ist eine Diagonale 43 vorgesehen, in der das 2/2-Wege-Proportional-Regelventil 25 (bzw. 25') angeordnet ist. Der Ast 37 ist mit dem Nachrang-Verbraucher V2 verbunden. Der Ast 36 ist über das zum Hydroverbraucher V2 öffnende Rückschlagventil 39 an die Versorgungsleitung 9 angeschlossen. Der Ast 38 ist über das zur Tankleitung 11' öffnende Rückschlagventil 42 an die Tankleitung 11' angeschlossen. Vom Ast 38 zweigt eine Lastdruckleitung 44 ab, in der ein weiteres Rückschlagventil 45, das zur Lastdruckleitung 10" öffnet, und stromab desselben eine Blende 46 vorgesehen sind, und die zur Lastdruckleitung 10" führt.Each control block module 22, 23 contains a hydraulic rectifier circuit 35 with an open bridge consisting of three branches 36, 37, 38 and four check valves 39, 40, 41, 42. Between the branches 36, 38 a diagonal 43 is provided, in which the 2 / 2-way proportional control valve 25 (or 25 ') is arranged. The branch 37 is connected to the secondary consumer V2. The branch 36 is connected to the supply line 9 via the non-return valve 39 which opens to the hydraulic consumer V2. The branch 38 is via the check valve 42 'opening to the tank line 11' connected to the tank line 11 '. From the branch 38 branches off a load pressure line 44, in which a further check valve 45, which opens to the load pressure line 10 ", and downstream of the same a diaphragm 46 are provided, and which leads to the load pressure line 10".

Das Rückschlagventil 42 enthält einen Ventilsitz 47, mit dem ein Schließglied 48 kooperiert, das durch einen Steuerkolben 49 (mit gegenüber dem Ventilsitz 47 größerer Beaufschlagungsfläche) betätigbar ist. Der Steuerkolben 49 wird durch eine Feder 50 beaufschlagt und ist auch mit dem in der Lastdruckleitung 44 herrschenden Druck stromab der Blende 46 beaufschlagbar, um die Schließstellung des Rückschlagventils 42 einzustellen. Der Ast 38 ist an einer Seite des Ventilsitzes 47 an das Rückschlagventil 42 angeschlossen, die Tankleitung 11' hingegen an der anderen Seite.The check valve 42 includes a valve seat 47, with which a closing member 48 cooperates, which is actuated by a control piston 49 (with respect to the valve seat 47 larger impact area). The control piston 49 is acted upon by a spring 50 and is also acted upon by the pressure prevailing in the load pressure line 44 downstream of the orifice 46 to adjust the closed position of the check valve 42. The branch 38 is connected to one side of the valve seat 47 to the check valve 42, the tank line 11 ', however, on the other side.

Das 2/2-Wege-Magnetventil 34 könnte auch im Steuermodulblock 22 (bzw. 23) zwischen der Steuerleitung 44 und der Tankleitung 11' installiert sein, beispielsweise falls nur einer der Steuerblockmodule vorgesehen ist. Ferner könnte das Rückschlagventil 42 auch anders ausgebildet sein, vorausgesetzt, es lässt sich mittels des Drucks aus der Steuerleitung 44 im erläuterten Sinne betätigen.The 2/2-way solenoid valve 34 could also be installed in the control module block 22 (or 23) between the control line 44 and the tank line 11 ', for example, if only one of the control block modules is provided. Furthermore, the check valve 42 could also be designed differently, provided that it can be actuated by means of the pressure from the control line 44 in the illustrated sense.

Funktion:Function:

Bei abgeschalteter Steuervorrichtung S ist das Lastkompensationssystem L über die Steuerleitung 32 druckentlastet. Beide Zweiwege-Druckwaagen W1, W2 stehen in den gezeigten Absperrstellungen. Wird die Pumpe 8 in Betrieb gesetzt, steuert die Zweiwege-Umlauf-Druckwaage W2 den drucklosen Umlauf zum Tank, wobei auch die Zweiwege-Vorspann-Druckwaage W1 auf Durchgang schaltet.When the control device S is switched off, the load compensation system L is depressurized via the control line 32. Both two-way pressure compensators W1, W2 are in the shut-off positions shown. When the pump 8 is put into operation, the two-way circulation pressure balance W2 controls the non-pressurized circulation to the tank, whereby the two-way bias pressure compensator W1 switches to passage.

Wird durch Bestromen der Proportionalmagneten m4 oder m5 der Prioritätsverbraucher V1 betätigt, verstellt sich die Zweiwege-Vorspann-Druckwaage W1 in Richtung zur Absperrstellung, so dass der Prioritätsverbraucher V1 mit dem erforderlichen Förderstrom versorgt wird. Der gegebenenfalls überschüssige Teil des Fördestroms wird über die Ablassleitung 20' zum Tank T abgelassen. Wird beispielsweise der Nachrang-Verbraucher V2 bei stromlosem Magneten m3 durch Bestromen des Proportionalmagneten m1 für die Funktion Heben betätigt, dann verstellt sich auch die Zweiwege-Umlauf-Druckwaage W2 in Richtung zur Durchgangsstellung, so dass der zugeteilte Förderstrom in der Versorgungsleitung 9 über das öffnende Rückschlagventil 39, das 2/2-Wege-Proportionalregelventil 25 in der Diagonale 43 zum Ast 38 strömt, das Rückschlagventil 41 öffnet, und den Nachrang-Verbraucher V2 beaufschlagt. Falls, beispielsweise im Fall einer Konstantförderpumpe 8, noch ein Überschuss im Förderstrom existieren sollte, dann kann dieser über die Zweiwege-Umlauf-Druckwaage zum Tank abgelassen werden. Selbst wenn der Lastdruck am Lastdruckanschluss 4' höher werden sollte als der Lastdruck in der Lastdruckleitung 10, wird die Priorität für den Prioritätsverbraucher V1 aufrecht gehalten. Der in der Steuerleitung 44 herrschende Lastdruck des Nachrang-Verbrauchers V2 hält das Rückschlagventil 42 geschlossen.If the priority consumer V1 is actuated by energizing the proportional magnets m4 or m5, the two-way biasing pressure compensator W1 moves in the direction of the shutoff position, so that the priority consumer V1 is supplied with the required delivery flow. The possibly excess part of the delivery flow is discharged via the discharge line 20 'to the tank T. If, for example, the subordinate consumer V2 with currentless magnet m3 by energizing the proportional magnet Pressed m1 for the lift function, then the two-way circulation pressure compensator W2 adjusted toward the passage position, so that the allocated flow in the supply line 9 via the opening check valve 39, the 2/2-way proportional control valve 25 in the diagonal 43 flows to the branch 38, the check valve 41 opens, and the subordinate consumer V2 acted upon. If, for example, in the case of a constant displacement pump 8, there should still be an excess in the flow, then this can be drained via the two-way circulation pressure compensator to the tank. Even if the load pressure at the load pressure port 4 'should become higher than the load pressure in the load pressure line 10, the priority for the priority consumer V1 is maintained. The prevailing in the control line 44 load pressure of the secondary consumer V2 keeps the check valve 42 closed.

Soll für den Nachrang-Verbraucher V2 die Funktion Senken eingesteuert werden, wird der Schaltmagnet m3 bestromt, so dass nicht nur die Lastdruckleitung 44 sondern auch die Lastdruckleitung 10' entlastet werden. Der Steuerkolben 49 wird durch den Druckabfall gegen die Kraft der Feder 50 verschoben, so dass das Rückschlagventil 42 voll öffnet. Das Arbeitsdruckmittel aus dem Nachrang-Verbrauchers V2 öffnet das Rückschlagventil 40 im Ast 36 und strömt mit der durch die Bestromung des Proportionalmagneten M1 eingestellten Geschwindigkeit und Fördermenge geregelt durch die Diagonale 43 und den Ast 38 in die Tankleitung 11'.If the function sinks is to be controlled for the subordinate consumer V2, the switching magnet m3 is supplied with current, so that not only the load pressure line 44 but also the load pressure line 10 'are relieved. The control piston 49 is displaced by the pressure drop against the force of the spring 50, so that the check valve 42 fully opens. The working pressure medium from the subordinate consumer V2 opens the check valve 40 in the branch 36 and flows with the set by the energization of the proportional solenoid M1 speed and flow controlled by the diagonal 43 and the branch 38 in the tank line 11 '.

Die in Fig. 4 gezeigte elektrohydraulische Steuervorrichtung S unterscheidet sich von der von Fig. 3 durch eine integrierte Regenerativfunktion. Dies bedeutet, dass mit dem beim Senken jedes Nachrangverbrauchers V2, V3 verdrängten Arbeitsdruckmittel elektrische Energie erzeugt wird. Für diese Funktion ist die Eingangssektion E modifiziert, und auch jeder Steuermodulbloock 22, 23.In the Fig. 4 shown electro-hydraulic control device S is different from that of Fig. 3 through an integrated regenerative function. This means that electrical energy is generated with the working pressure medium displaced when each subordinate consumer V2, V3 is lowered. For this function, the input section E is modified, and also each control module block 22, 23.

Die Pumpe 8' ist eine umkehrbare Pumpe, die im Umkehrbetrieb als Hydromotor arbeitet und einen als Generator arbeitenden Elektromotor MG treibt. In der Eingangsektion E ist der Tankleitungsanschluss 5' über einen Tankleitungsstrang 11" mit einem Anschluss 51 in der Pumpenleitung 12 verbunden. Zwischen der Lastdruckleitung 10' und der Ablassleitung 20' ist keine Verbindung vorgesehen oder ist die Verbindung abgesperrt. Das 2/2-Wege-Magnetventil 34 von Fig. 3 fehlt oder ist deaktiviert.The pump 8 'is a reversible pump, which operates in reverse operation as a hydraulic motor and drives a generator operating as an electric motor MG. In the inlet section E, the tank-line connection 5 'is connected via a tank-line branch 11 "to a connection 51 in the pump line 12. No connection is provided between the load-pressure line 10' and the outlet line 20 'or is the connection shut off. The 2/2-way solenoid valve 34 of Fig. 3 is missing or disabled.

In jedem Steuerblockmodul 22 und 23 ist das Rückschlagventil 42, das zur Tankleitung 11' öffnet, nicht mit der Lastdruckleitung 44 verbunden.In each control block module 22 and 23, the check valve 42, which opens to the tank line 11 ', is not connected to the load pressure line 44.

Funktion:Function:

Die Priorität des Prioritäts-Verbrauchers V1 ist in jedem Fall gegeben, unabhängig davon, ob die Nachrang-Verbraucher betätigt sind, oder nicht, und auch unabhängig davon, ob der Lastdruck der Nachrang-Verbraucher V2, V3 höher ist als der Lastdruck des Prioritäts-Verbrauchers V1 oder nicht.The priority of the priority consumer V1 is given in each case, irrespective of whether the subordinate consumers are actuated or not, and also regardless of whether the sub-consumer load pressure V2, V3 is higher than the load pressure of the priority consumer. Consumer V1 or not.

Die Funktion Heben für jeden Nachrang-Verbraucher V2 oder V3 läuft wie anhand von Fig. 3 beschrieben ab.The lifting function for each subordinate consumer V2 or V3 runs as per Fig. 3 described from.

Die Funktion Senken jedes Nachrang-Verbrauchers V2 und/oder V3 wird durch den Umkehrbetrieb der Pumpe 8' und die entsprechende Bestromung des Proportionalmagneten m1 bzw. m2 eingeleitet, wobei der Prioritätsverbraucher V1 nicht betätigt ist. Durch den über die Pumpe 8' erzeugten Drucksenkungsimpuls wird das Rückschlagventil 42 geöffnet und das Arbeitsdruckmittel strömt durch die Pumpe 8' zum Tank T, wobei der Motorgenerator MG Strom erzeugt. Um beim lastfreien Senken des Nachrang-Verbrauchers V2 oder V3 die am Proportionalmagneten m1 bzw. m2 eingestellte Geschwindigkeit zu erzielen, wird gegebenenfalls die Pumpe 8' auf Leerlauf-Umkehrbetrieb geschaltet.The function of lowering each subordinate consumer V2 and / or V3 is initiated by the reverse operation of the pump 8 'and the corresponding energization of the proportional magnet m1 or m2, the priority consumer V1 is not actuated. By the pressure reduction pulse generated by the pump 8 ', the check valve 42 is opened and the working pressure fluid flows through the pump 8' to the tank T, the motor generator MG generating power. In order to achieve the speed set on the proportional solenoid m1 or m2 during load-free lowering of the subordinate consumer V2 or V3, the pump 8 'is optionally switched to idling reverse operation.

Claims (10)

  1. Electrohydraulic control device (S) for at least two hydraulic consumers (V1, V2, V3), in particular for a stacker truck, with a two-way rotating pressure balance (W2) between a pump (8, 8') and a tank (T), a preloading pressure balance (W1) for distributing the pump delivery flow amongst the hydraulic consumers, and with a load compensation system (L), characterized in that the preloading pressure balance (W1), which is arranged in an input section (E) of the control device (S), is in the form of a two-way pressure balance and is jointly assigned to all the hydraulic consumers (V1, V2, V3) provided in relation to the pump (8, 8') parallel to or upstream of the two-way rotating pressure balance (W2), which is likewise arranged in the input section (E), and is arranged in a supply line (9) to at least one subordinate consumer (V2, V3), in such a way that the preloading pressure balance (W1) makes possible the prioritized supply to a priority consumer (V1).
  2. Electrohydraulic control device according to Claim 1, characterized in that the input section (E) is in the form of a block module (1) with pump and tank connections (6, 7) and supply, load-pressure and tank-line connections (3, 4, 5, 3', 4', 5') with at least two identical connection schemes for the supply, load-pressure and tank-line connections (3, 4, 5, 3', 4', 5'), and in that a connection scheme is in the form of a priority connection scheme for connecting the priority consumer (V1).
  3. Electrohydraulic control device according to Claim 2, characterized in that the block module (1) is an integral housing block or comprises components.
  4. Electrohydraulic control device according to Claim 1, characterized in that the load compensation system (L) has load pressure lines (10, 10') in the input section (E) which are separated or are linked via a shuttle valve arrangement (16, 16'), for the at least one priority consumer (V1) and at least one subordinate consumer (V2, V3), and in that exclusively the load pressure of the priority consumer (V1) can be applied to the preloading two-way pressure balance (W1) on the closing side (15), and either the load pressure of at least one subordinate consumer (V2, V3) or optionally the load pressure of at least one subordinate consumer (V2, V3) or the priority consumer (V1) can be applied to the two-way rotating pressure balance (W2) on the closing side (19).
  5. Electrohydraulic control device according to at least one of the preceding claims, characterized in that the pump (8') can be switched over and, in the switched-over direction, drives, as a hydraulic motor, the drive motor (MG), which is in the form of a generator, and in that at least one tank-line connection (5) of the input section (E) can be connected to the tank (T) via the supply line (12) and the pump (8') whilst bypassing the two pressure balances (W1, W2).
  6. Electrohydraulic control device according to Claim 4, characterized in that a connecting line (29), which is safeguarded via inductors (30), is provided between the load pressure lines (10, 10') in the input section (E) and connected to the tank-line connection (7).
  7. Electrohydraulic control device according to Claim 4, characterized in that the load pressure line (10'), which leads to the closing side (19) of the two-way rotating pressure balance (W2), can be relieved of load via an optionally actuable 2/2-way switching solenoid valve (34) in the load compensation system (L) to the tank connection (7).
  8. Electrohydraulic control device according to Claim 1, with consumer block modules (21, 22, 23), characterized in that the priority consumer (V1), which can be connected to the input section (E) with the consumer block module (21), is a twin-action hydraulic consumer, and in that subordinate consumers (V2, V3), which can be attached to the input section (E) with further consumer block modules (22, 23), which are preferably arranged in a row, are hydraulic consumers which can be acted upon on one side counter to the load.
  9. Electrohydraulic control device according to Claim 8, characterized in that the consumer block module (22, 23) of a subordinate consumer (V2, V3) has a single 2/2-way proportional control valve (25, 25') in a diagonal (43) of a hydraulic rectifier circuit (35) with four nonreturn valves (39 to 42) in an open bridge, in that two branches (36, 38) of the bridge which can be connected to the subordinate consumer (V2, V3) are connected to the supply line (9') or the tank line (11'), and in that a load pressure line (44), which is connected to the hydraulic load compensation system (L), branches off from the branch (38), which is connected to the tank line (11').
  10. Electrohydraulic control system according to Claim 9, characterized in that one nonreturn valve (42), which is arranged between the branch (38) connected to the tank line (11') and the tank line (11'), has a closing element (48), which can be actuated by a control piston (49) between an open position and a closed position, the control piston (49) of said closing element either being capable of being acted upon in the closing direction from the load pressure line (44) or being capable of being relieved of load via the load pressure line (44) and a solenoid valve, preferably the 2/2-way switching solenoid valve (34) which is arranged in the input section (E).
EP20050012251 2004-09-08 2005-06-07 Electro-hydraulic control device Expired - Fee Related EP1635072B1 (en)

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DE200420014030 DE202004014030U1 (en) 2004-09-08 2004-09-08 Electrohydraulic control device

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DE102009028816A1 (en) * 2009-08-21 2011-02-24 Deere & Company, Moline Hydraulic arrangement
EP2465812B1 (en) * 2010-12-16 2013-11-06 BT Products AB Industrial truck comprising an extendable mast
ITUB20152856A1 (en) * 2015-08-04 2017-02-04 Antonioni Hydraulic Solutions S R L HYDRAULIC ACTUATOR, PARTICULARLY OF THE SUSPENSION AND / OR DAMPER TYPE.
CN105035979B (en) * 2015-08-05 2017-05-03 常德中联重科液压有限公司 Balance valve group and hydraulic system
EP3171039A1 (en) * 2015-11-18 2017-05-24 HAWE Hydraulik SE Hydraulic lifting module having a lifting and lowering function
EP4019786B1 (en) 2020-12-28 2023-11-22 Danfoss Power Solutions (Zhejiang) Co. Ltd Load-sensing multi-way valve work section

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US5129229A (en) * 1990-06-19 1992-07-14 Hitachi Construction Machinery Co., Ltd. Hydraulic drive system for civil-engineering and construction machine
DE4140408A1 (en) 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Electrohydraulic control of linear hydraulic actuator - has proportional flow control valve responding to pressure feedback to provide load compensating action
DE4140409A1 (en) 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De ELECTROHYDRAULIC CONTROL DEVICE
SE9300084L (en) * 1993-01-14 1994-04-18 Voac Hydraulics Boraas Ab Procedure for controlling a hydraulic motor, as well as hydraulic valve for this
DE29802498U1 (en) 1998-02-13 1998-04-16 Heilmeier & Weinlein Forklift control
DE20208577U1 (en) 2002-06-03 2003-12-11 Hawe Hydraulik Gmbh & Co. Kg Electro-hydraulic lift control device for industrial trucks
DE10308289B4 (en) 2003-02-26 2010-11-25 Bosch Rexroth Aktiengesellschaft LS-way valve block

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