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EP1635070B1 - Electro-hydraulic control device - Google Patents

Electro-hydraulic control device Download PDF

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Publication number
EP1635070B1
EP1635070B1 EP20050013372 EP05013372A EP1635070B1 EP 1635070 B1 EP1635070 B1 EP 1635070B1 EP 20050013372 EP20050013372 EP 20050013372 EP 05013372 A EP05013372 A EP 05013372A EP 1635070 B1 EP1635070 B1 EP 1635070B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
line
valve
load
load pressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP20050013372
Other languages
German (de)
French (fr)
Other versions
EP1635070A1 (en
EP1635070B8 (en
Inventor
Martin Dipl.-Ing. Univ. 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 SE
Original Assignee
Hawe Hydraulik GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hawe Hydraulik GmbH and Co KG filed Critical Hawe Hydraulik GmbH and Co KG
Publication of EP1635070A1 publication Critical patent/EP1635070A1/en
Application granted granted Critical
Publication of EP1635070B1 publication Critical patent/EP1635070B1/en
Publication of EP1635070B8 publication Critical patent/EP1635070B8/en
Not-in-force 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
    • F15B11/006—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
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • 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"
    • 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

Definitions

  • the invention relates to an electro-hydraulic control device specified in the preamble of claim 1 Art.
  • a known control device includes a unilaterally between the supply line and the tank line open rectifier circuit.
  • the branching from the diagonal load pressure line is connected to load compensation to an adjustment for the flow rate of the variable.
  • two pilot-operated or unlockable non-return valves are incorporated in the rectifier circuit, both of which are controlled during lifting and turned on for lowering. Since the check valve opened on lowering to the tank must control and combine the control oil flow from the other check valve and the working flow and adjust the load pressure on the opening side of a sampling valve, the lowering control becomes difficult at low lowering speed and low load or no-load lifting cylinder.
  • the lowering function is controlled in the current-fed 2/2-way proportional control valve and energized proportional pressure valve in the tank line, the design of the proportional pressure valve in the tank line builds up a dynamic pressure at low load or even load-free to lowering hydraulic consumers set speed undesirable reduced. Sensitive control is difficult because the proportional pressure valve in the tank line must handle the entire working flow and at the same time generate a pressure signal for the lowering function.
  • the invention has for its object to provide an electro-hydraulic control device of the type mentioned, which is structurally and functionally simple and allows a sensitive speed control even when lowering.
  • the bridge Since the bridge is designed to be open on one side, the feed flow does not affect the non-return valve opening to the tank line.
  • This check valve is exposed only to the negligible pressure in the tank line and can be designed as the only one of the check valves of the rectifier circuit unlockable. It is possible to perform a sensitive speed control of the hydraulic consumer when lifting and lowering, even if quickly switched between lifting and lowering back and forth or a low lowering speed is driven.
  • the purely hydraulic load compensation system is structurally simple, cost-effective and reliable, and can be combined with other consumer-supplied controls from the same pump.
  • the 2/2-way proportional control valve is structurally simple, since it only needs to set the respective speed and regulate the set speed value, without affecting the load compensation.
  • the inlet regulator measures the flow rate for the hydraulic consumer load-compensated to and as needed. Since when lowering the pressure medium via the check valve opening to the tank line flows directly into the tank line and the check valve design causes hardly any back pressure, even with low load or load-free hydro consumer can drive any desired and possibly even the maximum lowering speed exactly.
  • the core of the concept is to hydraulically tap the load pressure for the control device of the hydraulic consumer and provide it as a hydraulic pressure signal for a purely hydraulic load compensation system, and to use this load pressure signal not only for load compensation but also for the function sinks, so that the 2/2-way -Proportional control valve only needs to fulfill the task of adjusting and regulating the speed.
  • a black and white magnet can be used for the 212-way control valve.
  • a valve opening to the tank check valve of the hydraulic rectifier circuit from the load pressure line is selectively reversible between the blocking position and the passage position.
  • the load pressure line is connected to a switchable between a lifting-blocking position and a lowering open position, to the tank line or tank opening solenoid valve.
  • the solenoid valve can therefore be physically small and inexpensive.
  • the check valve can be opened and closed by the pressure signal in the load pressure line. Thus, for example, by a generated by a reduction of the load pressure in the load pressure line load pressure signal, the lowering process can be initiated.
  • the solenoid valve is preferably a 2/2-way solenoid valve in poppet design, which guarantees freedom from leaks in the lifting-blocking position.
  • the check valve has a arranged between the tank line and a branch of the bridge valve seat, which is associated with a switchable by a control piston between a closed position and an open position closing member.
  • the control piston is acted upon from the load pressure line and relieved via the solenoid valve. In this way, the opening and closing movements of the check valve can be controlled very clean.
  • the solenoid valve is arranged in an inlet control section containing the input control section of the control device.
  • This input section has thus a basic equipment that can use as many hydro consumers.
  • electrohydraulic control device S for a cantilevered against load hydraulic consumer V3, typically a lift cylinder of a lift truck, is a modular deployable module 23 for building an electro-hydraulic control device assembly.
  • the module 23 contains a supply line 9 ', a tank line 11' and a load pressure line 10 ".
  • the tank line 11 ' leads to a tank T.
  • the supply line 9' leads from a pump 8 through a supply regulator Z.
  • the load pressure line 10" is connected to a hydraulic load compensation system and connected as a control line to the supply controller Z. If the pump 8 promotes speed control, the pump 8 could fulfill the function of the inlet regulator Z.
  • a hydraulic rectifier circuit 35 is provided with a three branches 36, 37, 38, one-sided open bridge and four check valves 39, 40, 41 and 42.
  • the branch 37 is connected to the hydraulic consumer V3.
  • the branch 36 is connected via the check valve 39 to the supply line 9 '.
  • the branch 38 is connected via the check valve 42 to the tank line 11 '.
  • a diagonal 43 is provided in which a 2/2-way proportional control valve 25 '(e.g., in poppet style) with a proportional solenoid m2 is included. If necessary, a black-and-white magnet is used instead of the proportional magnet m2.
  • the 2/2-way proportional control valve 25 ' is for setting and controlling the moving speed of the hydraulic consumer V3 both in lifting and lowering, and also for holding the load of the hydraulic consumer V3.
  • a check valve 45 to the load pressure line 10" and downstream of the same a diaphragm 46 is provided. Further, between the load pressure line 44 and the tank line 11 'is provided by a magnet m3 from the shut-off position shown in a passage position switchable solenoid valve 34, preferably a 2/2-way solenoid valve.
  • the check valve 42 can be brought and retained by the load pressure in the load pressure line 44 in the lifting-blocking position shown and by relieving the load pressure line 44 in its lowering open position.
  • An embodiment of the pilot-operated check valve 42 is indicated.
  • the check valve 42 includes between the branch 38 and the tank line 11 'a valve seat 47. With the valve seat 47 cooperates a closing member 48 which is operatively coupled to a control piston 49, by a spring 50 and by the pressure in the load pressure line 44th can be acted upon.
  • the loading surface of the control piston 49 is, for example, larger than the loading surface of the closing member 48.
  • the proportional magnet m2 is energized according to the desired speed while the pump 8 is running.
  • the pressure medium flows via the check valve 39, the branch 36, the 2/2-way proportional control valve 25 'and the check valve 41 to the hydraulic consumer V3.
  • the magnet m3 is not energized.
  • the check valve 42 is held by the load pressure in the lift-lock position shown.
  • the load pressure line 44 is depressurized at least downstream of the orifice 46.
  • the pressure relief (pressure signal) leads via the prevailing in the branch 38 load pressure to open the check valve 42.
  • the working pressure fluid flows directly into the tank line 11 '. Since, if necessary, a pressure reduction also occurs in the load pressure line 10 ", the inlet regulator Z does not deliver any flow.
  • Fig. 2 illustrates an electro-hydraulic control device arrangement for several unilaterally acted upon load hydraulic consumers V2, V3, from control modules 22, 23.
  • the structure of each module 22, 23 largely corresponds to the in Fig. 1 shown.
  • the check valves 42 are shown symbolically with an unlocking line 44 'connected to the load pressure line 44.
  • Each module 22, 23 contains a 2/2-way proportional control valve 25, 25 'with proportional magnets m1 and m2.
  • the hydraulic consumers V2, V3 can work together at different speeds or individually be operated for lifting and lowering.
  • the solenoid valve 34 could be housed in one of the modules 22, 23, as in FIG Fig. 1 or, as shown, the solenoid valve 34 is interposed between the load pressure line 10 "and the tank T common to and separate from all the modules Fig. 1 described.
  • Fig. 3 For example, there is shown an electro-hydraulic control device arrangement for a lift truck in which the modules 22, 23 of the Fig. 1 and 2 and a control block module 21 and an input section E are incorporated.
  • the pump 8 is driven by an electric motor M.
  • the input section E which is designed as a block module 1, is connected to the control block module 21 for a hydraulic 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 hydraulic consumer V1 has priority over the hydraulic consumption V2, V3 in the control device arrangement.
  • the hydraulic consumption modules V2, V3 are mounted on the other side of the inlet section, with the load pressure line 10 ", the supply line 9 'and the tank line 11' being led into the input section E 1.
  • the load compensation system L in the input section E is for example connected via a connection 4 'in the block module 1 with the load pressure line 10 ".
  • the load pressure line 10 receives the load pressure of the hydraulic consumer V1, and the load pressure line 10', the load pressure from the load pressure line 10 "from the load pressure lines 10, 10 'branch off control lines 26, 27 , which are connected to each other via a shuttle valve assembly 16 'of two check valves and a connecting line 28.
  • From the connecting line 28 branches off a control line 31 to a discharge line 20', in which a pressure relief valve 33 is provided for the system pressure in the load compensation system L for all hydraulic consumers.
  • a further connecting line 29 in which two apertures 30 are placed, between which a control line 33 to the outlet line 20 ' branches. That on the basis of Fig. 1 and 2 explained solenoid valve 34 is here integrated between the control line 26 and the drain line 20 'in the input section E.
  • a pump line 12 leads to a bias two-way pressure balance W1.
  • the drain line 20 ' includes a two-way recirculation pressure balance W2.
  • the load pressure line 10 is connected to the closing side of the two-way bias pressure compensator W1, while the opening control side is applied with derived from the pump line 12 control pressure.
  • the closing side of the two-way recirculation pressure compensator W2 is connected to the load pressure line 10 ', while the opening adjustment side with pilot pressure from the discharge line 20' is applied.
  • the two pressure compensators W1, W2 operate as an inlet regulator Z at least for the hydraulic consumers V2, V3, the hydraulic consumer V1 always having priority.
  • electro-hydraulic control device arrangement S differs from that of Fig. 3 through an integrated regenerative function. Electrical energy can be generated with the working pressure medium displaced when each hydraulic consumer V2, V3 is lowered.
  • the input section E and the modules 22, 23 are modified.
  • the pump 8 ' is a reversible pump, which operates as a hydraulic motor to reverse operation and drives a working as a generator electric motor MG.
  • a tank line connection 5 ' is connected via a tank line 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 the connection is blocked Fig. 3 is missing, or is disabled.
  • the check valve 42 which opens to the tank line 11 ', is disconnected from the load pressure line 44 (possibly a locked connection or simple check valve 42).
  • the pump 8 ' When lowering the hydraulic consumers V2 and / or V3, the pump 8 'is switched to reverse operation.
  • the proportional magnets m1 and m2 are energized accordingly.
  • the pressure lowering pulse generated by the pump 8 ' opens the check valve 42 and the working pressure fluid flows through the pump 8' to the tank T, wherein, at least within a predetermined flow and / or pressure range, the motor MG generates power.
  • the pump 8 ' At low load or in load-free state of the hydraulic consumer V2 and / or V3, the pump 8 'is optionally operated at idle to achieve the set speed accurately.

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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.

Die aus EP 0 057 355 A bekannte Steuervorrichtung enthält eine einseitig zwischen der Versorgungsleitung und der Tankleitung offene Gleichrichterschaltung. Die von der Diagonale abzweigende Lastdruckleitung ist zur Lastkompensation an eine Einstellvorrichtung für die Fördermenge der Verstellpumpe angeschlossen. Ferner sind zwei vorgesteuerte bzw. entsperrbare Rückschlagventile in die Gleichrichterschaltung eingegliedert, die beide beim Heben zugesteuert und zum Senken aufgesteuert werden. Da das beim Senken zum Tank aufgesteuerte Rückschlagventil den Steuerölstrom vom anderen Rückschlagventil und den Arbeitsstrom beherrschen und kombinieren sowie den Lastdruck an der Öffnungsseite eines Abtastventils einstellen muss, gestaltet sich die Senksteuerung bei niedriger Senkgeschwindigkeit und geringer Last oder lastfreien Hubzylindem schwierig.From EP 0 057 355 A known control device includes a unilaterally between the supply line and the tank line open rectifier circuit. The branching from the diagonal load pressure line is connected to load compensation to an adjustment for the flow rate of the variable. Furthermore, two pilot-operated or unlockable non-return valves are incorporated in the rectifier circuit, both of which are controlled during lifting and turned on for lowering. Since the check valve opened on lowering to the tank must control and combine the control oil flow from the other check valve and the working flow and adjust the load pressure on the opening side of a sampling valve, the lowering control becomes difficult at low lowering speed and low load or no-load lifting cylinder.

Die aus EP 546 300 A1 und DE 41 40 408 A1 bekannte und lastkompensierende elektrohydraulische Steuervorrichtung eines Hubzylinders enthält in einer hydraulischen Gleichrichterschaltung eine geschlossene Vollbrücke, die an einer Vollbrücken-Ecke an die Versorgungsleitung und an die Tankleitung angeschlossen ist. In der Tankleitung ist ein Proportionaldruckventil angeordnet. Von der Diagonale zweigen Lastdruckleitungen zu hydroelektrischen Druckwandlern ab, die an eine elektronische Steuerung des 2/2-Wege-Proportionalregelventils angeschlossen sind. Die Druckwandler, die Steuerung und das 2/2-Wege-Proportionalregelventil sind Teile des elektronisch aufwendig ausgebildeten Lastkompensationssystems beim Heben und Senken. Die Versorgungsleitung führt zu weiteren Hydroverbrauchem. Die Senkfunktion wird bei bestromtem 2/2-Wege-Proportionalregelventil und bestromtem Proportionaldruckventil in der Tankleitung gesteuert, wobei bauartbedingt das Proportionaldruckventil in der Tankleitung einen Staudruck aufbaut, der bei mit geringer Last oder sogar lastfrei zu senkendem Hydroverbraucher die eingestellte Geschwindigkeit unerwünscht vermindert. Eine feinfühlige Steuerung gestaltet sich schwierig, da das Proportionaldruckventil in der Tankleitung den gesamten Arbeitsstrom verarbeiten und gleichzeitig ein Drucksignal für die Senkfunktion erzeugen muss.From EP 546 300 A1 and DE 41 40 408 A1 known and load-compensating electro-hydraulic control device of a lifting cylinder includes in a hydraulic rectifier circuit a closed full bridge, which is connected to a full-bridge corner to the supply line and to the tank line. In the tank line a proportional pressure valve is arranged. From the diagonal branch load pressure lines to hydroelectric pressure transducers, which are connected to an electronic control of the 2/2-way proportional control valve. The pressure transducers, the control and the 2/2-way proportional control valve are parts of the electronically complex trained load compensation system when lifting and lowering. The supply line leads to further Hydroverbrauchem. The lowering function is controlled in the current-fed 2/2-way proportional control valve and energized proportional pressure valve in the tank line, the design of the proportional pressure valve in the tank line builds up a dynamic pressure at low load or even load-free to lowering hydraulic consumers set speed undesirable reduced. Sensitive control is difficult because the proportional pressure valve in the tank line must handle the entire working flow and at the same time generate a pressure signal for the lowering function.

Der Erfindung liegt die Aufgabe zugrunde, eine elektrohydraulische Steuervorrichtung der eingangs genannten Art zu schaffen, die baulich und funktionell einfach ist und eine feinfühlige Geschwindigkeitssteuerung auch beim Senken ermöglicht.The invention has for its object to provide an electro-hydraulic control device of the type mentioned, which is structurally and functionally simple and allows a sensitive speed control even when lowering.

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

Da die Brücke einseitig offen ausgebildet ist, beeinflusst der Zulaufförderstrom das zur Tankleitung öffnende Rückschlagventil nicht. Dieses Rückschlagventil ist nur dem vernachlässigbaren Druck in der Tankleitung ausgesetzt und kann als einziges der Rückschlagventile der Gleichrichterschaltung entsperrbar ausgelegt sein. Es lässt sich eine feinfühlige Geschwindigkeitssteuerung des Hydroverbrauchers beim Heben und beim Senken durchführen, selbst wenn rasch zwischen Heben und Senken hin- und hergeschaltet bzw. eine geringe Senkgeschwindigkeit gefahren wird. Das rein hydraulische Lastkompensationssystem ist baulich einfach, kostengünstig und funktionssicher und kann mit anderen aus derselben Pumpe versorgten Verbrauchersteuerungen kombiniert werden. Das 2/2-Wege-Proportionalregelventil ist baulich einfach, da es nur die jeweilige Geschwindigkeit einzustellen und den eingestellten Geschwindigkeitswert einzuregeln braucht, ohne auf die Lastkompensation einzuwirken. Der Zulaufregler misst den Förderstrom für den Hydroverbraucher lastkompensiert zu und je nach Bedarf. Da beim Senken das Druckmittel über das zur Tankleitung öffnende Rückschlagventil direkt in die Tankleitung abfließt und das Rückschlagventil bauartbedingt kaum Staudruck erzeugt, lässt sich auch bei geringer Last oder lastfreiem Hydroverbraucher jede gewünschte und gegebenenfalls sogar die maximale Senkgeschwindigkeit exakt fahren. Kern des Konzepts ist es, für die Steuervorrichtung des Hydroverbrauchers den Lastdruck hydraulisch abzugreifen und als hydraulisches Drucksignal für ein rein hydraulisches Lastkompensationssystem bereitzustellen, und dieses Lastdrucksignal nicht nur zur Lastkompensation sondern auch für die Funktion Senken zu benutzen, so dass das 2/2-Wege-Proportional-regelventil nur die Aufgabe zu erfüllen braucht, die Geschwindigkeit einzustellen und zu regeln. In einfachen nicht erfindungsgemäßen Ausführungsformen könnte statt eines Proportionalmagneten sogar ein Schwarz/Weiß-Magnet für das 212-Wege-Regelventil benutzt werden. Zur feinfühligen Senksteuerung ist vorgesehen, dass ein zur Tankleitung öffnendes Rückschlagventil der hydraulischen Gleichrichterschaltung aus der Lastdruckleitung wahlweise zwischen der Sperrstellung und der Durchgangsstellung umsteuerbar ist. Hierfür ist die Lastdruckleitung an ein zwischen einer Hebe-Sperrstellung und einer Senk-Offenstellung umstellbares, zur Tankleitung oder zum Tank öffnendes Magnetventil angeschlossen. Durch Umstellen des Magnetventils in die Senk-Offenstellung wird das Drucksignal zum Aufsteuem des Rückschlagventils erzeugt, das Arbeitsdruckmittel ohne Staudruck in die Tankleitung abströmen lässt. Es ist eine feinfühlige Steuerung möglich, da das Magnetventil nur eine kleine Steuerölmenge zu verarbeiten hat. Das Magnetventil kann deshalb kleinbauend und kostengünstig sein. Das Rückschlagventil kann so durch das Drucksignal in der Lastdruckleitung auf- und zugesteuert werden. So lässt sich beispielsweise durch ein durch eine Absenkung des Lastdrucks in der Lastdruckleitung erzeugtes Lastdrucksignal der Senkvorgang einleiten.Since the bridge is designed to be open on one side, the feed flow does not affect the non-return valve opening to the tank line. This check valve is exposed only to the negligible pressure in the tank line and can be designed as the only one of the check valves of the rectifier circuit unlockable. It is possible to perform a sensitive speed control of the hydraulic consumer when lifting and lowering, even if quickly switched between lifting and lowering back and forth or a low lowering speed is driven. The purely hydraulic load compensation system is structurally simple, cost-effective and reliable, and can be combined with other consumer-supplied controls from the same pump. The 2/2-way proportional control valve is structurally simple, since it only needs to set the respective speed and regulate the set speed value, without affecting the load compensation. The inlet regulator measures the flow rate for the hydraulic consumer load-compensated to and as needed. Since when lowering the pressure medium via the check valve opening to the tank line flows directly into the tank line and the check valve design causes hardly any back pressure, even with low load or load-free hydro consumer can drive any desired and possibly even the maximum lowering speed exactly. The core of the concept is to hydraulically tap the load pressure for the control device of the hydraulic consumer and provide it as a hydraulic pressure signal for a purely hydraulic load compensation system, and to use this load pressure signal not only for load compensation but also for the function sinks, so that the 2/2-way -Proportional control valve only needs to fulfill the task of adjusting and regulating the speed. In simple embodiments not according to the invention, instead of a proportional magnet could even a black and white magnet can be used for the 212-way control valve. For sensitive lowering control is provided that a valve opening to the tank check valve of the hydraulic rectifier circuit from the load pressure line is selectively reversible between the blocking position and the passage position. For this purpose, the load pressure line is connected to a switchable between a lifting-blocking position and a lowering open position, to the tank line or tank opening solenoid valve. By switching the solenoid valve in the lowering open position, the pressure signal is generated to aufsteuem the check valve, the working pressure can flow off without back pressure in the tank line. It is a sensitive control possible because the solenoid valve has to process only a small amount of control oil. The solenoid valve can therefore be physically small and inexpensive. The check valve can be opened and closed by the pressure signal in the load pressure line. Thus, for example, by a generated by a reduction of the load pressure in the load pressure line load pressure signal, the lowering process can be initiated.

Das Magnetventil ist vorzugsweise ein 2/2-Wege-Schwarz/Weiß-Magnetventil in Sitzventilbauweise, das in der Hebe-Sperrstellung Leckagefreiheit garantiert.The solenoid valve is preferably a 2/2-way solenoid valve in poppet design, which guarantees freedom from leaks in the lifting-blocking position.

Bei einer bevorzugten Ausführungsform weist das Rückschlagventil einen zwischen der Tankleitung und einem Ast der Brücke angeordneten Ventilsitz auf, dem ein durch einen Steuerkolben zwischen einer Schließstellung und einer Offenstellung umstellbares Schließglied zugeordnet ist. Der Steuerkolben wird aus der Lastdruckleitung beaufschlagt und über das Magnetventil entlastet. Auf diese Weise lassen sich die Öffnungs- und Schließbewegungen des Rückschlagventils sehr sauber steuern.In a preferred embodiment, the check valve has a arranged between the tank line and a branch of the bridge valve seat, which is associated with a switchable by a control piston between a closed position and an open position closing member. The control piston is acted upon from the load pressure line and relieved via the solenoid valve. In this way, the opening and closing movements of the check valve can be controlled very clean.

Bei einer bevorzugten Ausführungsform mit mehreren, an denselben Zulaufregler angeschlossenen, gegebenenfalls individuell betätigbaren, Hydroverbrauchem ist jedem ein in der Diagonale einer hydraulischen Gleichrichterschaltung platziertes 2/2-Wege-Proportionalregelventil zugeordnet. Die Lastdruckleitungen der mehreren Hydroverbraucher werden im hydraulischen Lastkompensationssystem zusammengefasst, so dass der Zulaufregler auf den jeweils höchsten Lastdruck anspricht. Ein einziges Magnetventil zwischen dem hydraulischen Lastkompensationssystem und der Tankleitung oder dem Tank, genügt, um jeden Hydroverbraucher allein oder alle Hydroverbraucher miteinander beim Senken steuern zu können.In a preferred embodiment with a plurality of, optionally individually operable, Hydroverbrauchem connected to the same inlet regulator, each associated with a placed in the diagonal of a hydraulic rectifier circuit 2/2-way proportional control valve. The load pressure lines of the several hydraulic consumers are combined in the hydraulic load compensation system, so that the inlet regulator responds to the respective highest load pressure. A single solenoid valve between the hydraulic load compensation system and the tank line or the tank, is sufficient to control each hydraulic consumer alone or all the hydraulic consumers with each other when lowering.

Zweckmäßig ist das Magnetventil in einer den Zulaufregler enthaltenden Eingangssteuersektion der Steuervorrichtung angeordnet. Dies Eingangssektion hat damit eine Grundausstattung, die beliebig viele Hydroverbraucher nutzen können.Suitably, the solenoid valve is arranged in an inlet control section containing the input control section of the control device. This input section has thus a basic equipment that can use as many hydro consumers.

Schließlich ist es für eine feinfühlige Regelung beim Senken zweckmäßig, in der Lastdruckleitung zwischen der Diagonale und dem Steuerkolben des Rückschlagventils ein zur Diagonale sperrendes Rückschlagventil und stromab desselben eine Blende anzuordnen.Finally, it is useful for a sensitive control when lowering, in the load pressure line between the diagonal and the control piston of the check valve to a diagonal blocking check valve and downstream of the same to arrange a diaphragm.

Anhand der Zeichnung werden Ausführungsformen des Erfindungsgegenstandes erläutert. Es zeigen:

Fig. 1
ein Blockschaltbild einer elektrohydraulischen Steuervorrichtung für einen Hydroverbraucher,
Fig. 2
elektrohydraulische Steuervorrichtungen für mehrere Hydroverbraucher,
Fig. 3
eine elektrohydraulische Steuervorrichtung als Gesamtkonzept, und
Fig. 4
eine elektrohydraulische Steuervorrichtung, als Gesamtkonzept, in einer alternativen Ausführung für Regenerativbetrieb.
Reference to the drawings, embodiments of the subject invention will be explained. Show it:
Fig. 1
a block diagram of an electro-hydraulic control device for a hydraulic consumer,
Fig. 2
Electrohydraulic control devices for several hydraulic consumers,
Fig. 3
an electro-hydraulic control device as an overall concept, and
Fig. 4
an electro-hydraulic control device, as an overall concept, in an alternative embodiment for regenerative operation.

Die in Fig. 1 gezeigte elektrohydraulische Steuervorrichtung S für einen einseitig gegen Last beaufschlagbaren Hydroverbraucher V3, typischerweise einen Hubzylinder eines Hubstaplers, ist ein baukastenartig einsetzbarer Modul 23 zum Aufbauen einer elektrohydraulischen Steuervorrichtungsanordnung. Der Modul 23 enthält eine Versorgungsleitung 9', eine Tankleitung 11' und eine Lastdruckleitung 10". Die Tankleitung 11' führt zu einem Tank T. Die Versorgungsleitung 9' führt von einer Pumpe 8 durch einen Zulaufregler Z. Die Lastdruckleitung 10" ist an ein hydraulisches Lastkompensationssystem und als Steuerleitung an den Zulaufregler Z angeschlossen. Falls die Pumpe 8 drehzahlgeregelt fördert, könnte die Pumpe 8 die Funktion des Zulaufreglers Z erfüllen.In the Fig. 1 shown electrohydraulic control device S for a cantilevered against load hydraulic consumer V3, typically a lift cylinder of a lift truck, is a modular deployable module 23 for building an electro-hydraulic control device assembly. The module 23 contains a supply line 9 ', a tank line 11' and a load pressure line 10 ". The tank line 11 'leads to a tank T. The supply line 9' leads from a pump 8 through a supply regulator Z. The load pressure line 10" is connected to a hydraulic load compensation system and connected as a control line to the supply controller Z. If the pump 8 promotes speed control, the pump 8 could fulfill the function of the inlet regulator Z.

In dem Modul ist eine hydraulische Gleichrichterschaltung 35 mit einer aus drei Ästen 36, 37, 38 bestehenden, einseitig offenen Brücke und vier Rückschlagventilen 39, 40, 41 und 42 vorgesehen. Der Ast 37 ist mit dem Hydroverbraucher V3 verbunden. Der Ast 36 ist über das Rückschlagventil 39 an die Versorgungsleitung 9' angeschlossen. Der Ast 38 ist über das Rückschlagventil 42 an die Tankleitung 11' angeschlossen. In der Brücke ist eine Diagonale 43 vorgesehen, in der ein 2/2-Wege-Proportionalregelventil 25' (z.B. in Sitzventilbauweise) mit einem Proportionalmagneten m2 enthalten ist. Gegebenenfalls wird sogar anstelle des Proportionalmagneten m2 ein Schwarz/Weiß-Magnet verwendet.In the module, a hydraulic rectifier circuit 35 is provided with a three branches 36, 37, 38, one-sided open bridge and four check valves 39, 40, 41 and 42. The branch 37 is connected to the hydraulic consumer V3. The branch 36 is connected via the check valve 39 to the supply line 9 '. The branch 38 is connected via the check valve 42 to the tank line 11 '. In the bridge, a diagonal 43 is provided in which a 2/2-way proportional control valve 25 '(e.g., in poppet style) with a proportional solenoid m2 is included. If necessary, a black-and-white magnet is used instead of the proportional magnet m2.

Das 2/2-Wege-Proportionalregelventil 25' dient zum Einstellen und Regeln der Bewegungsgeschwindigkeit des Hydroverbrauchers V3 sowohl beim Heben als auch beim Senken, und auch zum Halten der Last des Hydroverbrauchers V3.The 2/2-way proportional control valve 25 'is for setting and controlling the moving speed of the hydraulic consumer V3 both in lifting and lowering, and also for holding the load of the hydraulic consumer V3.

Stromab des 2/2-Wege-Proportionalregelventils 25' zweigt eine Lastdruckleitung 44 zur Lastdruckleitung 10" ab. In der Lastdruckleitung 44 sind ein zur Lastdruckleitung 10" öffnendes Rückschlagventil 45 und stromab desselben eine Blende 46 vorgesehen. Ferner ist zwischen der Lastdruckleitung 44 und der Tankleitung 11' ein durch einen Magneten m3 aus der gezeigten Absperrstellung in eine Durchgangsstellung schaltbares Magnetventil 34 vorgesehen, vorzugsweise ein 2/2-Wege-Magnetventil.Downstream of the 2/2-way proportional control valve 25 'branches off a load pressure line 44 to the load pressure line 10 "In the load pressure line 44, a check valve 45 to the load pressure line 10" and downstream of the same a diaphragm 46 is provided. Further, between the load pressure line 44 and the tank line 11 'is provided by a magnet m3 from the shut-off position shown in a passage position switchable solenoid valve 34, preferably a 2/2-way solenoid valve.

Das Rückschlagventil 42 ist durch den Lastdruck in der Lastdruckleitung 44 in die gezeigten Hebe-Sperrstellung bringbar und haltbar und durch Entlasten der Lastdruckleitung 44 in seine Senk-Offenstellung umschaltbar. Eine Ausführungsform des entsperrbaren Rückschlagventils 42 ist angedeutet. Das Rückschlagventil 42 enthält zwischen dem Ast 38 und der Tankleitung 11' einen Ventilsitz 47. Mit dem Ventilsitz 47 kooperiert ein Schließglied 48, das mit einem Steuerkolben 49 funktionell gekoppelt ist, der durch eine Feder 50 und durch den Druck in der Lastdruckleitung 44 beaufschlagbar ist. Die Beaufschlagungsfläche des Steuerkolbens 49 ist z.B. größer als die Beaufschlagungsfläche des Schließgliedes 48.The check valve 42 can be brought and retained by the load pressure in the load pressure line 44 in the lifting-blocking position shown and by relieving the load pressure line 44 in its lowering open position. An embodiment of the pilot-operated check valve 42 is indicated. The check valve 42 includes between the branch 38 and the tank line 11 'a valve seat 47. With the valve seat 47 cooperates a closing member 48 which is operatively coupled to a control piston 49, by a spring 50 and by the pressure in the load pressure line 44th can be acted upon. The loading surface of the control piston 49 is, for example, larger than the loading surface of the closing member 48.

Funktion:Function:

In der in Fig. 1 gezeigten Schaltstellung wird die Last des Hydroverbrauchers V3 von den Rückschlagventilen 39, 41 und dem in Sitzventilbauweise ausgebildeten 2/2-Wege-Proportionalregelventil gehalten. Der Proportionalmagnet m2 und der Magnet m3 sind stromlos.In the in Fig. 1 shown switching position, the load of the hydraulic consumer V3 is held by the check valves 39, 41 and formed in the poppet design 2/2-way proportional control valve. The proportional magnet m2 and the magnet m3 are de-energized.

Zum Heben wird bei laufender Pumpe 8 der Proportionalmagnet m2 entsprechend der gewünschten Geschwindigkeit bestromt. Das Druckmittel strömt über das Rückschlagventil 39, den Ast 36, das 2/2-Wege-Proportionalregelventil 25' und das Rückschlagventil 41 zum Hydroverbraucher V3. Der Magnet m3 ist nicht bestromt. Das Rückschlagventil 42 wird vom Lastdruck in der gezeigten Hebe-Sperr-Stellung gehalten.For lifting, the proportional magnet m2 is energized according to the desired speed while the pump 8 is running. The pressure medium flows via the check valve 39, the branch 36, the 2/2-way proportional control valve 25 'and the check valve 41 to the hydraulic consumer V3. The magnet m3 is not energized. The check valve 42 is held by the load pressure in the lift-lock position shown.

Zum Senken wird am Proportionalmagneten m2 die gewünschte Geschwindigkeit eingestellt, und wird das Magnetventil 34 durch Bestromen des Magneten m3 in die Senk-Offenstellung umgeschaltet. Die Lastdruckleitung 44 wird zumindest stromab der Blende 46 druckentlastet. Die Druckentlastung (Drucksignal) führt über den im Ast 38 herrschenden Lastdruck zum Öffnen des Rückschlagventils 42. Das Arbeitsdruckmittel strömt direkt in die Tankleitung 11'. Da ggfs. auch in der Lastdruckleitung 10" eine Druckabsenkung eintritt, liefert der Zulaufregler Z keinen Förderstrom. Gegebenenfalls wird sogar die Pumpe 8 abgeschaltet.For lowering the desired speed is set on the proportional magnet m2, and the solenoid valve 34 is switched by energizing the magnet m3 in the lowering open position. The load pressure line 44 is depressurized at least downstream of the orifice 46. The pressure relief (pressure signal) leads via the prevailing in the branch 38 load pressure to open the check valve 42. The working pressure fluid flows directly into the tank line 11 '. Since, if necessary, a pressure reduction also occurs in the load pressure line 10 ", the inlet regulator Z does not deliver any flow.

Fig. 2 verdeutlicht eine elektrohydraulische Steuervorrichtungsanordnung für mehrere einseitig gegen Last beaufschlagbare Hydroverbraucher V2, V3, aus Steuermodulen 22, 23. Der Aufbau jedes Moduls 22, 23 entspricht weitgehend dem in Fig. 1 gezeigten. Die Rückschlagventile 42 sind mit einer an die Lastdruckleitung 44 angeschlossenen Entsperrleitung 44' symbolisch dargestellt. Jeder Modul 22, 23 enthält ein 2/2-Wege-Proportionalregelventil 25, 25' mit Proportionalmagneten m1 und m2. Die Hydroverbraucher V2, V3 können gemeinsam unterschiedlich schnell oder einzeln sowohl zum Heben als auch zum Senken betätigt werden. Für die Senkfunktion könnte das Magnetventil 34 in einem der Module 22, 23 untergebracht sein, wie in Fig. 1, oder ist wie gezeigt, das Magnetventil 34 zwischen der Lastdruckleitung 10" und dem Tank T gemeinsam für alle Module und getrennt von diesen angeordnet. Die Funktion ist wie anhand Fig. 1 beschrieben. Fig. 2 illustrates an electro-hydraulic control device arrangement for several unilaterally acted upon load hydraulic consumers V2, V3, from control modules 22, 23. The structure of each module 22, 23 largely corresponds to the in Fig. 1 shown. The check valves 42 are shown symbolically with an unlocking line 44 'connected to the load pressure line 44. Each module 22, 23 contains a 2/2-way proportional control valve 25, 25 'with proportional magnets m1 and m2. The hydraulic consumers V2, V3 can work together at different speeds or individually be operated for lifting and lowering. For the lowering function, the solenoid valve 34 could be housed in one of the modules 22, 23, as in FIG Fig. 1 or, as shown, the solenoid valve 34 is interposed between the load pressure line 10 "and the tank T common to and separate from all the modules Fig. 1 described.

In Fig. 3 wird eine elektrohydraulische Steuervorrichtungsanordnung für einen Hubstapler gezeigt, in die die Module 22, 23 der Fig. 1 und 2 und ein Steuerblockmodul 21 und eine Eingangssektion E eingegliedert sind. Die Pumpe 8 wird von einem Elektromotor M angetrieben. Die Eingangssektion E, die als Blockmodul 1 ausgebildet ist, ist mit dem Steuerblockmodul 21 für einen Hydroverbraucher V1 verbunden (doppelseitig beaufschlagbarer Hydroverbraucher), der über ein Mehrwege-Proportional-Schieberventil 24 mit zwei Proportionalmagneten m4 und m5 betätigbar ist. Der Hydroverbraucher V1 hat in der Steuervorrichtungsanordnung Priorität gegenüber den Hydroverbrauchem V2, V3.In Fig. 3 For example, there is shown an electro-hydraulic control device arrangement for a lift truck in which the modules 22, 23 of the Fig. 1 and 2 and a control block module 21 and an input section E are incorporated. The pump 8 is driven by an electric motor M. The input section E, which is designed as a block module 1, is connected to the control block module 21 for a hydraulic 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 hydraulic consumer V1 has priority over the hydraulic consumption V2, V3 in the control device arrangement.

Die Module 22, 23 für die Hydroverbraucher V2, V3 sind an der anderen Seite der Eingangssektion montiert, wobei die Lastdruckleitung 10", die Versorgungsleitung 9' und die Tankleitung 11' bis in die Eingangssektion E1 geführt sind. Das Lastkompensationssystem L in der Eingangssektion E ist beispielsweise über einen Anschluss 4' im Blockmodul 1 mit der Lastdruckleitung 10" verknüpft.The hydraulic consumption modules V2, V3 are mounted on the other side of the inlet section, with the load pressure line 10 ", the supply line 9 'and the tank line 11' being led into the input section E 1. The load compensation system L in the input section E is for example connected via a connection 4 'in the block module 1 with the load pressure line 10 ".

In der Eingangssektion E sind zwei Lastdruckleitungen 10, 10' vorgesehen, wobei die Lastdruckleitung 10 den Lastdruck des Hydroverbrauchers V1 erhält, und die Lastdruckleitung 10' den Lastdruck aus der Lastdruckleitung 10". Von den Lastdruckleitungen 10, 10' zweigen Steuerleitungen 26, 27 ab, die über eine Wechselventilanordnung 16' aus zwei Rückschlagventilen und eine Verbindungsleitung 28 miteinander verbunden sind. Von der Verbindungsleitung 28 zweigt eine Steuerleitung 31 zu einer Ablassleitung 20' ab, in der für alle Hydroverbraucher ein Druckbegrenzungsventil 33 für den Systemdruck im Lastkompensationssystem L vorgesehen ist. Zwischen den Steuerleitungen 26, 27 erstreckt sich eine weitere Verbindungsleitung 29, in der zwei Blenden 30 platziert sind, zwischen denen eine Steuerleitung 33 zur Ablassleitung 20' abzweigt. Das anhand der Fig. 1 und 2 erläuterte Magnetventil 34 ist hier zwischen der Steuerleitung 26 und der Ablassleitung 20' in die Eingangssektion E integriert.In the input section E two load pressure lines 10, 10 'are provided, the load pressure line 10 receives the load pressure of the hydraulic consumer V1, and the load pressure line 10', the load pressure from the load pressure line 10 "from the load pressure lines 10, 10 'branch off control lines 26, 27 , which are connected to each other via a shuttle valve assembly 16 'of two check valves and a connecting line 28. From the connecting line 28 branches off a control line 31 to a discharge line 20', in which a pressure relief valve 33 is provided for the system pressure in the load compensation system L for all hydraulic consumers. Between the control lines 26, 27 extends a further connecting line 29, in which two apertures 30 are placed, between which a control line 33 to the outlet line 20 ' branches. That on the basis of Fig. 1 and 2 explained solenoid valve 34 is here integrated between the control line 26 and the drain line 20 'in the input section E.

Von der Pumpe 8 führt eine Pumpenleitung 12 zu einer Vorspann-Zweiwege-Druckwaage W1 In derAblassleitung 20' ist eine Zweiwege-Umlauf-Druckwaage W2 enthalten. Die Lastdruckleitung 10 ist an die Schließstellseite der Zweiwege-Vorspann-Druckwaage W1 angeschlossen, während deren Öffnungsstellseite mit aus der Pumpenleitung 12 abgeleitetem Steuerdruck beaufschlagt wird. Die Schließstellseite der Zweiwege-Umlauf-Druckwaage W2 ist an die Lastdruckleitung 10' angeschlossen, während die Öffnungsstellseite mit Vorsteuerdruck aus der Ablassleitung 20' beaufschlagt wird. Zwischen den Druckwaagen W1, W2 zweigt von der Ablassleitung 20' eine Versorgungsleitung 9 ab, die zu der Versorgungsleitung 9' der Module 22, 23 führt. Die beiden Druckwaagen W1, W2 arbeiten als Zulaufregler Z zumindest für die Hydroverbraucher V2, V3, wobei der Hydroverbraucher V1 stets Priorität hat.From the pump 8, a pump line 12 leads to a bias two-way pressure balance W1. The drain line 20 'includes a two-way recirculation pressure balance W2. The load pressure line 10 is connected to the closing side of the two-way bias pressure compensator W1, while the opening control side is applied with derived from the pump line 12 control pressure. The closing side of the two-way recirculation pressure compensator W2 is connected to the load pressure line 10 ', while the opening adjustment side with pilot pressure from the discharge line 20' is applied. Between the pressure compensators W1, W2 branches from the discharge line 20 'from a supply line 9, which leads to the supply line 9' of the modules 22, 23. The two pressure compensators W1, W2 operate as an inlet regulator Z at least for the hydraulic consumers V2, V3, the hydraulic consumer V1 always having priority.

Die in Fig. 4 gezeigte elektrohydraulische Steuervorrichtungsanordnung S unterscheidet sich von der von Fig. 3 durch eine integrierte Regenerativfunktion. Mit beim Senken jedes Hydroverbrauchers V2, V3 verdrängtem Arbeitsdruckmittel kann elektrische Energie erzeugt werden. Für diese Funktion sind die Eingangssektion E und die Module 22, 23 modifiziert. Die Pumpe 8' ist eine umkehrbare Pumpe, die um Umkehrbetrieb als Hydromotor arbeitet und einen als Generator arbeitenden Elektromotor MG treibt. In der Eingangssektion E ist ein 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 gesperrt. Das Magnetventil 34 von Fig. 3 fehlt, oder ist deaktiviert. In jedem Modul 22 und 23 ist das Rückschlagventil 42, das zur Tankleitung 11' öffnet, von der Lastdruckleitung 44 getrennt (ggfs. gesperrte Verbindung oder einfaches Rückschlagventil 42).In the Fig. 4 shown electro-hydraulic control device arrangement S differs from that of Fig. 3 through an integrated regenerative function. Electrical energy can be generated with the working pressure medium displaced when each hydraulic consumer V2, V3 is lowered. For this function, the input section E and the modules 22, 23 are modified. The pump 8 'is a reversible pump, which operates as a hydraulic motor to reverse operation and drives a working as a generator electric motor MG. In the inlet section E, a tank line connection 5 'is connected via a tank line 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 the connection is blocked Fig. 3 is missing, or is disabled. In each module 22 and 23, the check valve 42, which opens to the tank line 11 ', is disconnected from the load pressure line 44 (possibly a locked connection or simple check valve 42).

Beim Senken der Hydroverbraucher V2 und/oder V3 wird die Pumpe 8' auf Umkehrbetrieb geschaltet. Die Proportionalmagneten m1 bzw. m2 sind entsprechend bestromt. Durch den über die Pumpe 8' erzeugten Drucksenkimpuls öffnet das Rückschlagventil 42 und das Arbeitsdruckmittel strömt durch die Pumpe 8' zum Tank T, wobei, zumindest innerhalb eines vorbestimmten Förderstrom- und/oder Druckbereichs, der Motor MG Strom erzeugt. Bei geringer Last oder in lastfreiem Zustand des Hydroverbrauchers V2 und/oder V3 wird gegebenenfalls die Pumpe 8' im Leerlauf betrieben, um die eingestellte Geschwindigkeit genau erzielen zu lassen.When lowering the hydraulic consumers V2 and / or V3, the pump 8 'is switched to reverse operation. The proportional magnets m1 and m2 are energized accordingly. By the pressure lowering pulse generated by the pump 8 'opens the check valve 42 and the working pressure fluid flows through the pump 8' to the tank T, wherein, at least within a predetermined flow and / or pressure range, the motor MG generates power. At low load or in load-free state of the hydraulic consumer V2 and / or V3, the pump 8 'is optionally operated at idle to achieve the set speed accurately.

Claims (6)

  1. Electro-hydraulic control device for at least one hydraulic consumer (V2, V3) which can be actuated on one side towards load, in particular for stacker trucks, with a supply line (9'), which can be fed from a pump (8, 8'), a tank line (11'), and a hydraulic rectifier circuit (35), which is arranged between the supply line (9') or the tank line (11') and the hydraulic consumer (V3, V2) and forms a bridge containing four nonreturn valves (39 to 42) and a diagonal (43), in which diagonal (43) a 2/2-way proportional control valve (25, 25') is arranged for the purpose of controlling the lifting and lowering speed of the hydraulic consumer (V2, V3), and with a load pressure line (44), which branches off in the rectifier circuit downstream of the 2/2-way proportional control valve (25, 25'), for a load compensation system (L), the bridge being designed to be open on one side and to have three branches (36, 37, 38), of which one branch (36) is connected to the supply line (9') and another branch (38) is connected to the tank line (11'), characterized in that the load pressure line (44) is connected to a solenoid valve (34), which can be moved between a lift blocking position and a lowering open position and opens towards the tank line (11'), in that one nonreturn valve (42), which opens towards the tank line (11'), of the nonreturn valves (39 to 42) in the hydraulic rectifier circuit (35) can optionally be controlled from the load pressure line (44) so as to move between its blocking position and its passage position, and in that the load pressure line (44) can be integrated in a hydraulic load compensation system (L) and can be connected to a supply-line feed controller (Z).
  2. Electro-hydraulic control apparatus according to Claim 1, characterized in that the solenoid valve (34) is a 2/2-way black/white solenoid valve.
  3. Electro-hydraulic control apparatus according to Claim 1, characterized in that the nonreturn valve (42) has a valve seat (47), which is arranged between the tank line (11') and the other branch (38), with a closing element (48), which can be moved by a piston valve (49) between a closed position and a passage position, being associated with said valve seat (47), and in that the piston valve (49) can be acted upon in the closing direction of the closing element (48) from the load pressure line (44) and can be relieved of load in the opening direction via the solenoid valve (34).
  4. Electro-hydraulic control apparatus according to at least one of the preceding claims, characterized in that, in the case of a plurality of individually actuable hydraulic consumers (V2, V3), which are connected to the same supply-line feed controller (Z), a 2/2-way proportional control valve (25, 25') is associated with each hydraulic consumer in in each case one hydraulic rectifier circuit (35), in that the load pressure lines (44) are combined in the hydraulic load compensation system (L), and in that the solenoid valve (34) which is common to all of the hydraulic consumers is provided between the load compensation system (L) and the tank (T).
  5. Electro-hydraulic control apparatus according to Claim 1, characterized in that the solenoid valve (34) is arranged in an input control section (E) containing the supply-line feed controller (Z).
  6. Electro-hydraulic control apparatus according to Claim 3, characterized in that a nonreturn valve (45), which blocks in the direction towards the diagonal, and, downstream thereof, a diaphragm (46) are provided between the diagonal (43) and the piston valve (49) in the load pressure line (44).
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DE3103745A1 (en) 1981-02-04 1982-09-02 Sperry-Vickers Zweigniederlassung der Sperry GmbH, 6380 Bad Homburg HYDRAULIC LIFTING DEVICE
DE4140409A1 (en) 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De ELECTROHYDRAULIC CONTROL DEVICE
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

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EP1635070A1 (en) 2006-03-15
EP1635070B8 (en) 2009-04-08
DE502005006256D1 (en) 2009-01-29
DE202004014029U1 (en) 2006-01-12

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