EP2985473B1 - Lifting module - Google Patents

Lifting module Download PDF

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Publication number
EP2985473B1
EP2985473B1 EP14180521.8A EP14180521A EP2985473B1 EP 2985473 B1 EP2985473 B1 EP 2985473B1 EP 14180521 A EP14180521 A EP 14180521A EP 2985473 B1 EP2985473 B1 EP 2985473B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
conduit
lifting module
control
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
EP14180521.8A
Other languages
German (de)
French (fr)
Other versions
EP2985473A1 (en
Inventor
Recep Macit
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 SE
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Filing date
Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP14180521.8A priority Critical patent/EP2985473B1/en
Publication of EP2985473A1 publication Critical patent/EP2985473A1/en
Application granted granted Critical
Publication of EP2985473B1 publication Critical patent/EP2985473B1/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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/004—Fluid pressure supply failure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053—Flow control characterised by the type of flow control means or valve with flow dividers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy
    • 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
    • F15B2211/8633—Pressure source supply failure

Definitions

  • the invention relates to a lifting module according to the preamble of claim 1.
  • the lifting proportional control valve is arranged with a arranged in the lifting rod pressure compensator as a three-way current regulator.
  • the pressure line fed directly from the pressure source like the tank line, leads to other consumers of the industrial truck connected to the lifting module.
  • the safety valve which connects the load pressure signal circuit to the tank line without being energized and at the same time shuts off the control line branching off from the drawstring, while connecting the control side of the drawstring pressure compensator to the tank line, is supplied in each case by energizing the proportional solenoid of the lifting proportional control valve or the lowering proportional Energized so that it separates the load pressure signal circuit from the tank line and at the same time switches the branching off from the drain line control line to the control side of the pressure compensator in the positive sequence.
  • the safety valve has the task to ensure that a load neither sinks nor is raised further uncontrolled when the lifting proportional control valve or the lowering proportional control valve or its pressure compensator.
  • EP 2466155 A1 is a pilot-operated check valve, especially for lifting modules, known, which has a very large Auf Kunststoffdruck husband and possibly even with pre-relief is unlocked.
  • the pilot-operated check valve is housed in a Einschraubgephaseuse, which may be designed in the manner of an Ermeto screw-in housing and therefore conveniently in the connection bore, for example, a pressure source can be accommodated.
  • EP 0546300 A1 discloses a lift module of an industrial truck in which the lift proportional control valve is part of a three-way flow regulator, that is its 3/2-way pressure compensator is connected directly to the pressure line fed by the pressure wave. From this pressure compensator via a check valve performs a working line to further, fed from the same pressure source consumers.
  • the 3/2-way pressure compensator as part of the three-way flow regulator can not reliably prevent a flow from the pressure source to the lifting string if the 2/2-way proportional valve of the 3-way flow regulator or the pressure compensator should become stuck. In such a malfunction case, the unilaterally acted hydraulic consumer would lift the load.
  • the invention is based on the object, a lifting module of the type mentioned with a structurally simple, functionally reliable and space-saving shut-off device for the flow indicate the pressure source in order to comply with applicable regulations on the safety of industrial trucks.
  • the provided on or in the lifting module disconnecting device for the flow of the pressure source requires no magnet and speaks independently to the control pressure in the load pressure signal circuit.
  • the shutdown device has either one of the load pressure signal circuit hydraulically releasable check valve. As long as the load pressure signal circuit carries a load pressure signal, the check valve is unlocked, so that the pressure line can be beaugschlasgt. On the other hand, the check valve locks in the absence of a signal pressure in the load pressure signal circuit. Otherwise, the shutdown on a pressure-controlled 3/2-way priority valve. In the absence of a signal pressure, the priority valve allows the load pressure signal circuit to control the priority hydro-consumer, but prevents the delivery flow from the pressure source from being fed to the pressure line.
  • the shutdown device is designed for either an OC function or a CC function.
  • An OC function is typically given when using a constant displacement pump, while a CC function is given when using a variable displacement pump. So if it is clear from the outset that the user wants only an OC function or only a CC function, the lifting module can be tuned to it right from the start. More expediently, however, the lifting module is optionally convertible between the OC function and the CC function, so that the user can freely choose the function for which he uses the lifting module. This embodiment extends the field of application of the lifting module in a universal manner.
  • the priority hydraulic consumer in a further embodiment in which a priority hydraulic consumer, which can be fed separately from the pressure source, is connected to the lifting module, the priority hydraulic consumer can be permanently controlled.
  • the shutdown device between the pressure line and the tank line in addition to the priority valve or the pilot-operated check valve has a pressure compensator slide or a 2/2-way seat valve.
  • the pressure line remains unpressurized after the shutdown, while the priority hydro consumer is still controllable.
  • the lifting module it is expedient to provide a mechanically adjustable stop on the 2/2-way pressure compensator slide or on the 2/2-way seat valve to its intended passivation.
  • the stop secures the shut-off position and can be used as required. If it is clear from the outset that only one CC function is desired, the pressure compensator valve or the seat valve can also be omitted.
  • a control line bypass provided with a pressure source blocking check valve and a throttle downstream of the check valve, and branches between the check valve and the throttle an unlocking control pressure line to unlockable check valve.
  • the pilot-operated check valve is expediently unlocked with a pre-relief, so that relatively low control pressure sufficient for proper unlocking and keeping open.
  • a larger pressure application area is expediently provided at a second control side of the priority valve facing away from a spring and a first control side than at the first control side.
  • the lifting module has a load pressure signal connection, for example for a variable displacement pump, and a separate load pressure signal connection of the priority hydraulic consumer, in order to optimize the latter in each case Supply priority pressure or the required amount. Between these load pressure signal connections a shuttle valve is expediently arranged in the load pressure signal circuit.
  • the 2/2-way pressure compensator valve or the 2/2-way seat valve in the direction of control from the pressure line and in Zuberichtraumraum, parallel to a spring, pressure-controlled from the load pressure signal circuit.
  • the pilot-operated check valve has expediently a Aufberichtdruck chorus of at least 1: 5 to, preferably, even to about 1:30 to unlock the check valve reliably even at high working pressure with low control pressure and low amount of control oil.
  • pilot-operated check valve and the control line bypass with the unlocking control line are accommodated in a screw-in housing with which the pressure source is connected to the lifting module.
  • the Einschraubgecher resembles a standard Ermeto screw-in.
  • Fig. 1 is a dot-dash line indicated lifting module 1 for a one-sided controllable against a load hydraulic consumer H of a material handling vehicle, for example, formed as a block with integrated or built-hydraulic components.
  • non-illustrated hydraulic consumers of the industrial truck are connected, for example, to terminals 2, 3 and 22 (pressure line connection 2, tank line connection 3, load pressure signal circuit connection 22).
  • a load pressure signal connection 4 is provided, from which a load pressure signal can be brought to a schematically indicated pressure source Q, in the case of a variable displacement pump to the pump regulator.
  • a pressure source connection 5 and a load pressure signal circuit 19 with a connection 6 are provided, in the region of which a switch-off device V is integrated or screwed on, for example in the form of an Ermeto screw connection 38 (screw-in housing).
  • a tank line connection 7 is connected to the tank, not shown, of the pressure source.
  • a working line 8 From the terminal 5 performs a working line 8 to a 2/2-pressure compensator slide 27, which is acted on the closing control side by a spring 28 and coming from a port 6 control line 24 of a load pressure signal circuit 19, on the control side, however, via a control line 29, the the working line 8 is connected.
  • the 2/2-way pressure compensator 27 is equipped with a manually adjustable stop 30 to be passivated if necessary (in the locked position).
  • a pressure relief valve 26 is provided between the control line 24 and the tank line 10.
  • the load pressure signal circuit 19 is used i.a.
  • the lifting proportional control valve 11 has a spring 14, which is responsible for the shut-off position shown, and a proportional solenoid 13 and, as an option, a hydraulic pressure pilot 15. It is used for load-independent control of the lifting speed of the hydraulic consumer H.
  • Downstream of the check valve 13 branches off from the lifting strand 12 from a Senkstrang 17 to the tank line 10, in which a lowering proportional control valve 16 (with the same equipment as the lifting proportional control valve 11) and a 2/2-way pressure compensator 18 included are.
  • a control line 31 which leads via a damping device 32 with check valve and throttle to Schndmatiseite the pressure compensator 18, and between the pressure compensator 18 and the lowering proportional control valve 16, a control line 33 to the closing control side of the pressure compensator 18, where also a Spring ensures the passage position shown.
  • the load pressure signal circuit 19 is connected via a control line 25 to the tank line 10, wherein in the control line 25, a 3/2-way safety valve 34 with magnetic actuation (black / white magnet 35) is included in the energizing the proportional solenoid 13 of the lifting Proportional control valve 11 or the lowering proportional control valve 16 is energized, and then switches from the position shown in the upper position. The position shown is held by a spring 36. In this position, the control line 25 and the control side of the pressure compensator 18 via the short-circuit line 37 to the tank line 10, while the branched off from the sunk strand 17 control line 33 is shut off to the control side of the pressure compensator 18. In the other switching position is at Bestromen the magnet 35, the control line 25 separated from the tank line 10, and the Senkstrang 17 is connected via the control line 33 to the control side of the pressure compensator 18.
  • the proportional magnet 13 and the magnet 35 are connected to a higher-level control device CU, which ensures the simultaneous energization.
  • a program routine is provided, with which the 3/2-way safety valve 34 can also be switched back and forth independently of the proportional magnet 13.
  • the control line 20 is connected via a filter and a throttle and a control line section 23 to the tank line 10, and continues via a throttle to a shuttle valve 21 and the load pressure signal port 4.
  • a load pressure signal from the other Consumers are fed, the shuttle valve 21 ensures that the respective higher signal pressure is transmitted to the terminal 4.
  • the disconnecting device V in Einschraubgephase 38 contains, for example, before the connection 5 in Fig. 1 in the direction of the working line 8 blocking, but hydraulically releasable check valve 39 to port 5, and a control line bypass 40 to port 6.
  • a control line bypass 40 in the direction of the pressure source Q blocking check valve 41 and a throttle 42 are included, wherein between the check valve 41 and the throttle 42 an unlock control line 43 leads to the pilot-operated check valve 39.
  • the lifting proportional control valve 11 If the lifting proportional control valve 11 is energized, then the 3/2-way safety valve 34 is energized, so that the load pressure signal circuit 19 is shut off to the tank line 10 and on the one hand via the control line bypass 40 of the shutdown device V and on the other hand from the lifting strand 12th Signal pressure builds up.
  • the check valve 39 is unlocked and acts on the pressure line 9.
  • the hydraulic consumer H is raised against the load.
  • the lift proportional control valve 11 is de-energized, as well as the solenoid 35, the load is held by the check valve 13 and the lowering proportional control valve 16. If the lifting movement is interrupted, i. the proportional solenoid 13 of the lifting proportional control valve 11 is de-energized, and the magnet 35 is de-energized, and the load pressure signal circuit 19 relieved.
  • the shutdown device V switches over, i. the check valve 39 blocks from the pressure source Q to the working line 8 from.
  • the shutdown device V is then active (check valve 39 blocks) when none of the proportional solenoid 13 and the magnet 35 is energized.
  • the lowering control remains possible at any time.
  • the stop 30 is adjusted so that the 2/2-way pressure compensator valve 27 remains in the blocking position.
  • the 2/2-way pressure compensator 27 could even be omitted.
  • the attack remains passive.
  • a priority hydro consumer Cf connected to the lifting module 1, which is supplied with pressure medium separated from the pressure line G from the pressure source Q.
  • the priority hydraulic consumer Cf is, for example, a hydraulic steering of the industrial truck. From this hydraulic steering connection to a signal pressure port 46 is also given.
  • the shutdown device V contains, for example in the block of the lifting module, a 3/2-way priority valve 48th
  • control line 20 from the shuttle valve 21 via a shuttle valve 45 is selectively connectable to the signal pressure port 46 or 4.
  • the priority hydraulic consumer Cf is connected to a working line 47 leading to the 3/2 priority valve 48 leads between the working line 8 and the pressure line 9. From the working line 47 branched control lines 49 on the one hand to the control line 25 and to a second control side 51 of the 3/2-way priority valve 48 and the control line 24 and to a first control side 50 from where the spring 28 acts.
  • the loading surface on the second control side 51 is greater than the loading surface on the first control side 50, so that when there is a signal pressure in the load pressure signal circuit 19, the 3/2-way priority valve 48 switches from the switching position shown, and both the working line 47 and the pressure line 9 are fed, the working line 47 has priority.
  • a 2/2-way valve seat 27 ' is arranged (analogous function as the 2/2-way pressure compensator valve 27 in Fig. 1 , but without leakage losses), which is pressure-controlled from the pressure line 9 in the up direction and from the load pressure signal circuit 19 via the shuttle valve 45, on the closing control side parallel to the spring 28 '.
  • the 2/2-way seat valve 27 ' contains inside a throttle, via which a closing pressure can be generated.
  • the 2/2-way seat valve 27 ' can be passivated via the manually adjustable stop 30', so that it keeps its closed position shown. In an OC function, however, the stop 30 'is not effective. If only one CC function is possible from the outset, the valve 27 'can be omitted.
  • a lifting process will be like in Fig. 1 controlled. A lowering process is possible at any time.
  • the shutdown device V is then active when no lifting operation is controlled, in which then the 3/2-way priority valve 48, the in Fig. 2 shown switching position holds.
  • the pressure line 9 remains unpressurized, previously the 2/2-way valve seat 27 'may have relieved the pressure line 9 to the tank line 10 when the signal pressure drops. If signal pressure is present in the load pressure signal circuit 19, the 2/2-way seat valve separates 27 ', however, the pressure line 9 from the tank line 10.
  • pressure gauges can be connected to the lifting module 1.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Structural Engineering (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid Mechanics (AREA)
  • Civil Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Analytical Chemistry (AREA)

Description

Die Erfindung betrifft einen Hubmodul gemäß Oberbegriff des Patentanspruches 1.The invention relates to a lifting module according to the preamble of claim 1.

Bei dem aus EP 1369598 A1 bekannten Hubmodul ist das Hebe-Proportional-Steuerventil mit einer im Hebestrang angeordneten Druckwaage als Drei-Wege-Stromregler ausgebildet. Die direkt aus der Druckquelle gespeiste Druckleitung führt wie die Tankleitung zu weiteren, an den Hubmodul angeschlossenen Verbrauchern des Flurförderfahrzeugs. Das Sicherheitsventil, das unbestromt den Lastdrucksignalkreis mit der Tankleitung verbindet und gleichzeitig die vom Senkstrang abzweigende Steuerleitung absperrt, hingegen die Aufsteuerseite der Senkstrang-Druckwaage mit der Tankleitung verbindet, wird jeweils mit Bestromen des Proportionalmagneten des Hebe-Proportional-Steuerventils oder des Senk-Proportional-Steuerventils bestromt, so dass es den Lastdrucksignalkreis von der Tankleitung trennt und gleichzeitig die vom Senkstrang abzweigende Steuerleitung zur Aufsteuerseite der Druckwaage im Senkstrang durchgängig schaltet. Das Sicherheitsventil hat die Aufgabe, beim Hängenbleiben des Hebe-Proportional-Steuerventils oder des Senk-Proportional-Steuerventils oder dessen Druckwaage sicherzustellen, dass eine Last weder absinkt noch unkontrolliert weiter angehoben wird. Dies entspricht DIN/ISO-Vorschriften zur Sicherheit von Flurförderfahrzeugen. Diese Vorschriften fordern auch eine Abschaltung des Förderstroms von der Druckquelle für den Fall, dass beispielsweise die Druckquelle weiter fördert, beispielsweise weil sie die steuerungsseitig hängengeblieben ist oder ein Fahrer versehentlich einen Förderbefehl gibt. Dies könnte nämlich trotz der Einflussnahme des Sicherheitsventils beispielsweise ein weiteres Anheben der Last bewirken. Um diese Vorschriften zu erfüllen, wird in der Praxis bei dem bekannten Hubmodul zwischen der Druckquelle und dem Hubmodul ein magnetbetätigtes 2/2-Wegeventil separat angeordnet, mit dem der Förderstrom der Druckquelle abschaltbar ist. Dieses 2/2-Magnetventil ist im beengten Bauraum schwer unterzubringen und bedeutet erheblichen Kostenaufwand nur für die Abschaltfunktion.At the EP 1369598 A1 Known lifting module, the lifting proportional control valve is arranged with a arranged in the lifting rod pressure compensator as a three-way current regulator. The pressure line fed directly from the pressure source, like the tank line, leads to other consumers of the industrial truck connected to the lifting module. The safety valve, which connects the load pressure signal circuit to the tank line without being energized and at the same time shuts off the control line branching off from the drawstring, while connecting the control side of the drawstring pressure compensator to the tank line, is supplied in each case by energizing the proportional solenoid of the lifting proportional control valve or the lowering proportional Energized so that it separates the load pressure signal circuit from the tank line and at the same time switches the branching off from the drain line control line to the control side of the pressure compensator in the positive sequence. The safety valve has the task to ensure that a load neither sinks nor is raised further uncontrolled when the lifting proportional control valve or the lowering proportional control valve or its pressure compensator. This complies with DIN / ISO regulations for the safety of industrial trucks. These regulations also require a shutdown of the flow from the pressure source in the event that, for example, the pressure source further promotes, for example, because it has stuck on the control side or a driver accidentally gives a promotion command. This could cause, for example, a further lifting of the load despite the influence of the safety valve. In order to meet these requirements, in practice in the known lifting module between the pressure source and the lifting module, a magnet-operated 2/2-way valve is arranged separately, with which the flow of the pressure source can be switched off. This 2/2 solenoid valve is difficult to accommodate in a confined space and means considerable expense only for the shutdown function.

Aus EP 2466155 A1 ist ein entsperrbares Rückschlagventil, insbesondere auch für Hubmodule, bekannt, das ein sehr großes Aufsteuerdruckverhältnis hat und gegebenenfalls sogar mit Vorentlastung entsperrbar ist. Das entsperrbare Rückschlagventil ist in einem Einschraubgehäuse untergebracht, das nach Art eines Ermeto-Einschraubgehäuses ausgebildet sein kann und deshalb bequem in der Anschlussbohrung beispielsweise einer Druckquelle unterbringbar ist.Out EP 2466155 A1 is a pilot-operated check valve, especially for lifting modules, known, which has a very large Aufsteuerdruckverhältnis and possibly even with pre-relief is unlocked. The pilot-operated check valve is housed in a Einschraubgehäuse, which may be designed in the manner of an Ermeto screw-in housing and therefore conveniently in the connection bore, for example, a pressure source can be accommodated.

EP 0546300 A1 offenbart einen Hubmodul eines Flurförderfahrzeugs, in welchem das Hebe-Proportional-Steuerventil Teil eines Dreiwege-Stromreglers ist, das sind dessen 3/2-Wege-Druckwaage direkt an die von der Druckwelle gespeiste Druckleitung angeschlossen ist. Von dieser Druckwaage führt über ein Rückschlagventil eine Arbeitsleitung zu weiteren, aus derselben Druckquelle gespeisten Verbrauchern. Die 3/2-Wege-Druckwaage als Teil des Dreiwege-Stromreglers kann einen Förderstrom von der Druckquelle zum Hebestrang nicht zuverlässig unterbinden, falls das 2/2-Proportional-Wegeventil des Dreiwege-Stromreglers oder die Druckwaage hängen bleiben sollten. In einem solchen Störungsfall würde der einseitig beaufschlagte Hydroverbraucher die Last anheben. EP 0546300 A1 discloses a lift module of an industrial truck in which the lift proportional control valve is part of a three-way flow regulator, that is its 3/2-way pressure compensator is connected directly to the pressure line fed by the pressure wave. From this pressure compensator via a check valve performs a working line to further, fed from the same pressure source consumers. The 3/2-way pressure compensator as part of the three-way flow regulator can not reliably prevent a flow from the pressure source to the lifting string if the 2/2-way proportional valve of the 3-way flow regulator or the pressure compensator should become stuck. In such a malfunction case, the unilaterally acted hydraulic consumer would lift the load.

Der Erfindung liegt die Aufgabe zugrunde, ein Hubmodul der eingangs genannten Art mit einer baulich einfachen, funktionssicheren und platzsparenden Abschaltvorrichtung für den Förderstrom der Druckquelle anzugeben, um geltende Vorschriften zu Sicherheit von Flurförderfahrzeugen zu erfüllen.The invention is based on the object, a lifting module of the type mentioned with a structurally simple, functionally reliable and space-saving shut-off device for the flow indicate the pressure source in order to comply with applicable regulations on the safety of industrial trucks.

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

Die am oder im Hubmodul vorgesehene Abschaltvorrichtung für den Förderstrom der Druckquelle benötigt keinen Magneten und spricht selbständig auf den Steuerdruck im Lastdrucksignalkreis an. Die Abschaltvorrichtung weist entweder ein aus dem Lastdrucksignalkreis hydraulisch entsperrbares Rückschlagventil auf. Solange der Lastdrucksignalkreis ein Lastdrucksignal führt, wird das Rückschlagventil entsperrt, so dass die Druckleitung beaugschlasgt werden kann. Hingegen sperrt das Rückschlagventil bei Fehlen eines Signaldrucks im Lastdrucksignalkreis. Andernfalls weist die Abschaltvorrichtung ein druckvorgesteuertes 3/2-Wege-Prioritätsventil auf. Das Prioritätsventil lässt bei Fehlen eines Signaldrucks den Lastdrucksignalkreis den Prioritäts-Hydro-Verbraucher steuern, verhindert aber, dass dann der Förderstrom von der Druckquelle in die Druckleitung eingespeist wird. Dank der Einflussnahme der Abschaltvorrichtung gelangt der Förderstrom der Druckquelle nicht mehr zur Druckleitung, und zu dem daran direkt angeschlossenem Hebe-Proportional-Steuerventil, so dass selbst bei hängengebliebenem Hebe-Proportional-Steuerventil die Last nicht unkontrolliert angehoben werden kann. Allerdings sind mit dem entsperrbaren Rückschlagventil weitere an die Druckleitung angeschlossene Verbraucher dann ebenfalls nicht mehr steuerbar. Ist hingegen ein Prioritäts-Verbraucher, wie beispielsweise eine hydraulische Lenkung des Flurförderfahrzeugs, getrennt von der Druckleitung aus der Druckquelle speisbar, dann bleibt dieser Prioritäts-Hydroverbraucher trotz des Ansprechens der Abschaltvorrichtung über das §/2-Wege-Prioritätsventil weiterhin steuerbar.The provided on or in the lifting module disconnecting device for the flow of the pressure source requires no magnet and speaks independently to the control pressure in the load pressure signal circuit. The shutdown device has either one of the load pressure signal circuit hydraulically releasable check valve. As long as the load pressure signal circuit carries a load pressure signal, the check valve is unlocked, so that the pressure line can be beaugschlasgt. On the other hand, the check valve locks in the absence of a signal pressure in the load pressure signal circuit. Otherwise, the shutdown on a pressure-controlled 3/2-way priority valve. In the absence of a signal pressure, the priority valve allows the load pressure signal circuit to control the priority hydro-consumer, but prevents the delivery flow from the pressure source from being fed to the pressure line. Thanks to the intervention of the cut-off device, the flow of the pressure source no longer reaches the pressure line and the directly connected proportional control valve, so that even with the lifting proportional control valve stuck, the load can not be lifted uncontrollably. However, with the pilot-operated check valve further connected to the pressure line consumer then also no longer controllable. However, if a priority consumer, such as a hydraulic steering of the industrial truck, separated from the pressure line from the pressure source fed, then this priority hydraulic consumer remains despite the response of the shutdown device via the § / 2-way priority valve continues to be controlled.

Zweckmäßig ist die Abschaltvorrichtung entweder auf eine OC-Funktion oder eine CC-Funktion ausgelegt. Eine OC-Funktion ist typischerweise bei Verwendung einer Konstantpumpe gegeben, während eine CC-Funktion bei Einsatz einer Verstellpumpe gegeben ist. Wenn also von vornherein feststeht, dass der Anwender nur eine OC-Funktion oder nur eine CC-Funktion wünscht, kann der Hubmodul von vornherein darauf abgestimmt sein. Noch zweckmäßiger ist jedoch der Hubmodul wahlweise zwischen der OC-Funktion und der CC-Funktion umstellbar, so dass der Anwender frei wählen kann, für welche Funktion er den Hubmodul einsetzt. Diese Ausführungsform erweitert den Einsatzbereich des Hubmoduls in universeller Weise.Suitably, the shutdown device is designed for either an OC function or a CC function. An OC function is typically given when using a constant displacement pump, while a CC function is given when using a variable displacement pump. So if it is clear from the outset that the user wants only an OC function or only a CC function, the lifting module can be tuned to it right from the start. More expediently, however, the lifting module is optionally convertible between the OC function and the CC function, so that the user can freely choose the function for which he uses the lifting module. This embodiment extends the field of application of the lifting module in a universal manner.

Bei einer weiteren Ausführungsform, bei der ein von der Druckquelle getrennt von der Druckleitung speisbarer Prioritäts-Hydroverbraucher an den Hubmodul angeschlossen ist, ist der Prioritäts-Hydroverbraucher permanent steuerbar.In a further embodiment in which a priority hydraulic consumer, which can be fed separately from the pressure source, is connected to the lifting module, the priority hydraulic consumer can be permanently controlled.

Es kann zweckmäßig sein, wenn die Abschaltvorrichtung zwischen der Druckleitung und der Tankleitung zusätzlich zum Prioritätsventil oder dem entsperrbaren Rückschlagventil einen Druckwaagen-Schieber oder ein 2/2-Wege-Sitzventil aufweist. Damit bleibt die Druckleitung nach erfolgter Abschaltung drucklos, während der Prioritäts-Hydroverbraucher weiterhin steuerbar ist.It may be expedient if the shutdown device between the pressure line and the tank line in addition to the priority valve or the pilot-operated check valve has a pressure compensator slide or a 2/2-way seat valve. Thus, the pressure line remains unpressurized after the shutdown, while the priority hydro consumer is still controllable.

Bei der umstellbaren Ausführungsform des Hubmoduls ist es zweckmäßig, am 2/2-Wege-Druckwaagenschieber oder am 2/2-Wege-Sitzventil zu dessen gewollter Passivierung einen mechanisch verstellbarer Anschlag vorzusehen. Der Anschlag sichert die Absperrstellung und kann nach Bedarf benutzt werden. Ist von vornherein klar, dass nur eine CC-Funktion gewünscht wird, kann der Druckwaagenschieber oder das Sitzventil auch weggelassen werden.In the convertible embodiment of the lifting module, it is expedient to provide a mechanically adjustable stop on the 2/2-way pressure compensator slide or on the 2/2-way seat valve to its intended passivation. The stop secures the shut-off position and can be used as required. If it is clear from the outset that only one CC function is desired, the pressure compensator valve or the seat valve can also be omitted.

Bei der Ausführungsform des Hubmoduls mit dem entsperrbaren Rückschlagventil ist in der Abschaltvorrichtung zwischen der Druckquelle und dem Lastdrucksignalkreis ein Steuerleitungs-Bypass mit einem zur Druckquelle sperrenden Rückschlagventil und einer Drossel stromab des Rückschlagventils vorgesehen, und zweigt zwischen dem Rückschlagventil und der Drossel eine Entsperr-Steuerdruckleitung zum entsperrbaren Rückschlagventil ab. Das entsperrbare Rückschlagventil ist zweckmäßig mit einer Vorentlastung entsperrbar, so dass relativ geringer Steuerdruck zum ordnungsgemäßen Entsperren und Offenhalten ausreicht.In the embodiment of the lifting module with the pilot operated check valve is in the shutdown between the pressure source and the load pressure signal circuit a control line bypass provided with a pressure source blocking check valve and a throttle downstream of the check valve, and branches between the check valve and the throttle an unlocking control pressure line to unlockable check valve. The pilot-operated check valve is expediently unlocked with a pre-relief, so that relatively low control pressure sufficient for proper unlocking and keeping open.

Damit das Prioritätsventil zum Heben auch die Druckleitung speist, ist zweckmäßig an einer einer Feder und einer ersten Steuerseite abgewandten zweiten Steuerseite des Prioritätsventils eine größere Druckbeaufschlagungsfläche vorgesehen als an der ersten Steuerseite.So that the priority valve for lifting also feeds the pressure line, a larger pressure application area is expediently provided at a second control side of the priority valve facing away from a spring and a first control side than at the first control side.

Bei einer Ausführungsform für den Prioritäts-Hydroverbraucher weist der Hubmodul einen Lastdrucksignal-Anschluss beispielsweise für eine Verstellpumpe auf, und einen separaten Lastdrucksignal-Anschluss des Prioritäts-Hydroverbrauchers, um diesem den jeweils optimalen Prioritätsdruck bzw. die erforderliche Menge zuzuführen. Zwischen diesen Lastdrucksignal-Anschlüssen ist im Lastdrucksignalkreis zweckmäßig ein Wechselventil angeordnet.In one embodiment for the priority hydraulic consumer, the lifting module has a load pressure signal connection, for example for a variable displacement pump, and a separate load pressure signal connection of the priority hydraulic consumer, in order to optimize the latter in each case Supply priority pressure or the required amount. Between these load pressure signal connections a shuttle valve is expediently arranged in the load pressure signal circuit.

Zweckmäßig ist der 2/2-Wege-Druckwaagenschieber oder das 2/2-Wege-Sitzventil in Aufsteuerrichtung aus der Druckleitung und in Zusteuerrichtung, parallel zu einer Feder, aus dem Lastdrucksignalkreis druckvorgesteuert.Appropriately, the 2/2-way pressure compensator valve or the 2/2-way seat valve in the direction of control from the pressure line and in Zusteuerrichtung, parallel to a spring, pressure-controlled from the load pressure signal circuit.

Das entsperrbare Rückschlagventil hat zweckmäßig ein Aufsteuerdruckverhältnis von mindestens 1:5 bis, vorzugsweise, sogar bis etwa 1:30, um das Rückschlagventil auch bei hohem Arbeitsdruck mit geringem Steuerdruck und geringer Steuerölmenge zuverlässig zu entsperren.The pilot-operated check valve has expediently a Aufsteuerdruckverhältnis of at least 1: 5 to, preferably, even to about 1:30 to unlock the check valve reliably even at high working pressure with low control pressure and low amount of control oil.

Schließlich ist es zweckmäßig, wenn das entsperrbare Rückschlagventil und der Steuerleitungsbypass mit der Entsperr-Steuerleitung in einem Einschraubgehäuse untergebracht sind, mit dem die Druckquelle an den Hubmodul angeschlossen wird. Vorzugsweise gleicht das Einschraubgehäuse einem standardisierten Ermeto-Einschraubgehäuse.Finally, it is expedient if the pilot-operated check valve and the control line bypass with the unlocking control line are accommodated in a screw-in housing with which the pressure source is connected to the lifting module. Preferably, the Einschraubgehäuse resembles a standard Ermeto screw-in.

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

Fig. 1
ein Blockschaltbild einer ersten Ausführungsform eines Hubmoduls mit Abschaltvorrichtung, in drucklosem Zustand, und
Fig. 2
ein Blockschaltbild einer weiteren Ausführungsform eines Hubmoduls mit Abschaltvorrichtung im Falle eines an den Hubmodul angeschlossenen Prioritäts-Hydroverbrauchers, in drucklosem Zustand.
Reference to the drawings, embodiments of the subject invention will be explained. Show it:
Fig. 1
a block diagram of a first embodiment of a lifting module with shutdown, in a pressureless state, and
Fig. 2
a block diagram of another embodiment of a lifting module with shutdown in the case of a connected to the lifting module priority hydraulic consumer, in a pressureless state.

In Fig. 1 ist ein strichpunktiert angedeuteter Hubmodul 1 für eine einseitig gegen einen Last steuerbaren Hydroverbraucher H eines Flurförderfahrzeugs beispielsweise als Block mit integrierten oder eingebauten Hydraulikkomponenten ausgebildet. Weitere, nicht dargestellte Hydroverbraucher des Flurförderfahrzeugs sind beispielsweise an Anschlüssen 2, 3 und 22 (Druckleitungsanschluss 2, Tankleitungsanschluss 3, Lastdrucksignalkreisanschluss 22) angeschlossen. Ferner ist ein Lastdrucksignal-Anschluss 4 vorgesehen, von welchem ein Lastdrucksignal an eine schematisch angedeutete Druckquelle Q gebracht werden kann, im Falle einer Verstellpumpe an den Pumpenregler. Schließlich sind ein Druckquellenanschluss 5 und ein Lastdrucksignalkreis 19 mit einem Anschluss 6 vorgesehen, in deren Bereich eine Abschaltvorrichtung V integriert oder angeschraubt ist, beispielsweise in Form einer Ermeto-Verschraubung 38 (Einschraubgehäuse). Ein Tankleitungsanschluss 7 ist mit dem nicht dargestellten Tank der Druckquelle verbunden.In Fig. 1 is a dot-dash line indicated lifting module 1 for a one-sided controllable against a load hydraulic consumer H of a material handling vehicle, for example, formed as a block with integrated or built-hydraulic components. Further, non-illustrated hydraulic consumers of the industrial truck are connected, for example, to terminals 2, 3 and 22 (pressure line connection 2, tank line connection 3, load pressure signal circuit connection 22). Furthermore, a load pressure signal connection 4 is provided, from which a load pressure signal can be brought to a schematically indicated pressure source Q, in the case of a variable displacement pump to the pump regulator. Finally, a pressure source connection 5 and a load pressure signal circuit 19 with a connection 6 are provided, in the region of which a switch-off device V is integrated or screwed on, for example in the form of an Ermeto screw connection 38 (screw-in housing). A tank line connection 7 is connected to the tank, not shown, of the pressure source.

Vom Anschluss 5 führt eine Arbeitsleitung 8 zu einem 2/2-Druckwaagenschieber 27, der an der Schließsteuerseite durch eine Feder 28 und aus einer vom Anschluss 6 kommenden Steuerleitung 24 eines Lastdrucksignalkreises 19 beaufschlagt ist, an der Aufsteuerseite hingegen über eine Steuerleitung 29, die an die Arbeitsleitung 8 angeschlossen ist. Als Option ist der 2/2-Wege-Druckwaagenschieber 27 mit einem manuell verstellbaren Anschlag 30 ausgestattet, um bei Bedarf passiviert zu werden (in der Sperrstellung). Zwischen der Steuerleitung 24 und der Tankleitung 10 ist ein Druckbegrenzungsventil 26 vorgesehen. Der Lastdrucksignalkreis 19 wird u.a. über eine Steuerleitung 20 aus einem Hebestrang 12 gespeist, der an eine von der Arbeitsleitung 8 abzweigende Druckleitung 9 angeschlossen ist und ein Hebe-Proportional-Steuerventil 11 und stromab desselben ein Rückschlagventil 13 enthält. Das Hebe-Proportional-Steuerventil 11 weist eine Feder 14 auf, die für die dargestellte Absperrstellung verantwortlich ist, sowie einen Proportionalmagneten 13 und, als Option, eine hydraulische Druckvorsteuerung 15. Er dient zum lastunabhängigen Steuern der Hebegeschwindigkeit des Hydroverbrauchers H.From the terminal 5 performs a working line 8 to a 2/2-pressure compensator slide 27, which is acted on the closing control side by a spring 28 and coming from a port 6 control line 24 of a load pressure signal circuit 19, on the control side, however, via a control line 29, the the working line 8 is connected. As an option, the 2/2-way pressure compensator 27 is equipped with a manually adjustable stop 30 to be passivated if necessary (in the locked position). Between the control line 24 and the tank line 10, a pressure relief valve 26 is provided. The load pressure signal circuit 19 is used i.a. supplied via a control line 20 from a lifting strand 12 which is connected to a branching from the working line 8 pressure line 9 and a lifting proportional control valve 11 and downstream of the same contains a check valve 13. The lifting proportional control valve 11 has a spring 14, which is responsible for the shut-off position shown, and a proportional solenoid 13 and, as an option, a hydraulic pressure pilot 15. It is used for load-independent control of the lifting speed of the hydraulic consumer H.

Stromab des Rückschlagventils 13 zweigt vom Hebestrang 12 ein Senkstrang 17 zur Tankleitung 10 ab, in welchem ein Senk-Proportional-Steuerventil 16 (mit der gleichen Ausstattung wie das Hebe-Proportional-Steuerventil 11) und eine 2/2-Wege-Druckwaage 18 enthalten sind. Vom Senkstrang 17 zweigt eine Steuerleitung 31 ab, die über eine Dämpfungsvorrichtung 32 mit Rückschlagventil und Drossel zur Schließsteuerseite der Druckwaage 18 führt, und zwischen der Druckwaage 18 und dem Senk-Proportional-Steuerventil 16 eine Steuerleitung 33 zur Schließsteuerseite der Druckwaage 18, wo ebenfalls eine Feder für die dargestellte Durchgangsstellung sorgt. Der Lastdrucksignalkreis 19 ist über eine Steuerleitung 25 mit der Tankleitung 10 verbunden, wobei in der Steuerleitung 25 ein 3/2-Wege-Sicherheitsventil 34 mit Magnetbetätigung (Schwarz/Weiß-Magnet 35) enthalten ist, das bei Bestromen des Proportionalmagneten 13 des Hebe-Proportional-Steuerventils 11 oder des Senk-Proportional-Steuerventils 16 bestromt wird, und dann aus der gezeigten Stellung in die obere Stellung umschaltet. Die gezeigte Stellung wird durch eine Feder 36 gehalten. In dieser Stellung sind die Steuerleitung 25 und die Aufsteuerseite der Druckwaage 18 über die Kurzschlußleitung 37 mit der Tankleitung 10 verbunden, während die vom Senkstrang 17 abzweigende Steuerleitung 33 zur Aufsteuerseite der Druckwaage 18 abgesperrt ist. In der anderen Schaltstellung wird bei Bestromen des Magneten 35 die Steuerleitung 25 von der Tankleitung 10 getrennt, und wird der Senkstrang 17 über die Steuerleitung 33 mit der Aufsteuerseite der Druckwaage 18 verbunden.Downstream of the check valve 13 branches off from the lifting strand 12 from a Senkstrang 17 to the tank line 10, in which a lowering proportional control valve 16 (with the same equipment as the lifting proportional control valve 11) and a 2/2-way pressure compensator 18 included are. From the Senkstrang 17 branches off a control line 31, which leads via a damping device 32 with check valve and throttle to Schließsteuerseite the pressure compensator 18, and between the pressure compensator 18 and the lowering proportional control valve 16, a control line 33 to the closing control side of the pressure compensator 18, where also a Spring ensures the passage position shown. The load pressure signal circuit 19 is connected via a control line 25 to the tank line 10, wherein in the control line 25, a 3/2-way safety valve 34 with magnetic actuation (black / white magnet 35) is included in the energizing the proportional solenoid 13 of the lifting Proportional control valve 11 or the lowering proportional control valve 16 is energized, and then switches from the position shown in the upper position. The position shown is held by a spring 36. In this position, the control line 25 and the control side of the pressure compensator 18 via the short-circuit line 37 to the tank line 10, while the branched off from the sunk strand 17 control line 33 is shut off to the control side of the pressure compensator 18. In the other switching position is at Bestromen the magnet 35, the control line 25 separated from the tank line 10, and the Senkstrang 17 is connected via the control line 33 to the control side of the pressure compensator 18.

Die Proportionalmagneten 13 und der Magnet 35 sind an eine übergeordnete Steuervorrichtung CU angeschlossen, die für die gleichzeitige Bestromung sorgt. Gegebenenfalls ist eine Programmroutine vorgesehen, mit der das 3/2-Wege-Sicherheitsventil 34 auch unabhängig von den Proportionalmagneten 13 hin- und hergeschaltet werden kann.The proportional magnet 13 and the magnet 35 are connected to a higher-level control device CU, which ensures the simultaneous energization. Optionally, a program routine is provided, with which the 3/2-way safety valve 34 can also be switched back and forth independently of the proportional magnet 13.

Zum Zusammenspiel zwischen den Proportional-Steuerventilen 11, 16 und dem Sicherheitsventil 34 wird auf EP 1369598 A1 verwiesen, in der die funktionellen Zusammenhänge im Detail erläutert sind.The interaction between the proportional control valves 11, 16 and the safety valve 34 is on EP 1369598 A1 referenced, in which the functional relationships are explained in detail.

Die Steuerleitung 20 ist über einen Filter und eine Drossel und einen Steuerleitungsabschnitt 23 mit der Tankleitung 10 verbunden, und führt weiter über eine Drossel zu einem Wechselventil 21 und zum Lastdrucksignal-Anschluss 4. Zum Wechselventil 21 kann über den Anschluss 22 ein Lastdrucksignal von den weiteren Verbrauchern eingespeist werden, wobei das Wechselventil 21 dafür sorgt, dass der jeweils höhere Signaldruck an den Anschluss 4 übertragen wird.The control line 20 is connected via a filter and a throttle and a control line section 23 to the tank line 10, and continues via a throttle to a shuttle valve 21 and the load pressure signal port 4. To the shuttle valve 21 can via the terminal 22, a load pressure signal from the other Consumers are fed, the shuttle valve 21 ensures that the respective higher signal pressure is transmitted to the terminal 4.

Die Abschaltvorrichtung V im Einschraubgehäuse 38 enthält z.B. vor dem Anschluss 5 in Fig. 1 ein in Richtung zur Arbeitsleitung 8 sperrendes, jedoch hydraulisch entsperrbares Rückschlagventil 39 zum Anschluss 5, sowie einen Steuerleitungs-Bypass 40 zum Anschluss 6. Im Steuerleitungsbypass 40 sind ein in Richtung zur Druckquelle Q sperrendes Rückschlagventil 41 und eine Drossel 42 enthalten, wobei zwischen dem Rückschlagventil 41 und der Drossel 42 eine Entsperr-Steuerleitung 43 zum entsperrbaren Rückschlagventil 39 führt.The disconnecting device V in Einschraubgehäuse 38 contains, for example, before the connection 5 in Fig. 1 in the direction of the working line 8 blocking, but hydraulically releasable check valve 39 to port 5, and a control line bypass 40 to port 6. In the control line bypass 40 in the direction of the pressure source Q blocking check valve 41 and a throttle 42 are included, wherein between the check valve 41 and the throttle 42 an unlock control line 43 leads to the pilot-operated check valve 39.

Wird in der gezeigten Schaltstellung des Hubmoduls 1 in Fig. 1 durch die Druckquelle Q Druckmittel gefördert, und liegt kein Signaldruck an, da das 3/2-Wege-Sicherheitsventil 34 in der gezeigten Schaltstellung ist, dann verbindet der 2/2-Druckwaagenschieber 27 die Arbeitsleitung 8 mit der Tankleitung 10, sodass die Druckleitung 9 druckentlastet wird, während das Rückschlagventil 39 sperrt. Die Druckleitung 9 wird nicht mehr druckbeaufschlagt. Da jedoch kein Signaldruck im Lastdrucksignalkreis 19 vorliegt, hält das Rückschlagventil 39 seine Sperrstellung, wie auch der 2/2-Wege-Druckwaagenschieber 27. Ein geringer Druckmittelfluss findet über den Steuerleitungsbypass 40 und das 3/2-Wege-Sicherheitsventil 34 zur Tankleitung 10 statt.Is in the illustrated switching position of the lifting module 1 in Fig. 1 promoted by the pressure source Q pressure medium, and is no signal pressure, since the 3/2-way safety valve 34 is in the switching position shown, then connects the 2/2-pressure compensator valve 27, the working line 8 with the tank line 10, so that the pressure line. 9 depressurized while the check valve 39 locks. The pressure line 9 is no longer pressurized. However, since no signal pressure in the load pressure signal circuit 19 is present, the check valve 39 keeps its blocking position, as well as the 2/2-way pressure compensator valve 27. A low pressure fluid flow takes place via the control line bypass 40 and the 3/2-way safety valve 34 to the tank line 10 ,

Wird das Hebe-Proportional-Steuerventil 11 bestromt, dann wird auch das 3/2-Wege-Sicherheitsventil 34 bestromt, so dass der Lastdrucksignalkreis 19 zur Tankleitung 10 abgesperrt wird und sich einerseits über den Steuerleitungsbypass 40 der Abschaltvorrichtung V und andererseits aus dem Hebestrang 12 Signaldruck aufbaut. Das Rückschlagventil 39 wird entsperrt und beaufschlagt die Druckleitung 9. Der Hydroverbraucher H wird gegen die Last angehoben. Wird das Hebe-Proportional-Steuerventil 11 wieder stromlos geschaltet, wie auch der Magnet 35, wird die Last über das Rückschlagventil 13 und das Senk-Proportional-Steuerventil 16 gehalten. Wird die Hebebewegung unterbrochen, d.h. der Proportionalmagnet 13 des Hebe-Proportional-Steuerventils 11 stromlos geschaltet, wird auch der Magnet 35 stromlos geschaltet, und der Lastdrucksignalkreis 19 entlastet. Gleichzeitig schaltet die Abschaltvorrichtung V um, d.h. das Rückschlagventil 39 sperrt von der Druckquelle Q zur Arbeitsleitung 8 ab. Die Abschaltvorrichtung V wird jeweils dann aktiv (Rückschlagventil 39 sperrt), wenn keiner der Proportionalmagneten 13 bzw. der Magnet 35 bestromt wird. Die Senksteuerung bleibt jederzeit möglich.If the lifting proportional control valve 11 is energized, then the 3/2-way safety valve 34 is energized, so that the load pressure signal circuit 19 is shut off to the tank line 10 and on the one hand via the control line bypass 40 of the shutdown device V and on the other hand from the lifting strand 12th Signal pressure builds up. The check valve 39 is unlocked and acts on the pressure line 9. The hydraulic consumer H is raised against the load. When the lift proportional control valve 11 is de-energized, as well as the solenoid 35, the load is held by the check valve 13 and the lowering proportional control valve 16. If the lifting movement is interrupted, i. the proportional solenoid 13 of the lifting proportional control valve 11 is de-energized, and the magnet 35 is de-energized, and the load pressure signal circuit 19 relieved. At the same time, the shutdown device V switches over, i. the check valve 39 blocks from the pressure source Q to the working line 8 from. The shutdown device V is then active (check valve 39 blocks) when none of the proportional solenoid 13 and the magnet 35 is energized. The lowering control remains possible at any time.

Wird das Senk-Proportional-Steuerventil 16 bestromt, wird auch der Magnet 35 wieder bestromt, so dass sich Signaldruck im Lastdrucksignalkreis 19 aufbaut und der Hydroverbraucher H unter der Last einfährt.If the lowering proportional control valve 16 is energized, the magnet 35 is also energized again, so that signal pressure builds up in the load pressure signal circuit 19 and the hydraulic consumer H moves under the load.

Für eine CC-Funktion mit einer Verstellpumpe als Druckquelle Q wird der Anschlag 30 so eingestellt, dass der 2/2-Wege-Druckwaagenschieber 27 in der Sperrstellung bleibt. Für eine CC-Funktion könnte der 2/2-Wege-Druckwaagenschieber 27 sogar weggelassen werden. Für eine CO-Funktion bleibt der Anschlag passiv.For a CC function with a variable displacement pump as the pressure source Q, the stop 30 is adjusted so that the 2/2-way pressure compensator valve 27 remains in the blocking position. For a CC function, the 2/2-way pressure compensator 27 could even be omitted. For a CO function, the attack remains passive.

Bei der Ausführungsform des Hubmoduls 1 in Fig. 2 ist neben weiteren, nicht gezeigten Verbrauchern, die an den Anschlüssen 2, 3 und 22 angeschlossen sind, und dem Hydroverbraucher H, ein Prioritäts-Hydroverbraucher Cf an das Hubmodul 1 angeschlossen, der mit Druckmittel getrennt von der Druckleitung G aus der Druckquelle Q versorgt wird. Der Prioritäts-Hydroverbraucher Cf ist beispielsweise eine hydraulische Lenkung des Flurförderfahrzeuges. Von dieser hydraulischen Lenkung ist auch eine Verbindung zu einem Signaldruckanschluss 46 gegeben. Die Abschaltvorrichtung V enthält, z.B. im Block des Hubmoduls, ein 3/2-Wege-Prioritätsventil 48.In the embodiment of the lifting module 1 in Fig. 2 is next to other consumers, not shown, which are connected to the terminals 2, 3 and 22, and the hydraulic consumer H, a priority hydro consumer Cf connected to the lifting module 1, which is supplied with pressure medium separated from the pressure line G from the pressure source Q. , The priority hydraulic consumer Cf is, for example, a hydraulic steering of the industrial truck. From this hydraulic steering connection to a signal pressure port 46 is also given. The shutdown device V contains, for example in the block of the lifting module, a 3/2-way priority valve 48th

Im Lastdrucksignalkreis 19 ist die Steuerleitung 20 vom Wechselventil 21 über ein Wechselventil 45 wahlweise mit dem Signaldruck-Anschluss 46 oder 4 verbindbar. Der Prioritäts-Hydroverbraucher Cf ist an eine Arbeitsleitung 47 angeschlossen, die zu dem 3/2-Prioritätsventil 48 zwischen der Arbeitsleitung 8 und der Druckleitung 9 führt. Von der Arbeitsleitung 47 zweigen Steuerleitungen 49 einerseits zur Steuerleitung 25 und zu einer zweiten Steuerseite 51 des 3/2-Wege-Prioritätsventils 48 sowie zur Steuerleitung 24 und zu einer ersten Steuerseite 50 ab, an der auch die Feder 28 wirkt. Zweckmäßig ist die Beaufschlagungsfläche an der zweiten Steuerseite 51 größer als die Beaufschlagungsfläche an der ersten Steuerseite 50, so dass bei Vorliegen eines Signaldrucks im Lastdrucksignalkreis 19 das 3/2-Wege-Prioritätsventil 48 aus der gezeigten Schaltstellung umschaltet, und sowohl die Arbeitsleitung 47 als auch die Druckleitung 9 gespeist werden, wobei die Arbeitsleitung 47 Vorrang hat.In the load pressure signal circuit 19, the control line 20 from the shuttle valve 21 via a shuttle valve 45 is selectively connectable to the signal pressure port 46 or 4. The priority hydraulic consumer Cf is connected to a working line 47 leading to the 3/2 priority valve 48 leads between the working line 8 and the pressure line 9. From the working line 47 branched control lines 49 on the one hand to the control line 25 and to a second control side 51 of the 3/2-way priority valve 48 and the control line 24 and to a first control side 50 from where the spring 28 acts. Suitably, the loading surface on the second control side 51 is greater than the loading surface on the first control side 50, so that when there is a signal pressure in the load pressure signal circuit 19, the 3/2-way priority valve 48 switches from the switching position shown, and both the working line 47 and the pressure line 9 are fed, the working line 47 has priority.

Zwischen der Druckleitung 9 und der Rücklaufleitung 10 ist ein 2/2-Wege-Sitzventil 27' angeordnet(analoge Funktion wie der 2/2-Wege-Druckwaagenschieber 27 in Fig. 1, jedoch ohne Leckverluste), das aus der Druckleitung 9 in Aufsteuerrichtung und aus dem Lastdrucksignalkreis 19 über das Wechselventil 45, an der Schließsteuerseite parallel zur Feder 28', druckvorgesteuert ist. Das 2/2-Wege-Sitzventil 27' enthält innen eine Drossel, über die ein Schließdruck erzeugbar ist. Im Falle einer CC-Funktion kann das 2/2-Wege-Sitzventil 27' über den manuell verstellbaren Anschlag 30' passiviert werden, so dass es seine gezeigte Schließstellung hält. Bei einer OC-Funktion ist hingegen der Anschlag 30' nicht wirksam. Falls von vornherein nur eine CC-Funktion in Frage kommt, kann das Ventil 27' weggelassen werden.Between the pressure line 9 and the return line 10, a 2/2-way valve seat 27 'is arranged (analogous function as the 2/2-way pressure compensator valve 27 in Fig. 1 , but without leakage losses), which is pressure-controlled from the pressure line 9 in the up direction and from the load pressure signal circuit 19 via the shuttle valve 45, on the closing control side parallel to the spring 28 '. The 2/2-way seat valve 27 'contains inside a throttle, via which a closing pressure can be generated. In the case of a CC function, the 2/2-way seat valve 27 'can be passivated via the manually adjustable stop 30', so that it keeps its closed position shown. In an OC function, however, the stop 30 'is not effective. If only one CC function is possible from the outset, the valve 27 'can be omitted.

Funktion:Function:

In der gezeigten Schaltsituation bei nicht bestromten Proportionalmagneten 13 und nicht bestromtem Schaltmagneten 35 des 3/2-Wege-Sicherheitsventils 34 beaufschlagt die Druckquelle Q die Arbeitsleitung 8 und über die von der Feder 28 eingestellte Schaltstellung des 3/2-Wege-Prioritätsventils 48 die Arbeitsleitung 47, während die Druckleitung 9 abgesperrt und gegebenenfalls über das Sitzventil 27' druckentlastet ist. Werden die Ventile 11, 34 oder 16, 34 bestromt, baut sich im Lastdrucksignalkreis 19 Signaldruck auf, durch den das 3/2-Wege-Prioritätsventil 48 in eine Regelstellung schaltet, da die größere Druckbeaufschlagungsfläche an der zweiten Steuerseite 51 bei gleichen Steuerdrücken eine Kraft generiert, die die Feder 28 überwindet, so dass der Druck in der Arbeitsleitung 47 wie auch der Druck in der Druckleitung 9 geregelt werden. Ein Hebevorgang wird wie in Fig. 1 gesteuert. Ein Senkvorgang ist jederzeit möglich. Die Abschaltvorrichtung V wird dann aktiv, wenn kein Hebevorgang gesteuert wird, in dem dann das 3/2-Wege-Prioritätsventil 48 die in Fig. 2 gezeigte Schaltstellung hält. Die Druckleitung 9 bleibt drucklos, wobei zuvor das 2/2-Wege-Sitzventil 27' bei Wegfallen des Signaldrucks die Druckleitung 9 zur Tankleitung 10 entlastet haben kann. Liegt Signaldruck im Lastdrucksignalkreis 19 vor, trennt das 2/2-Wege-Sitzventil
27' hingegen die Druckleitung 9 von der Tankleitung 10. In beiden Ausführungsformen können Manometer an den Hubmodul 1 angeschlossen werden.In the switching situation shown in non-energized proportional solenoid 13 and non-energized solenoid 35 of the 3/2-way safety valve 34 pressurizes the pressure source Q the working line 8 and set by the spring 28 switching position of the 3/2-way priority valve 48, the working line 47, while the pressure line 9 is shut off and optionally via the seat valve 27 'relieved of pressure. When the valves 11, 34 or 16, 34 are energized, 19 signal pressure builds up in the load pressure signal circuit, through which the 3/2-way priority valve 48 switches to a control position, since the larger pressurization surface on the second control side 51 at the same control pressures a force generated, which overcomes the spring 28, so that the pressure in the working line 47 as well as the pressure in the pressure line 9 are regulated. A lifting process will be like in Fig. 1 controlled. A lowering process is possible at any time. The shutdown device V is then active when no lifting operation is controlled, in which then the 3/2-way priority valve 48, the in Fig. 2 shown switching position holds. The pressure line 9 remains unpressurized, previously the 2/2-way valve seat 27 'may have relieved the pressure line 9 to the tank line 10 when the signal pressure drops. If signal pressure is present in the load pressure signal circuit 19, the 2/2-way seat valve separates
27 ', however, the pressure line 9 from the tank line 10. In both embodiments, pressure gauges can be connected to the lifting module 1.

Claims (11)

  1. A lifting module (1) for a hydraulic consumer, which may be acted upon on one side against a load from a pressure conduit (9), which is connected to a pressure source (Q) and leads to at least one hydraulic consumer (H), (Cf), of a forklift truck with a lifting-proportional control valve (11) in a lifting line (12), connected to the pressure conduit (9), and a lowering-proportional control valve (16) in a lowering line, connected to a tank conduit (10), a load pressure signal circuit connected at least to the lifting line (12) downstream of the lifting-proportional control valve (11) and a magnetically actuated 4/2 safety valve (34) between the load pressure signal circuit (19) and the tank conduit (10), which, when energised, separates the load pressure signal circuit (19) from the tank conduit (10) and simultaneously connects an opening side of a pressure compensator (18) of the lowering-proportional control valve (16) to the lowering line (17) and, when not energised, connects the load pressure signal circuit (19) to the tank conduit and the opening side of the pressure compensator (18) to the tank circuit (10) and simultaneously separates the lowering line (17) from the opening side of the pressure compensator (18), characterised in that provided between the pressure source (Q) and the pressure conduit (19) there is a switch-off device (V), which responds purely hydraulically and in dependence on the load pressure in the load pressure signal circuit (19), for a conveyed flow produced by the pressure source (Q) to the lifting-proportional control valve (11) and that the switch-off device (V) includes either a non-return valve (39), which may be unlocked hydraulically with control pressure, or a pressure pilot-controlled 3/2-way priority valve (48), which in each case, when not acted on by control pressure, blocks in the flow direction to the pressure conduit (9).
  2. A lifting module as claimed in Claim 1, characterised in that the switch-off device (V) is designed either for an OC function for a constant displacement pump as the pressure source (Q), preferably a gear pump, or for a CC function for a variable displacement pump as the pressure source (Q) or is switchable over between an OC function and a CC function.
  3. A lifting module as claimed in Claim 1, characterised in that a priority hydraulic consumer (Cf), which may be supplied from the pressure source (Q) separately from the pressure conduit (9), is connected via the pressure pilot-controlled 3/2-way priority valve (48) to the lifting module (1).
  4. A lifting module as claimed in Claim 1, characterised in that the switch-off device (V) between the pressure conduit (9) and the tank conduit (10) includes a pressure compensator slide valve (27) or a 2/2-way poppet valve (27') in addition to the hydraulically unlockable non-return valve (39) or the 3/2-way priority valve (48).
  5. A lifting module as claimed in Claim 4, characterised in that for the purpose of switching over the switch-off device (V) between an OC function and a CC function, a mechanically adjustable abutment (30, 30') is provided on the 2/2-way pressure compensator slide valve (27) or on the 2/2 poppet valve (27') to passivate it.
  6. A lifting module as claimed in Claim 1, characterised in that a control conduit bypass (40) with a non-return valve (41) blocking towards the pressure source (Q) and a throttle (42) downstream of the non-return valve (41) is provided in the switch-off device, including the hydraulically unlockable non-return valve (39), between the pressure source (Q) and the load pressure signal circuit (19) and that branching off between the non-return valve (41) and the throttle (42) there is an unlocking control pressure conduit (43) to the unlockable non-return valve (39), which is unlockable preferably with pilot relief.
  7. A lifting module as claimed in Claim 1, characterised in that the 3/2-way priority valve (48) has a larger control pressure impingement area on a second control side (51) directed away from a spring (28) and a first control side (50) than on the first control side (50).
  8. A lifting module as claimed in Claim 1, characterised in that the lifting module (1) includes a load pressure signal connection (4) for the load pressure signal circuit (19) and a separate load pressure signal circuit connector (46) for a priority consumer (Cf), arranged between which there is, preferably, a shuttle valve (45).
  9. A lifting module as claimed in Claim 4, characterised in that the 2/2-way pressure compensator slide valve (27) or the 2/2-way poppet valve (27') is pressure pilot-controlled in the opening direction from the pressure conduit (9) and in the closing direction parallel to a spring (28, 28') from the load pressure signal circuit (19).
  10. A lifting module as claimed in Claim 1, characterised in that the hydraulically unlockable non-return valve (19) has an opening pressure ratio of at least 1:5 to, preferably, 1:13.
  11. A lifting module as claimed in Claim 6, characterised in that the unlockable non-return valve (39) and the control conduit bypass (40) with the unlocking control pressure conduit (43) are accommodated in a screw-in housing (38), with which the pressure source (Q) is connected to the lifting module (1) via a hose or a conduit (44), preferably in an Ermeto screw-in housing.
EP14180521.8A 2014-08-11 2014-08-11 Lifting module Not-in-force EP2985473B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14180521.8A EP2985473B1 (en) 2014-08-11 2014-08-11 Lifting module

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14180521.8A EP2985473B1 (en) 2014-08-11 2014-08-11 Lifting module

Publications (2)

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EP2985473A1 EP2985473A1 (en) 2016-02-17
EP2985473B1 true EP2985473B1 (en) 2017-10-11

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EP14180521.8A Not-in-force EP2985473B1 (en) 2014-08-11 2014-08-11 Lifting module

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016124504A1 (en) * 2016-12-15 2018-06-21 Jungheinrich Aktiengesellschaft Lifting device for an industrial truck and such a truck

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140409A1 (en) * 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De ELECTROHYDRAULIC CONTROL DEVICE
DE20208577U1 (en) 2002-06-03 2003-12-11 Hawe Hydraulik Gmbh & Co. Kg Electro-hydraulic lift control device for industrial trucks
EP2466155B1 (en) 2010-12-15 2013-02-13 HAWE Hydraulik SE Hydraulically unlocked return-seat valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
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