EP1635072A1 - Electro-hydraulic control device - Google Patents

Electro-hydraulic control device Download PDF

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Publication number
EP1635072A1
EP1635072A1 EP05012251A EP05012251A EP1635072A1 EP 1635072 A1 EP1635072 A1 EP 1635072A1 EP 05012251 A EP05012251 A EP 05012251A EP 05012251 A EP05012251 A EP 05012251A EP 1635072 A1 EP1635072 A1 EP 1635072A1
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EP
European Patent Office
Prior art keywords
line
pressure
consumer
load
way
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP05012251A
Other languages
German (de)
French (fr)
Other versions
EP1635072B1 (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 date
Priority to DE200420014030 priority Critical patent/DE202004014030U1/en
Application filed by Hawe Hydraulik GmbH and Co KG filed Critical Hawe Hydraulik GmbH and Co KG
Publication of EP1635072A1 publication Critical patent/EP1635072A1/en
Application granted granted Critical
Publication of EP1635072B1 publication Critical patent/EP1635072B1/en
Expired - Fee Related legal-status Critical Current
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162Servomotor 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/006Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445Systems 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055Systems 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/14Energy-recuperation means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/505Pressure control characterised by the type of pressure control means
    • F15B2211/50563Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves

Abstract

In an electrohydraulic control device (S) for at least two hydraulic consumers (V1, V2, V3) for a forklift, a two-way circulation pressure compensator (W2) and a pretensioning system are connected between a pump (8, 8 ') and a tank (T). Pressure balance (W1) for dividing the pump flow under the Hydroverbrauchem, as well as a load compensation system (L) provided and the bias pressure compensator (W1) is designed as a two-way pressure compensator and relative to the pump (8, 8 ') parallel to or upstream of the two-way Circulating pressure compensator (W2) arranged in an input section (E).

Description

  • The invention relates to an electro-hydraulic control device specified in the preamble of claim 1 Art.
  • In the known from DE 298 02 498 U1 electro-hydraulic control device is provided in the input section, which is also responsible for the control of a priority consumer, 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.
  • In the electrohydraulic control device known from DE 41 40 408 A1, two separate 2/2-proportional pressure control valves are provided either for the functions lifting and lowering, wherein the non-pressurized circulation is controlled via a supply line leading to further Hydroverbrauchem, or is one for each hydraulic consumer Hydraulic rectifier circuit with four check valves and a single, for the functions lifting and lowering responsible 2/2-way proportional pressure control valve provided. The load compensation system operates with electrical pressure sensors which are connected to a higher-level 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, but due to the functional causes back pressure for the discharged working flow, which can lead to problems when lowering the load-free hydraulic consumer. In one embodiment with a hydraulic rectifier circuit, a reversible pump is provided which drives a generator during engine operation to produce power during drainage. The reversed pump opens the downstream check valve of the rectifier circuit.
  • In one known from EP 546 300 A1 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.
  • The known 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.
  • 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 either controls the non-pressurized circulation of the pump delivery flow or adjusts the supply pressure in a parallel connected, equal hydropower 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 stated object is achieved with the features of claim 1.
  • 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. Furthermore, the bias two-way pressure compensator in the inlet section optionally allows the preferential 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.
  • 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 formed 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 the non-pressurized circulation and the delivery flow distribution, and also provides the structural requirements of a hydraulic load compensation system.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 controlled 2/2-way solenoid valve moves only a small control pressure medium flow. This is desirable for a low or no load lowering function to reliably drive the set speed.
  • 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.
  • 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 solenoid 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.
  • 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.
  • 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.
  • 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.
  • An input section E schematically shown in FIG. 1 for an electrohydraulic control device S (for example of FIGS. 3 or 4) is a one-piece or multi-component 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, expediently austuaschbar. 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.
  • 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 input 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.
  • Function:
  • 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.
  • If 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.
  • 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.
  • 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.
  • Hydro consumers supplied via port 3 thus always have priority over all consumers connected to port 3 '.
  • The input section E shown in Fig. 2 differs from that of Fig. 1 in that the load pressure lines 10, 10 'are not linked, but the load pressure line 10 only to Schließstellseite 15 of the two-way bias pressure compensator W1, and the load pressure line 10th 'only lead to closing side 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. 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 the function explained with reference to FIG.
  • The electro-hydraulic control device S shown in FIG. 3 is supplied from a feed pump 8, which can be driven by an electric motor M, for example. 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.
  • 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).
  • The input section E in FIG. 3 is modified from that of FIG. 1 or 2 by branching off from the load pressure lines 10, 10 'control lines 26, 27, which are connected to one another via a shuttle valve arrangement 16' comprising two check valves and a connection control line 28. 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 drain line 20 'downstream of the two-way recirculation weigher W2 is a solenoid valve, e.g. a 2/2-way solenoid valve 34 with an actuating magnet m3, provided to release if necessary the load pressure prevailing at the terminal 4 'to the 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 functions lifting and lowering 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. 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.
  • Function:
  • 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.
  • 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.
  • 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 '.
  • The electro-hydraulic control device S shown in FIG. 4 differs from that of FIG. 3 by 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. 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 absent or deactivated.
  • 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.
  • Function:
  • 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.
  • The lifting function for each subordinate consumer V2 or V3 proceeds as described with reference to FIG.
  • 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 lift truck, with a two-way circulation pressure compensator (W2) between a pump (8, 8 ') and a tank (T), a leader Pressure balance (W1) for dividing the pump delivery flow among the hydraulic consumers, and with a load compensation system (L), characterized in that the bias pressure compensator (W1) designed as a two-way pressure compensator and relative to the pump (8, 8 ') parallel to or upstream of the two-way circulation pressure balance (W2) in an input section (E) of the control device (S) is arranged.
  2. Electrohydraulic control device according to claim 1, characterized in that the input section (E) as 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') is formed with at least two identical Anschlußbildem for the supply, load pressure and tank line connections (3, 4, 5, 3 ', 4', 5 '), preferably with one of them as a priority connection diagram ,
  3. Electrohydraulic control device according to claim 2, characterized in that the block module (1) is a one-piece housing block or composed of components.
  4. Electrohydraulic control device according to claim 1, characterized in that for at least one priority consumer (V1) and at least one secondary consumer (V2, V3) the load compensation system (L) in the input section (E) is separate or via a shuttle valve arrangement (16, 16 ') associated load pressure lines (10, 10'), and that the bias two-way pressure compensator (W1) on Schließverstellseite (15) exclusively with the load pressure of the priority consumer (V1) and the two-way circulation pressure compensator (W2) at the Schließverstellseite (19) either with the load pressure of at least one subordinate consumer (V2, V3) or optionally with the load pressure of at least one subordinate consumer (V2, V3) or the priority consumer (V1) can be acted upon.
  5. Electrohydraulic control device according to at least one of the preceding claims, characterized in that the pump (8 ') is reversible and in the reversed direction as a hydraulic motor drives the generator designed as a drive motor (MG), and that at least one tank line connection (5) of the input section (E) via the supply line (12) and the pump (8 ') bypassing both pressure compensators (W1, W2) to the tank (T) is connectable.
  6. Electrohydraulic control device according to claim 4, characterized in that in the input section (E) via a throttles (30) secured connection line (29) between the load pressure lines (10, 10 ') is provided and connected to the tank line connection (7).
  7. Electrohydraulic control device according to at least one of claims 1 to 4, characterized in that the closing side (19), preferably, the two-way circulation pressure compensator (W2) leading load pressure line (10 ') via an optionally operable 2/2-way solenoid valve (34) in the load compensation system (L) to the tank connection (7) is relieved.
  8. Electrohydraulic control device according to Claim 4, characterized in that the priority consumer (V1) which is connected to the input section (E) with a consumer block module (21) is a double-acting hydraulic consumer, and that with further consumers, preferably in series, consumers Block modules (22, 23) to the input section (E) attached subordinate consumers (V2, V3) are unilaterally load actuated hydraulic consumers.
  9. Electrohydraulic control device according to claim 8, characterized in that the consumer block module (22, 23) of a subordinate consumer (V2, V3) in a diagonal (43) of a hydraulic rectifier circuit (35) with four check valves (39 to 42) in a has a single 2/2-way proportional control valve (25, 25 ') that two connected to the load (V2, V3) branches (36, 38) of the bridge to the supply line (9') and the tank line ( 11 ') are connected, and that of the connected to the tank line (11') Branch (38) branches off to the hydraulic load compensation system (L) connected load pressure line (44).
  10. Electrohydraulic control system according to claim 9, characterized in that the one between the to the tank line (11 ') connected branch (38) and the tank line (11') arranged check valve (42) by a control piston (49) between an open and a closing position operable closing member (48), the control piston (49) in the closing direction either from the load pressure line (44) acted upon or via the load pressure line (44) and a solenoid valve, preferably arranged in the input section (E) 2/2-way Mag-net switching valve (34), is relieved.
EP20050012251 2004-09-08 2005-06-07 Electro-hydraulic control device Expired - Fee Related EP1635072B1 (en)

Priority Applications (1)

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

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EP1635072A1 true EP1635072A1 (en) 2006-03-15
EP1635072B1 EP1635072B1 (en) 2008-02-13

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DE (2) DE202004014030U1 (en)

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DE102009028816A1 (en) * 2009-08-21 2011-02-24 Deere & Company, Moline Hydraulic arrangement
EP2465812A1 (en) * 2010-12-16 2012-06-20 BT Products AB Industrial truck comprising an extendable mast
CN105035979A (en) * 2015-08-05 2015-11-11 常德中联重科液压有限公司 Balance valve group and hydraulic system

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ITUB20152856A1 (en) * 2015-08-04 2017-02-04 Antonioni Hydraulic Solutions S R L hydraulic actuator, particularly the amortized type and / or damper.
EP3171039A1 (en) * 2015-11-18 2017-05-24 HAWE Hydraulik SE Hydraulic lifting module having a lifting and lowering function

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EP0546300A1 (en) 1991-12-07 1993-06-16 Robert Bosch Gmbh Electrohydraulic control system
EP0607108A2 (en) * 1993-01-14 1994-07-20 Voac Hydraulics Boras Ab A method for controlling a hydraulic motor and a hydraulic valve therefor
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
DE10308289A1 (en) 2003-02-26 2004-09-09 Bosch Rexroth Ag LS-valve block control/drive method e.g. for work appliance such as farm tractor, requires operating electric control valve arrangements in relation to changed differential control pressure

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EP0462590A1 (en) * 1990-06-19 1991-12-27 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
EP0546300A1 (en) 1991-12-07 1993-06-16 Robert Bosch Gmbh Electrohydraulic control system
EP0607108A2 (en) * 1993-01-14 1994-07-20 Voac Hydraulics Boras Ab A method for controlling a hydraulic motor and a hydraulic valve therefor
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
DE10308289A1 (en) 2003-02-26 2004-09-09 Bosch Rexroth Ag LS-valve block control/drive method e.g. for work appliance such as farm tractor, requires operating electric control valve arrangements in relation to changed differential control pressure

Cited By (4)

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Publication number Priority date Publication date Assignee Title
DE102009028816A1 (en) * 2009-08-21 2011-02-24 Deere & Company, Moline Hydraulic arrangement
CN101994725A (en) * 2009-08-21 2011-03-30 迪尔公司 Hydraulic assembly
EP2465812A1 (en) * 2010-12-16 2012-06-20 BT Products AB Industrial truck comprising an extendable mast
CN105035979A (en) * 2015-08-05 2015-11-11 常德中联重科液压有限公司 Balance valve group and hydraulic system

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DE202004014030U1 (en) 2006-01-12
DE502005002807D1 (en) 2008-03-27

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