EP3037678A1 - Lifting module - Google Patents

Lifting module Download PDF

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Publication number
EP3037678A1
EP3037678A1 EP14200055.3A EP14200055A EP3037678A1 EP 3037678 A1 EP3037678 A1 EP 3037678A1 EP 14200055 A EP14200055 A EP 14200055A EP 3037678 A1 EP3037678 A1 EP 3037678A1
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EP
European Patent Office
Prior art keywords
pressure
valve
control
line
lifting module
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
EP14200055.3A
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German (de)
French (fr)
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EP3037678B1 (en
Inventor
Recep Macit
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Hawe Hydraulik SE
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Hawe Hydraulik SE
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Priority to EP14200055.3A priority Critical patent/EP3037678B1/en
Publication of EP3037678A1 publication Critical patent/EP3037678A1/en
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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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/005—Leakage; Spillage; Hose burst
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control
    • F15B2211/5756—Pilot pressure control for opening a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/855—Testing of fluid pressure systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/863—Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8636—Circuit failure, e.g. valve or hose failure

Definitions

  • the invention relates to a lifting module specified in the preamble of claim type.
  • a pipe break valve is installed in the hydraulic consumer, which acts as a lowering brake, if a line or pipe or hose should break as a connection from the lifting module to the hydraulic consumer.
  • the burst break valve is designed for a higher maximum lowering speed of the hydraulic consumer, than the maximum adjustable with the two-way flow controller and the proportional pressure control valve and independent of the load controlled lowering speed.
  • Hubmodule there are requirements, eg. B. by users or the Technical Inspection Association to be able to check the proper function of the pipe break valve in the assembled state of the lifting module as needed.
  • the invention has for its object to improve a lifting module of the type mentioned in that combined with the hydraulic consumer pipe break valve in the assembled state of the lifting module can be checked at any time for proper operation.
  • the two-way flow regulator associated pipe rupture valve tester allows also in the assembled state of the lifting module and at any time a check of the proper operation of the pipe rupture valve, in which when using the rupture valve tester such a high lowering speed (volume flow to the tank) is set that the pipe break valve is made to respond. When not operating the pipe burst valve tester this does not affect the control of the hydraulic consumer.
  • the burst breaker valve tester is a stopcock which can be actuated between a free passage and a shutoff position, either manually and / or electrically, e.g. B. via a magnet, and the previously held in the shut-off on a control side of the pressure balance of the two-way flow control pressure holds or locks, so that the pressure balance remains in the fully open position and thus no longer active on the proportional pressure control valve for lowering set pressure difference keeps constant.
  • the pressure compensator is designed so that it discharges a larger volume flow to the tank in the fully open position than the volume flow at which the burst valve responds.
  • the pressure compensator of the two-way flow regulator is acted upon on the supply side of a branched from the Senkstrang upstream of the proportional pressure control valve first control line and the Aufwinseite parallel to a control spring from a branch line between the proportional pressure control valve and the pressure compensator second control line ,
  • the stopcock of the pipe break valve tester is arranged in the second control line, so that it locks control pressure after its actuation in the control position and holds the pressure compensator in the open switching position.
  • a magnet-actuated 4/2 safety valve is arranged in the second control line and in a parallel discharge line from a load pressure signal circuit to a tank line.
  • This safety valve is energized during operation of the lifting module in each case when energizing a proportional pressure control valve and held in a switching position in which shut off the drain line to the tank and the second control line are continuous.
  • the stopcock of the pipe break valve tester is located between the 4/2-way safety valve and the control side of the pressure compensator to lock in the case of a test applied by the safety valve on the control side of the pressure compensator control pressure and, so to speak, to make the open pressure compensator inoperative.
  • the pipe break valve is responsive to a higher lowering speed or higher flow rate of the hydraulic consumer, as the maximum via the two-way flow regulator with properly working pressure compensator adjustable lowering speed of the hydraulic consumer.
  • the pressure source is a variable pump, which is Herbertregelbar to minimum promotion or zero promotion (CC function, Closed Center) is the main line of the lifting module to the lifting strand on the side of the pressure source separated from the tank line.
  • CC function Closed Center
  • the main line which runs from the pressure source to the hoist strand, connected via a recirculating pressure compensator to the tank line to the flow of the constant pump to the tank with dissipate as small as possible throttle losses when no load is removed.
  • the circulation pressure compensator is acted upon by a spring on its closing control side and by a load pressure signal circuit fed downstream of the proportional pressure regulating valve on the lifting line, while control pressure is applied to the control side of the pressure compensator from the main line.
  • the in Fig. 1 Stitch-point shown lifting module H is intended for installation in a material handling vehicle (not shown) and pre-assembled or installed in an industrial truck, z. B. to one here designed as a lifting cylinder on one side, for example, to be acted upon by a load hydraulic consumers V to control.
  • the lifting module H can be combined in block construction with other modules that can control further hydraulic consumers, and share a main line 10 and a tank line 11 (not shown).
  • the lifting module H is arranged between a pressure source P (constant pump or variable displacement pump) and the hydraulic consumer V, where it is connected to the hydraulic consumer V via a working line 2 in the form of a pipe, hose or a line.
  • a pressure source P constant pump or variable displacement pump
  • the lifting module H is designed with an OC function (Open Center), ie the pressure source P is a constant-displacement pump.
  • the lifting module can be designed for a CC function (closed center), for which purpose the in Fig. 1 Some of the components shown are removed or not installed (will be explained later).
  • the CC function the pressure source P is a variable displacement pump that can be regulated between maximum flow and minimum or zero flow.
  • the hydraulic consumer V is a lifting cylinder 1 which can be acted upon on one side and which is connected to the working line 2 on the side of its piston bottom surface via a pipe break valve 3.
  • the pipe break valve 3 is designed in the manner of a so-called lowering brake. Specifically, this is e.g. a 2/2-way valve, which is held by a spring 7 in the shown, possibly slightly throttling passage position, and in the closing direction via a pilot line 5 from the side of the hydraulic consumer and in Aufwinides via a pilot line 6 from the line 2 parallel to the spring. 7 is charged.
  • a strong discharge throttle 8 parallel to a blocking in the flow direction from the lifting cylinder 1 check valve 9, so that even under load of the hydraulic consumer V can retract only with a certain lowering speed.
  • the broken pipe valve 3 is responsive to a pressure difference, for example, in the event of a pipe break between the control lines 5, 6, as soon as the pressure difference is able to overcome the force of the spring 7, and then assumes the controlled position, in which the load pressure is maintained at the check valve 9 and the throttle 8 limits the predetermined lowering speed.
  • a in the lifting module H connected to the pressure source P main line 10 branches into a branch to a hoisting line 20, and in a branch 14 to a circulating pressure compensator 12, said branch 14 with a tank line 11 is connectable.
  • the circulating pressure compensator 12 is held by a spring 17 in the blocking position shown, is acted parallel to the spring 17 from a load pressure signal circuit 18 which is connected for example in a node 19 to the lifting strand 20, and via a drain control line 18th 'is connected to the tank line 11.
  • the circulation pressure compensator 12 is acted upon from one of the main line 10 and its branch 14 branching control line.
  • the load pressure signal circuit 18 is connected to the supply side 16 of the circulation pressure compensator 12. Between the load pressure signal circuit 18 and the tank line 11, a system pressure limiting valve 13 is further arranged.
  • a proportional pressure control valve 21 for lifting control of the hydraulic consumer V is arranged between the node 19 and the main line 10, here a 2/2-way proportional pressure control valve 21 with a proportional solenoid, a spring and a hydraulic pilot.
  • a check valve 22 is arranged, which blocks in the flow direction to the proportional pressure control valve 21.
  • the working line 2 is connected. From the node 23, a drain line 24 leads to the tank line 11.
  • the drain line 24 includes a proportional pressure control valve 26, for example in poppet design, which may be identical to the proportional pressure control valve 21, and by a proportional solenoid 27 against spring force and, for example, by means of hydraulic pilot is operable ,
  • the energization of the proportional solenoid 27 determines inter alia, the lowering speed of the hydraulic consumer V, the maximum eg about 0.6 m / s load, even under load and which is influenced by a pressure compensator 28 in the sink train 24.
  • the proportional pressure control valve 26 and the pressure compensator 28 form a two-way current controller 25, with which the lowering speed is regulated independent of the load, as mentioned, except for example, a maximum of 0.6 m / s.
  • a control line 30 is connected, which branches off at a node 29 from the sink train 24 upstream of the proportional pressure control valve 26.
  • a second control line 34 from the control side 32 from where the control spring 33 acts.
  • the lowering of the hydraulic load to be limited in response to the pipe break valve 3 is about 20% higher than the maximum speed to be set with the two-way flow controller 25.
  • a 4/2-way safety valve 36 is disposed in the drain control line 18 'between the load pressure signal circuit 18 and the tank line 11 and in the second control line 34, which is held by a spring in the switching position shown and is to switch by a black and white magnet 37 in the other switching position. Whenever one of the proportional solenoids of the two proportional pressure control valves 21 and 26 is energized, the magnet 37 is also energized, so that during operation of the lifting module, the drain line 18 'shut off and the second control line 38 are continuous.
  • a pipe rupture valve test device T is provided in the second control line 34, here for example a shut-off cock 38 which in the embodiment shown is installed between the safety valve 36 and the rudder 32.
  • the stopcock 38 can be manually or manually and electrically operated (via a magnet 39), between a non-throttling passage position and a shut-off position.
  • the stopcock 38 may be replaced by any other shut-off device that can be switched between a passage position and a shut-off.
  • the pipe breakage valve tester T allows in assembled and ready state of the lifting module H with connected hydraulic consumer V and connected pressure source P a check of the proper function of the pipe break valve 3, which can not be made to respond solely by the two-way current controller 25.
  • the stopcock 38 is brought into the blocking position at full energization of the proportional magnet 27 and the black-and-white magnet 37, so that the prevailing at the Aufberichtseite 32 held pressure or existing in this part of the second control line 34 and on the control side hydraulic medium is locked up.
  • the pressure compensator 28 can therefore no longer regulate, but remains in the fully open position in which the lowering speed of the hydraulic consumer or the pressure difference between the control lines 5, 6 is so high that the pipe break valve 3 switches. Then, the lowering speed of the hydraulic consumer can be controlled, and thus in the reverse order, the proper operation of the pipe break valve. 3
  • the safety valve 36 is an option and may be omitted as appropriate. Then, if necessary, the drain line 18 'is connected to the tank line 11 via a throttle (not shown), and the second control line 34 containing the test device T is continuous from the node 35 to the control side 32.
  • the circulation pressure compensator 12 is removed or not installed, the branch 14 of the main line 10 is shut off, and the up and Zunellquest 15, 16 blocked, as well as the connection to the tank line eleventh

Abstract

In einem Hubmodul (H), mit einem einseitig von einer Druckquelle (P) aus einem Hebenstrang (20) über ein Proportional-Druckregelventil (21) beaufschlagbaren Hydroverbraucher (V), der über einen Senkenstrang (24) mit einem Zweiwege-Stromregler (25) in Senkrichtung verstellbar ist, und mit einem dem Hydroverbraucher (V) zugeordneten, als Senkbremse ausgebildeten Rohrbruchventil (3), ist dem Zweiwege-Stromregler (25) eine wahlweise betätigbare Rohrbruchventil-Prüfvorrichtung (T) zugeordnet.In a lifting module (H), with a one-sided by a pressure source (P) from a hoist strand (20) via a proportional pressure control valve (21) acted upon hydraulic consumers (V) via a drain line (24) with a two-way current controller (25 ) is adjustable in lowering direction, and associated with a hydraulic consumer (V), designed as a lowering pipe break valve (3), the two-way flow regulator (25) is associated with a selectively operable burst breaker valve tester (T).

Description

Die Erfindung betrifft einen Hubmodul der im Oberbegriff des Patentanspruchs angegebenen Art.The invention relates to a lifting module specified in the preamble of claim type.

Bei dem aus EP 1 369 598 B1 bekannten Hubmodul für den Hubzylinder eines Flurförderfahrzeugs ist im Hydroverbraucher ein Rohrbruchventil verbaut, das als Senkbremse fungiert, sofern eine Leitung oder ein Rohr oder ein Schlauch als Verbindung vom Hubmodul zum Hydroverbraucher brechen sollte. Das Rohrbruchventil ist auf eine höhere maximale Senkgeschwindigkeit des Hydroverbrauchers ausgelegt, als die mit dem Zweiwege-Stromregler und dem Proportional-Druckregelventil maximal einstellbare und lastunabhängig geregelte Senkgeschwindigkeit. Für solche Hubmodule gibt es Anforderungen, z. B. von Anwendern oder dem Technischen Überwachungsverein, die ordnungsgemäße Funktion des Rohrbruchventils in zusammengebautem Zustand des Hubmoduls nach Bedarf überprüfen zu können. Dies ist jedoch bei Verwendung des Zweiwege-Stromreglers nicht möglich, da dessen maximale Senkgeschwindigkeit geringer ist als die Senkgeschwindigkeit, auf die das Rohrbruchventil ausgelegt ist, so dass im zusammengebautem Zustand des Hubmoduls das Rohrbruchventil mittels des Zweiwege-Stromreglers nicht zum Ansprechen gebracht werden kann.At the EP 1 369 598 B1 known lifting module for the lifting cylinder of a material handling vehicle a pipe break valve is installed in the hydraulic consumer, which acts as a lowering brake, if a line or pipe or hose should break as a connection from the lifting module to the hydraulic consumer. The burst break valve is designed for a higher maximum lowering speed of the hydraulic consumer, than the maximum adjustable with the two-way flow controller and the proportional pressure control valve and independent of the load controlled lowering speed. For such Hubmodule there are requirements, eg. B. by users or the Technical Inspection Association to be able to check the proper function of the pipe break valve in the assembled state of the lifting module as needed. However, this is not possible when using the two-way current regulator, since its maximum lowering speed is lower than the lowering speed to which the pipe break valve is designed so that in the assembled state of the lifting module the pipe break valve can not be made to respond by means of the two-way flow regulator.

Dies gilt auch für den Hubmodul aus der EP-Anmeldung mit der Anmeldenummer 14 180 521.8 mit älterem Zeitrang, der sich vom Hubmodul der EP 1 369 598 B1 hauptsächlich dadurch unterscheidet, dass zwischen der Druckquelle und der Hauptleitung eine rein hydraulisch und lastdruckabhängig ansprechende Abschaltvorrichtung für den Förderstrom der Druckquelle vorgesehen ist. Ein, wie üblich, am Hydroverbraucher verbautes Rohrbruchventil kann bei zusammengebautem Hubmodul nicht auf ordnungsgemäße Funktion überprüft werden. Ein hier in den Figuren dargestellter Absperrhahn ist ein Notablasshahn und ermöglicht in der Praxis nur eine stark gedrosselte Senkgeschwindigkeit des Hydroverbrauchers.This also applies to the lifting module from the EP application with the application number 14 180 521.8 with older seniority, different from the lifting module of the EP 1 369 598 B1 mainly differs in that between the pressure source and the main line a purely hydraulic and load pressure dependent responsive shut-off device is provided for the flow of the pressure source. A, as usual, installed on the hydraulic consumer pipe break valve can not be checked for proper function with assembled lifting module. A stopcock shown here in the figures is an emergency drain cock and allows in practice only a strongly throttled lowering speed of the hydraulic consumer.

Der Erfindung liegt die Aufgabe zugrunde, einen Hubmodul der eingangs genannten Art dahingehend zu verbessern, dass ein mit dem Hydroverbraucher kombiniertes Rohrbruchventil in zusammengebautem Zustand des Hubmoduls jederzeit auf ordnungsgemäße Funktion überprüft werden kann.The invention has for its object to improve a lifting module of the type mentioned in that combined with the hydraulic consumer pipe break valve in the assembled state of the lifting module can be checked at any time for proper operation.

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

Die dem Zweiwege-Stromregler zugeordnete Rohrbruchventil-Prüfvorrichtung ermöglicht auch in zusammengebautem Zustand des Hubmoduls und jederzeit eine Prüfung der ordnungsgemäßen Funktion des Rohrbruchventils, in dem bei Benutzen der Rohrbruchventil-Prüfvorrichtung eine so hohe Senkgeschwindigkeit (Volumenstrom zum Tank) eingestellt wird, dass das Rohrbruchventil zum Ansprechen gebracht wird. Bei Nichtbetätigen der Rohrbruchventil-Prüfvorrichtung nimmt diese keinen Einfluss auf die Steuerung des Hydroverbrauchers.The two-way flow regulator associated pipe rupture valve tester allows also in the assembled state of the lifting module and at any time a check of the proper operation of the pipe rupture valve, in which when using the rupture valve tester such a high lowering speed (volume flow to the tank) is set that the pipe break valve is made to respond. When not operating the pipe burst valve tester this does not affect the control of the hydraulic consumer.

In einer zweckmäßigen Ausführungsform ist die Rohrbruchventil-Prüfvorrichtung ein Absperrhahn, der sich zwischen einem freien Durchgangs- und einer Absperrstellung betätigen lässt, und zwar entweder manuell oder/und elektrisch, z. B. über einen Magneten, und der in der Absperrstellung zuvor auf eine Aufsteuerseite der Druckwaage des Zweiwege-Stromreglers gebrachten Steuerdruck hält bzw. einsperrt, so dass die Druckwaage in der voll aufgesteuerten Stellung bleibt und somit nicht mehr aktiv die am Proportional-Druckregelventil zum Senken eingestellte Druckdifferenz konstant hält. Die Druckwaage ist so ausgelegt, dass sie in der voll aufgesteuerten Stellung einen größeren Volumenstrom zum Tank ablässt, als den Volumenstrom, bei dem das Rohrbruchventil anspricht.In an expedient embodiment, the burst breaker valve tester is a stopcock which can be actuated between a free passage and a shutoff position, either manually and / or electrically, e.g. B. via a magnet, and the previously held in the shut-off on a control side of the pressure balance of the two-way flow control pressure holds or locks, so that the pressure balance remains in the fully open position and thus no longer active on the proportional pressure control valve for lowering set pressure difference keeps constant. The pressure compensator is designed so that it discharges a larger volume flow to the tank in the fully open position than the volume flow at which the burst valve responds.

Bei einer zweckmäßigen Ausführungsform wird die Druckwaage des Zweiwege-Stromreglers an der Zusteuerseite aus einer vom Senkstrang stromauf des Proportional-Druckregelventils abzweigenden ersten Steuerleitung und an der Aufsteuerseite parallel zu einer Regelfeder aus einer vom Senkstrang zwischen dem Proportional-Druckregelventil und der Druckwaage abzweigenden zweiten Steuerleitung beaufschlagt. Der Absperrhahn der Rohrbruchventil-Prüfvorrichtung ist in der zweiten Steuerleitung angeordnet, so dass er nach seiner Betätigung in die Steuerstellung Steuerdruck einsperrt und die Druckwaage in der aufgesteuerten Schaltstellung hält.In an expedient embodiment, the pressure compensator of the two-way flow regulator is acted upon on the supply side of a branched from the Senkstrang upstream of the proportional pressure control valve first control line and the Aufsteuerseite parallel to a control spring from a branch line between the proportional pressure control valve and the pressure compensator second control line , The stopcock of the pipe break valve tester is arranged in the second control line, so that it locks control pressure after its actuation in the control position and holds the pressure compensator in the open switching position.

Bei einer weiteren zweckmäßigen Ausführungsform ist in der zweiten Steuerleitung und in einer parallelen Ablassleitung von einem Lastdrucksignalkreis zu einer Tankleitung ein magnetbetätigtes 4/2-Sicherheitsventil angeordnet. Dieses Sicherheitsventil wird im Betrieb des Hubmoduls jeweils bei Bestromen eines Proportional-Druckregelventils bestromt und in einer Schaltstellung gehalten, in der die Ablassleitung zum Tank abgesperrt und die zweite Steuerleitung durchgängig sind. Der Absperrhahn der Rohrbruchventil-Prüfvorrichtung ist zwischen dem 4/2-Wege-Sicherheitsventil und der Aufsteuerseite der Druckwaage angeordnet, um im Falle einer Prüfung den vom Sicherheitsventil auf die Aufsteuerseite der Druckwaage aufgebrachten Steuerdruck einzusperren und sozusagen die offene Druckwaage funktionslos zu machen.In a further expedient embodiment, a magnet-actuated 4/2 safety valve is arranged in the second control line and in a parallel discharge line from a load pressure signal circuit to a tank line. This safety valve is energized during operation of the lifting module in each case when energizing a proportional pressure control valve and held in a switching position in which shut off the drain line to the tank and the second control line are continuous. The stopcock of the pipe break valve tester is located between the 4/2-way safety valve and the control side of the pressure compensator to lock in the case of a test applied by the safety valve on the control side of the pressure compensator control pressure and, so to speak, to make the open pressure compensator inoperative.

Zweckmäßig spricht das Rohrbruchventil auf eine höhere Senkgeschwindigkeit bzw. höheren Volumenstrom des Hydroverbrauchers an, als die maximal über den Zweiwege-Stromregler mit ordnungsgemäß arbeitender Druckwaage einstellbare Senkgeschwindigkeit des Hydroverbrauchers.Suitably, the pipe break valve is responsive to a higher lowering speed or higher flow rate of the hydraulic consumer, as the maximum via the two-way flow regulator with properly working pressure compensator adjustable lowering speed of the hydraulic consumer.

Bei einer weiteren Ausführungsform, deren Druckquelle eine Verstellpumpe ist, die auf Minimalförderung oder Nullförderung zurückregelbar ist (CC-Funktion, Closed Centre) ist die Hauptleitung des Hubmoduls zum Hebenstrang an der Seite der Druckquelle von der Tankleitung separiert.In a further embodiment, the pressure source is a variable pump, which is zurückregelbar to minimum promotion or zero promotion (CC function, Closed Center) is the main line of the lifting module to the lifting strand on the side of the pressure source separated from the tank line.

Hingegen ist bei einer Auslegung des Hubmoduls für eine OC-Funktion (Open Centre) mit einer Konstantpumpe als Druckquelle die Hauptleitung, die von der Druckquelle zum Hebenstrang verläuft, über eine Umlauf-Druckwaage mit der Tankleitung verbindbar, um den Förderstrom der Konstantpumpe zum Tank mit möglichst geringen Drosselverlusten abzuführen, wenn keine Last abgenommen wird. Die Umlaufdruckwaage ist an ihrer Schließsteuerseite von einer Feder und aus einem an dem Hebenstrang stromab des Proportional-Druckregelventils gespeisten Lastdrucksignal-Kreis beaufschlagbar, während die Aufsteuerseite der Druckwaage aus der Hauptleitung mit Steuerdruck beaufschlagt wird.On the other hand, in a design of the stroke module for an OC function (Open Center) with a constant displacement pump as a pressure source, the main line, which runs from the pressure source to the hoist strand, connected via a recirculating pressure compensator to the tank line to the flow of the constant pump to the tank with dissipate as small as possible throttle losses when no load is removed. The circulation pressure compensator is acted upon by a spring on its closing control side and by a load pressure signal circuit fed downstream of the proportional pressure regulating valve on the lifting line, while control pressure is applied to the control side of the pressure compensator from the main line.

Anhand der Zeichnung mit der Fig. 1 wird eine Ausführungsform eines Hubmoduls mit einer OC-Funktion anhand eines Blockschaltbilds erläutert.Based on the drawing with the Fig. 1 an embodiment of a lifting module with an OC function is explained with reference to a block diagram.

Der in Fig. 1 stichpunktiert gezeigte Hubmodul H ist zum Einbau in ein Flurförderfahrzeug (nicht gezeigt) bestimmt und vormontiert bzw. in ein Flurförderfahrzeug eingebaut, z. B. um einen hier als Hubzylinder ausgebildeten einseitig z.B. gegen eine Last beaufschlagbaren Hydroverbraucher V zu steuern. Der Hubmodul H kann in Blockbauweise mit anderen Modulen vereinigt sein, die weitere Hydroverbraucher steuern lassen, und die sich eine Hauptleitung 10 und eine Tankleitung 11 teilen (nicht gezeigt).The in Fig. 1 Stitch-point shown lifting module H is intended for installation in a material handling vehicle (not shown) and pre-assembled or installed in an industrial truck, z. B. to one here designed as a lifting cylinder on one side, for example, to be acted upon by a load hydraulic consumers V to control. The lifting module H can be combined in block construction with other modules that can control further hydraulic consumers, and share a main line 10 and a tank line 11 (not shown).

Der Hubmodul H wird zwischen einer Druckquelle P (Konstantpumpe oder Verstellpumpe) und dem Hydroverbraucher V angeordnet, wobei er mit dem Hydroverbraucher V über eine Arbeitsleitung 2 in Form eines Rohres, Schlauches oder einer Leitung verbunden ist.The lifting module H is arranged between a pressure source P (constant pump or variable displacement pump) and the hydraulic consumer V, where it is connected to the hydraulic consumer V via a working line 2 in the form of a pipe, hose or a line.

In der in Fig. 1 gezeichneten Ausführung ist der Hubmodul H mit einer OC-Funktion (Open Centre) ausgelegt, d. h. die Druckquelle P ist eine Konstantpumpe. Alternativ kann der Hubmodul für eine CC-Funktion (Closed Centre) ausgebildet werden, wofür von den in Fig. 1 gezeigten Komponenten einige entnommen oder nicht verbaut werden (wird später erläutert). Bei der CC-Funktion ist die Druckquelle P eine Verstellpumpe, die zwischen maximalem Volumenstrom und Minimal- oder Nullförderung geregelt werden kann.In the in Fig. 1 In the illustrated embodiment, the lifting module H is designed with an OC function (Open Center), ie the pressure source P is a constant-displacement pump. Alternatively, the lifting module can be designed for a CC function (closed center), for which purpose the in Fig. 1 Some of the components shown are removed or not installed (will be explained later). With the CC function, the pressure source P is a variable displacement pump that can be regulated between maximum flow and minimum or zero flow.

Der Hydroverbraucher V ist hier ein einseitig beaufschlagbarer Hubzylinder 1, der an der Seite seiner Kolbenbodenfläche an die Arbeitsleitung 2 angeschlossen ist, und zwar über ein Rohrbruchventil 3.Here, the hydraulic consumer V is a lifting cylinder 1 which can be acted upon on one side and which is connected to the working line 2 on the side of its piston bottom surface via a pipe break valve 3.

Das Rohrbruchventil 3 ist nach Art einer sogenannten Senkbremse ausgebildet. Konkret ist dies z.B. ein 2/2-Wegeventil, das durch eine Feder 7 in der gezeigten, allenfalls leicht drosselnden Durchgangsstellung gehalten wird, und in Schließrichtung über eine Vorsteuerleitung 5 von der Seite des Hydroverbrauchers sowie in Aufsteuerrichtung über eine Vorsteuerleitung 6 aus der Leitung 2 parallel zur Feder 7 beaufschlagt ist. In der aus der Steuerleitung 5 zugesteuerten Schaltstellung wirkt eine starke Ablassdrossel 8 parallel zu einem in Strömungsrichtung aus dem Hubzylinder 1 sperrenden Rückschlagventil 9, so dass selbst unter Last der Hydroverbraucher V nur mit einer bestimmten Senkgeschwindigkeit einfahren kann. Das Rohrbruchventil 3 spricht auf eine beispielsweise im Fall eines Rohrbruchs entstehende Druckdifferenz zwischen den Steuerleitungen 5, 6 an, sobald die Druckdifferenz die Kraft der Feder 7 zu überwinden vermag, und nimmt dann die zugesteuerte Stellung ein, in der der Lastdruck am Rückschlagventil 9 gehalten wird und die Drossel 8 die vorbestimmte Senkgeschwindigkeit begrenzt.The pipe break valve 3 is designed in the manner of a so-called lowering brake. Specifically, this is e.g. a 2/2-way valve, which is held by a spring 7 in the shown, possibly slightly throttling passage position, and in the closing direction via a pilot line 5 from the side of the hydraulic consumer and in Aufsteuerrichtung via a pilot line 6 from the line 2 parallel to the spring. 7 is charged. In the controlled from the control line 5 switching position acts a strong discharge throttle 8 parallel to a blocking in the flow direction from the lifting cylinder 1 check valve 9, so that even under load of the hydraulic consumer V can retract only with a certain lowering speed. The broken pipe valve 3 is responsive to a pressure difference, for example, in the event of a pipe break between the control lines 5, 6, as soon as the pressure difference is able to overcome the force of the spring 7, and then assumes the controlled position, in which the load pressure is maintained at the check valve 9 and the throttle 8 limits the predetermined lowering speed.

Eine im Hubmodul H mit der Druckquelle P verbundene Hauptleitung 10 zweigt sich in einen Ast zu einem Hebenstrang 20 auf, und in einen Ast 14 zu einer Umlauf-Druckwaage 12, wobei dieser Ast 14 mit einer Tankleitung 11 verbindbar ist. Die Umlauf-Druckwaage 12 wird durch eine Feder 17 in der gezeigten Sperrstellung gehalten, wird parallel zur Feder 17 aus einem Lastdrucksignal-Kreis 18 beaufschlagt, der beispielsweise in einem Knoten 19 an den Hebenstrang 20 angeschlossen ist, und der über eine Ablass-Steuerleitung 18' mit der Tankleitung 11 verbindbar ist. In Aufsteuerrichtung an einer Aufsteuerseite 15 wird die Umlauf-Druckwaage 12 aus einer von der Hauptleitung 10 bzw. deren Ast 14 abzweigenden Steuerleitung beaufschlagt. Der Lastdrucksignal-Kreis 18 ist an die Zusteuerseite 16 der Umlauf-Druckwaage 12 angeschlossen. Zwischen dem Lastdrucksignal-Kreis 18 und der Tankleitung 11 ist ferner ein Systemdruck-Begrenzungsventil 13 angeordnet.A in the lifting module H connected to the pressure source P main line 10 branches into a branch to a hoisting line 20, and in a branch 14 to a circulating pressure compensator 12, said branch 14 with a tank line 11 is connectable. The circulating pressure compensator 12 is held by a spring 17 in the blocking position shown, is acted parallel to the spring 17 from a load pressure signal circuit 18 which is connected for example in a node 19 to the lifting strand 20, and via a drain control line 18th 'is connected to the tank line 11. In Aufsteuerrichtung on a Aufsteuerseite 15, the circulation pressure compensator 12 is acted upon from one of the main line 10 and its branch 14 branching control line. The load pressure signal circuit 18 is connected to the supply side 16 of the circulation pressure compensator 12. Between the load pressure signal circuit 18 and the tank line 11, a system pressure limiting valve 13 is further arranged.

Im Hebenstrang 20 ist zwischen dem Knoten 19 und der Hauptleitung 10 ein Proportional-Druckregelventil 21 zur Hebensteuerung des Hydroverbrauchers V angeordnet, hier ein 2/2-Wege-Proportional-Druckregelventil 21 mit einem Proportionalmagneten, einer Feder und einer Hydraulikvorsteuerung. Zwischen dem Knoten 19 und einem weiteren Knoten 23 im Hebenstrang 20 ist ein Rückschlagventil 22 angeordnet, das in Strömungsrichtung zum Proportional-Druckregelventil 21 sperrt. Am Knoten 23 ist die Arbeitsleitung 2 angeschlossen. Vom Knoten 23 führt ein Senkenstrang 24 zur Tankleitung 11. Der Senkenstrang 24 enthält ein Proportional-Druckregelventil 26, beispielsweise in Sitzventilbauweise, das baugleich sein kann mit dem Proportional-Druckregelventil 21, und durch einen Proportionalmagneten 27 gegen Federkraft und z.B, mittels Hydraulikvorsteuerung betätigbar ist. Die Bestromung des Proportionalmagneten 27 bestimmt unter anderem die Senkgeschwindigkeit des Hydroverbrauchers V, die maximal z.B. etwa Last 0,6 m/s beträgt, auch unter Last und die durch eine Druckwaage 28 im Senkenstrang 24 beeinflusst wird.In the hoisting line 20, a proportional pressure control valve 21 for lifting control of the hydraulic consumer V is arranged between the node 19 and the main line 10, here a 2/2-way proportional pressure control valve 21 with a proportional solenoid, a spring and a hydraulic pilot. Between the node 19 and another node 23 in the lifting strand 20, a check valve 22 is arranged, which blocks in the flow direction to the proportional pressure control valve 21. At node 23, the working line 2 is connected. From the node 23, a drain line 24 leads to the tank line 11. The drain line 24 includes a proportional pressure control valve 26, for example in poppet design, which may be identical to the proportional pressure control valve 21, and by a proportional solenoid 27 against spring force and, for example, by means of hydraulic pilot is operable , The energization of the proportional solenoid 27 determines inter alia, the lowering speed of the hydraulic consumer V, the maximum eg about 0.6 m / s load, even under load and which is influenced by a pressure compensator 28 in the sink train 24.

Das Proportional-Druckregelventil 26 und die Druckwaage 28 bilden einen Zweiwege-Stromregler 25, mit dem die Senkgeschwindigkeit lastunabhängig geregelt wird, wie erwähnt bis auf beispielsweise maximal 0,6 m/s. Die Druckwaage 28 hat eine Zusteuerseite 31 und eine Aufsteuerseite 32. An der Aufsteuerseite 32 wirkt eine Regelfeder 33. An der Zusteuerseite 31 ist eine Steuerleitung 30 angeschlossen, die an einem Knoten 29 vom Senkenstrang 24 stromauf des Proportional-Druckregelventils 26 abzweigt. Zwischen dem Proportional-Druckregelventil 26 und der Druckwaage 28 zweigt an einem Knoten 35 eine zweite Steuerleitung 34 zur Aufsteuerseite 32 ab, an der auch die Regelfeder 33 wirkt.The proportional pressure control valve 26 and the pressure compensator 28 form a two-way current controller 25, with which the lowering speed is regulated independent of the load, as mentioned, except for example, a maximum of 0.6 m / s. At the feed side 32, a control line 30 is connected, which branches off at a node 29 from the sink train 24 upstream of the proportional pressure control valve 26. Between the proportional pressure control valve 26 and the pressure compensator 28 branches off at a node 35, a second control line 34 from the control side 32 from where the control spring 33 acts.

Die bei Ansprechen vom Rohrbruchventil 3 zu begrenzende Senkgeschwindigkeit des Hydroverbrauchers ist um ca. 20 % höher als die mit dem Zweiwege-Stromregler 25 einzustellende maximale Geschwindigkeit.The lowering of the hydraulic load to be limited in response to the pipe break valve 3 is about 20% higher than the maximum speed to be set with the two-way flow controller 25.

In der gezeigten Ausführungsform ist in der Ablass-Steuerleitung 18' zwischen dem Lastdrucksignal-Kreis 18 und der Tankleitung 11 sowie in der zweiten Steuerleitung 34 ein 4/2-Wege-Sicherheitsventil 36 angeordnet, das durch eine Feder in der gezeigten Schaltstellung gehalten wird und durch einen Schwarz-Weiß-Magneten 37 in die andere Schaltstellung umzuschalten ist. Wenn immer einer der Proportionalmagneten der beiden Proportional-Druckregelventile 21 und 26 bestromt wird, ist auch der Magnet 37 bestromt, so dass im Betrieb des Hubmoduls die Ablassleitung 18' abgesperrt und die zweite Steuerleitung 38 durchgängig sind. In stromlosem Zustand entlastet hingegen das Sicherheitsventil 36 die Ablass-Steuerleitung 18' zum Tank, wie gezeigt, und auch den zur Aufsteuerseite 32 der Druckwaage 28 führenden Teil der zweiten Steuerleitung 34, während die Verbindung vom Knoten 35 zu diesem Teil der zweiten Steuerleitung 34 gesperrt ist.In the embodiment shown, a 4/2-way safety valve 36 is disposed in the drain control line 18 'between the load pressure signal circuit 18 and the tank line 11 and in the second control line 34, which is held by a spring in the switching position shown and is to switch by a black and white magnet 37 in the other switching position. Whenever one of the proportional solenoids of the two proportional pressure control valves 21 and 26 is energized, the magnet 37 is also energized, so that during operation of the lifting module, the drain line 18 'shut off and the second control line 38 are continuous. In the de-energized state, however, relieves the safety valve 36, the drain control line 18 'to the tank, as shown, and also leading to Aufsteuerseite 32 of the pressure compensator 28 part of the second control line 34, while the connection from the node 35 to this part of the second control line 34 locked is.

Erfindungsgemäß ist in der zweiten Steuerleitung 34 eine Rohrbruchventil-Prüfvorrichtung T vorgesehen, hier beispielsweise ein Absperrhahn 38, der in der gezeigten Ausführungsform zwischen dem Sicherheitsventil 36 und der Aufsteuerseite 32 verbaut ist. Der Absperrhahn 38 kann manuell bzw. manuell und elektrisch (über einen Magneten 39) betätigt werden, und zwar zwischen einer nicht drosselnden Durchgangsstellung und einer Absperrstellung.According to the invention, a pipe rupture valve test device T is provided in the second control line 34, here for example a shut-off cock 38 which in the embodiment shown is installed between the safety valve 36 and the rudder 32. The stopcock 38 can be manually or manually and electrically operated (via a magnet 39), between a non-throttling passage position and a shut-off position.

Der Absperrhahn 38 kann durch jede andere Absperrvorrichtung ersetzt sein, die sich zwischen einer Durchgangsstellung und einer Absperrstellung umschalten lässt.The stopcock 38 may be replaced by any other shut-off device that can be switched between a passage position and a shut-off.

Die Rohrbruchventil-Prüfvorrichtung T gestattet in zusammengebautem und betriebsbereitem Zustand des Hubmoduls H mit angeschlossenem Hydroverbraucher V und angeschlossener Druckquelle P eine Überprüfung der ordnungsgemäßen Funktion des Rohrbruchventils 3, das allein durch den Zweiwege-Stromregler 25 nicht zum Ansprechen gebracht werden kann.The pipe breakage valve tester T allows in assembled and ready state of the lifting module H with connected hydraulic consumer V and connected pressure source P a check of the proper function of the pipe break valve 3, which can not be made to respond solely by the two-way current controller 25.

Hierzu wird bei voller Bestromung des Proportionalmagneten 27 und des Schwarz-Weiß-Magneten 37 der Absperrhahn 38 in die Sperrstellung gebracht, so dass der an der Aufsteuerseite 32 herrschende Druck gehalten bzw. das in diesem Teil der zweiten Steuerleitung 34 und an der Aufsteuerseite vorhandene Hydraulikmedium eingesperrt wird. Die Druckwaage 28 kann demzufolge nicht mehr regeln, sondern bleibt in der voll aufgesteuerten Stellung, in der die Senkgeschwindigkeit des Hydroverbrauchers bzw. die Druckdifferenz zwischen den Steuerleitungen 5, 6 so hoch wird, dass das Rohrbruchventil 3 umschaltet. Dann kann die Senkgeschwindigkeit des Hydroverbrauchers kontrolliert werden, und damit im Umkehrschluss die ordnungsgemäße Funktion des Rohrbruchventils 3.For this purpose, the stopcock 38 is brought into the blocking position at full energization of the proportional magnet 27 and the black-and-white magnet 37, so that the prevailing at the Aufsteuerseite 32 held pressure or existing in this part of the second control line 34 and on the control side hydraulic medium is locked up. The pressure compensator 28 can therefore no longer regulate, but remains in the fully open position in which the lowering speed of the hydraulic consumer or the pressure difference between the control lines 5, 6 is so high that the pipe break valve 3 switches. Then, the lowering speed of the hydraulic consumer can be controlled, and thus in the reverse order, the proper operation of the pipe break valve. 3

Um das Rohrbruchventil 3 wieder in die gezeigte Stellung umzuschalten, wird ein Druckimpuls über das Heben-Proportionaldruckregelventil 21 eingesteuert, oder abgewartet, bis die Feder 7 die Umstellung vornimmt.In order to switch the pipe break valve 3 back into the position shown, a pressure pulse via the lifting proportional pressure control valve 21 is controlled, or waited until the spring 7 makes the changeover.

Das Sicherheitsventil 36 ist eine Option und kann gegebenenfalls weggelassen werden. Dann ist ggfs. die Ablassleitung 18' über eine Drossel (nicht gezeigt) mit der Tankleitung 11 verbunden, und ist die zweite die Prüfvorrichtung T enthaltende Steuerleitung 34 vom Knoten 35 zur Aufsteuerseite 32 durchgängig.The safety valve 36 is an option and may be omitted as appropriate. Then, if necessary, the drain line 18 'is connected to the tank line 11 via a throttle (not shown), and the second control line 34 containing the test device T is continuous from the node 35 to the control side 32.

Für eine CC-Funktion des Hubmoduls H wird die Umlauf-Druckwaage 12 ausgebaut oder nicht eingebaut, wird der Ast 14 der Hauptleitung 10 abgesperrt, und werden auch die Auf- und Zusteuerseiten 15, 16 blockiert, wie auch der Anschluss zu der Tankleitung 11.For a CC function of the lifting module H, the circulation pressure compensator 12 is removed or not installed, the branch 14 of the main line 10 is shut off, and the up and Zusteuerseiten 15, 16 blocked, as well as the connection to the tank line eleventh

Claims (7)

Hubmodul (H) für ein Flurförderfahrzeug, mit einem einseitig gegen eine Last von einer Druckquelle (P) aus einem Hebenstrang (20) über ein Proportional-Druckregelventil (21) zum Heben beaufschlagbaren Hydroverbraucher (V), der über einen Senkenstrang (24) mit einem Zweiwege-Stromregler (25) aus Proportional-Druckregelventil (26) und Druckwaage (28) in Senkrichtung verstellbar ist, und mit einem dem Hydroverbraucher (V) zugeordneten, als Senkbremse ausgebildeten Rohrbruchventil (3), dadurch gekennzeichnet, dass dem Zweiwege-Stromregler (25) eine wahlweise betätigbare Rohrbruchventil-Prüfvorrichtung (T) zugeordnet ist, mit der unter Betreiben des Hubmoduls (High-K-Dielektrikumsschicht) das Rohrbruchventil (3) zum Ansprechen bringbar ist.Lifting module (H) for an industrial truck, with a one-sided against a load from a pressure source (P) from a hoist strand (20) via a proportional pressure control valve (21) acted upon for lifting hydraulic consumer (V), via a drain line (24) a two-way flow regulator (25) from the proportional pressure control valve (26) and pressure compensator (28) in the lowering direction is adjustable, and with a hydraulic consumer (V) associated, formed as a lowering pipe break valve (3), characterized in that the two-way flow regulator (25) is associated with a selectively operable burst breaker valve tester (T), with the operation of the lifting module (high-K dielectric layer), the pipe break valve (3) can be brought to respond. Hubmodul nach Anspruch 1, dadurch gekennzeichnet, dass die Rohrbruchventil-Prüfvorrichtung (T) ein manuell und/oder elektrisch betätigbarer Absperrhahn (38) ist, in dessen Absperrstellung auf eine Aufsteuerseite (32) der Druckwaage (28) des Zweiwege-Stromreglers (25) gebrachter Steuerdruck mit aufgesteuerter Druckwaage (28) haltbar ist.Lifting module according to claim 1, characterized in that the broken pipe valve test device (T) is a manually and / or electrically operable shut-off valve (38), in its shut-off position on a control side (32) of the pressure compensator (28) of the two-way current regulator (25) supplied control pressure with controlled pressure compensator (28) is durable. Hubmodul nach Anspruch 1, dadurch gekennzeichnet, dass die Druckwaage (28) des Zweiwege-Stromreglers (25) an einer Zusteuerseite (31) aus einer vom Senkstrang (24) stromauf des Proportional-Druckregelventils (26) abzweigenden ersten Steuerleitung (30) und an der Aufsteuerseite (32) parallel zu einer Regelfeder (33) aus einer vom Senkstrang (24) zwischen dem Proportional-Druckregelventil (26) und der Druckwaage (28) abzweigenden zweiten Steuerleitung (34) beaufschlagbar ist, und dass der Absperrhahn (38) in der zweiten Steuerleitung (34) angeordnet ist.Lifting module according to claim 1, characterized in that the pressure compensator (28) of the two-way flow regulator (25) on a Zusteuerseite (31) from a lowering of the strand (24) upstream of the proportional pressure control valve (26) branching first control line (30) and the Aufsteuerseite (32) parallel to a control spring (33) from a Senkstrang (24) between the proportional pressure control valve (26) and the pressure compensator (28) branching second control line (34) can be acted upon, and that the stopcock (38) in the second control line (34) is arranged. Hubmodul nach Anspruch 3, dadurch gekennzeichnet, dass in der zweiten Steuerleitung (34) und in einer Ablassleitung (28') von einem Lastbruchsignal-Kreis (28) zu einem Rücklauf (R) ein magnetbetätigtes 4/2-Wege-Sicherheitsventil (36) angeordnet ist, und dass der Absperrhahn (38) in der zweiten Steuerleitung (34) zwischen dem 4/2-Wege-Sicherheitsventil (36) und der Aufsteuerseite (32) der Druckwaage (28) angeordnet ist.Lifting module according to claim 3, characterized in that in the second control line (34) and in a discharge line (28 ') from a load break signal circuit (28) to a return (R) a solenoid-operated 4/2-way safety valve (36) is arranged, and that the stopcock (38) in the second control line (34) between the 4/2-way safety valve (36) and the control side (32) of the pressure compensator (28) is arranged. Hubmodul nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Rohrbruchventil (3) auf eine höhere Senkgeschwindigkeit des Hydroverbrauchers (V) ausgelegt ist als die maximal über den Zweiwege-Stromregler (26) bei ordnungsgemäß arbeitender Druckwaage (28) einstellbare Senkgeschwindigkeit.Lifting module according to at least one of the preceding claims, characterized in that the pipe break valve (3) is designed for a higher lowering speed of the hydraulic consumer (V) than the maximum via the two-way flow regulator (26) with properly working pressure compensator (28) adjustable lowering speed. Hubmodul nach wenigstens einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Hubmodul (H) für eine CC-Lösung mit einer Verstellpumpe als Druckquelle (P) eine von einer Tankleitung (11) separierte Hauptleitung (10) von der Druckquelle (P) zum Hebenstrang (20) aufweist.Lifting module according to at least one of the preceding claims, characterized in that the lifting module (H) for a CC solution with a variable displacement pump as a pressure source (P) from a tank line (11) separated main line (10) from the pressure source (P) to the lifting strand (20). Hubmodul nach wenigstens einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass der Hubmodul (H) für eine OC-Lösung mit einer Konstantpumpe als Druckquelle (P) eine über eine Umlauf-Druckwaage (12) mit einer Tankleitung (11) verbindbare Hauptleitung (10) von der Druckquelle (P) zum Hebenstrang (20) aufweist und dass, die Umlauf-Druckwaage (12) an der Schließsteuerseite (16) von einer Feder (17) und aus einem vom Hebenstrang (20) stromab des Proportional-Druckregelventils (21) gespeisten Lastdruck-Signalkreis (18) und an der Schließsteuerseite (15) aus der Hauptleitung (10) beaufschlagbar ist.Lifting module according to at least one of claims 1 to 5, characterized in that the lifting module (H) for an OC solution with a constant pump as a pressure source (P) via a circulation pressure compensator (12) with a tank line (11) connectable main line ( 10) from the pressure source (P) to the hoistway (20), and in that the recirculation pressure compensator (12) is located at the closing control side (16) by a spring (17) and one from the hoistway (20) downstream of the proportional pressure control valve (16). 21) fed load pressure signal circuit (18) and on the closing control side (15) from the main line (10) can be acted upon.
EP14200055.3A 2014-12-23 2014-12-23 Lifting module Not-in-force EP3037678B1 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018104586A1 (en) * 2018-02-28 2019-08-29 Jungheinrich Aktiengesellschaft Truck with at least one hydraulic mast lifting cylinder
CN113233279A (en) * 2021-04-16 2021-08-10 广东省特种设备检测研究院（广东省特种设备事故调查中心） Speed limiting valve test device and test method

Citations (3)

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Publication number Priority date Publication date Assignee Title
DE4239321A1 (en) * 1992-11-23 1994-05-26 Heilmeier & Weinlein Fork lift stacking truck with hydraulic work platform activator - has electrically operated two-way flow regulation to maintain stable platform load position
EP1369598A1 (en) * 2002-06-03 2003-12-10 HAWE Hydraulik GmbH & Co. KG Electro-hydraulic lifting control device for industrial use vehicles
EP2236452A1 (en) * 2009-04-03 2010-10-06 HAWE Hydraulik SE Lifting module

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4239321A1 (en) * 1992-11-23 1994-05-26 Heilmeier & Weinlein Fork lift stacking truck with hydraulic work platform activator - has electrically operated two-way flow regulation to maintain stable platform load position
EP1369598A1 (en) * 2002-06-03 2003-12-10 HAWE Hydraulik GmbH & Co. KG Electro-hydraulic lifting control device for industrial use vehicles
EP1369598B1 (en) 2002-06-03 2007-09-26 HAWE Hydraulik GmbH & Co. KG Electro-hydraulic lifting control device for industrial use vehicles
EP2236452A1 (en) * 2009-04-03 2010-10-06 HAWE Hydraulik SE Lifting module

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018104586A1 (en) * 2018-02-28 2019-08-29 Jungheinrich Aktiengesellschaft Truck with at least one hydraulic mast lifting cylinder
US11377334B2 (en) 2018-02-28 2022-07-05 Jungheinrich Aktiengesellschaft Industrial truck with at least one hydraulic mast lift cylinder
CN113233279A (en) * 2021-04-16 2021-08-10 广东省特种设备检测研究院（广东省特种设备事故调查中心） Speed limiting valve test device and test method

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