EP2985473B1 - Module de levage - Google Patents

Module de levage 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
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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
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German (de)
English (en)
Other versions
EP2985473A1 (fr
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
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Hawe Hydraulik SE
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Publication date
Application filed by Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP14180521.8A priority Critical patent/EP2985473B1/fr
Publication of EP2985473A1 publication Critical patent/EP2985473A1/fr
Application granted granted Critical
Publication of EP2985473B1 publication Critical patent/EP2985473B1/fr
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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)

Claims (11)

  1. Module de levage (1) pour un consommateur hydraulique (H) pouvant être alimenté d'un côté contre une charge d'une conduite de pression (9) menant vers au moins un consommateur hydraulique (H), (Cf), reliée à une source de pression (Q) d'un chariot élévateur, avec une soupape de commande proportionnelle de levage (11) dans un brin de levage (12) raccordé à la conduite de pression (9) et une soupape de commande proportionnelle d'abaissement (16) dans un brin d'abaissement raccordé à une conduite de réservoir (10), un circuit de signal de pression de charge raccordé au moins au brin de levage (12) en aval de la soupape de commande proportionnelle de levage (11), et une soupape de sécurité 4/2 (34) actionnée magnétiquement entre le circuit de signal de pression de charge (19) et la conduite de réservoir (10) qui sépare sous tension le circuit de signal de pression de charge (19), de la conduite de réservoir (10) et relie simultanément un côté de commande d'ouverture d'une balance de pression (18) de la soupape de commande proportionnelle d'abaissement (16) au brin d'abaissement (17), et relie hors tension le circuit de signal de pression de charge (19) à la conduite de réservoir et le côté de commande d'ouverture de la balance de pression (18) à la conduite de réservoir (10), et sépare simultanément le brin d'abaissement (17), du côté de commande d'ouverture de la balance de pression (18), caractérisé en ce qu'un dispositif de coupure (V) répondant purement hydrauliquement et dépendant de la pression de charge dans le circuit de signal de pression de charge (19) pour un courant de refoulement généré par la source de pression (Q) vers la soupape de commande proportionnelle de levage (11) est prévu entre la source de pression (Q) et la conduite de pression (9), et en ce que le dispositif de coupure (V) présente un clapet antiretour (39) déverrouillable hydrauliquement avec la pression de commande ou une soupape de priorité à 3/2 voies précommandée par pression (48) qui ne bloque pas respectivement par sollicitation de pression de commande dans le sens d'écoulement à la conduite de pression (9).
  2. Module de levage selon la revendication 1, caractérisé en ce que le dispositif de coupure (V) est conçu sur une fonction OC pour une pompe à cylindrée constante comme source de pression (Q), de préférence une pompe à roue dentée, ou sur une fonction CC pour une pompe à cylindrée variable comme source de pression (Q) ou peut être changé entre une fonction OC et une fonction CC.
  3. Module de levage selon la revendication 1, caractérisé en ce qu'un consommateur hydraulique (Cf) de priorité pouvant être alimenté par la source de pression (Q) séparément de la conduite de pression (9) est raccordé par la soupape de priorité à 3/2 voies (48) précommandée par pression au module de levage (1).
  4. Module de levage selon la revendication 1, caractérisé en ce que le dispositif de coupure (V) présente entre la conduite de pression (9) et la conduite de réservoir (10), outre le clapet antiretour (29) déverrouillable hydrauliquement ou la soupape de priorité à 3/2 voies (48), un coulisseau de balance de pression (27) ou une soupape de siège à 2/2 voies (27').
  5. Module de levage selon la revendication 4, caractérisé en ce que pour le changement du dispositif de coupure (V) entre une fonction OC et une fonction CC, une butée (30, 30') réglable mécaniquement est prévue sur le coulisseau de balance de pression à 2/2 voies (27) ou sur la soupape de siège à 2/2 voies (27') pour sa passivation.
  6. Module de levage selon la revendication 1, caractérisé en ce que dans le dispositif de coupure (V) présentant le clapet antiretour (39) déverrouillable hydrauliquement entre la source de pression (Q) et le circuit de signal de pression de charge (19), une dérivation de conduite de commande (40) est prévue avec un clapet antiretour (41) verrouillant vers la source de pression (Q) et un étranglement (42) en aval du clapet antiretour (41), et en ce qu'entre le clapet antiretour (41) et l'étranglement (42), une conduite de pression de commande de déverrouillage (43) diverge du clapet antiretour (39) déverrouillable qui est déverrouillable de préférence avec une prédécharge.
  7. Module de levage selon la revendication 1, caractérisé en ce que la soupape de priorité à 3/2 voies (48) présente sur un ressort (28) et un second côté de commande (51) éloigné du premier côté de commande (50) une plus grande surface d'alimentation de pression de commande que sur le premier côté de commande (50).
  8. Module de levage selon la revendication 1, caractérisé en ce que le module de levage (1) présente un raccordement de signal de pression de charge (4) du circuit de signal de pression de charge (19) et un raccordement de signal de pression de charge (46) séparé d'un consommateur de priorité (Cf), entre lesquels une soupape à deux voies (45) est de préférence agencée.
  9. Module de levage selon la revendication 4, caractérisé en ce que le coulisseau de balance de pression à 2/2 voies (27) ou la soupape de siège à 2/2 voies (27') est précommandé respectivement en pression dans le sens de commande d'ouverture depuis la conduite de pression (9) et dans le sens de commande de fermeture parallèlement à un ressort (28, 28') depuis le circuit de signal de pression de charge (19).
  10. Module de levage selon la revendication 1, caractérisé en ce que le clapet antiretour (39) déverrouillable hydrauliquement présente un rapport de pression de commande d'ouverture d'au moins 1:5 à de préférence 1:30.
  11. Module de levage selon la revendication 6, caractérisé en ce que le clapet antiretour déverrouillable (39) et la dérivation de conduite de commande (40) sont logés avec la conduite de pression de commande de déverrouillage (43) dans un boîtier de vissage (38), avec lequel la source de pression (Q) est raccordée par un tuyau ou une conduite (44) au module de levage (1), de préférence dans un boîtier d'inscription d'Erméto.
EP14180521.8A 2014-08-11 2014-08-11 Module de levage Not-in-force EP2985473B1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102016124504A1 (de) * 2016-12-15 2018-06-21 Jungheinrich Aktiengesellschaft Hubvorrichtung für ein Flurförderzeug sowie ein solches Flurförderzeug

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Publication number Priority date Publication date Assignee Title
DE4140409A1 (de) * 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Elektrohydraulische steuereinrichtung
DE20208577U1 (de) 2002-06-03 2003-12-11 Hawe Hydraulik Gmbh & Co. Kg Elektrohydraulische Hubsteuervorrichtung für Flurförerfahrzeuge
EP2466155B1 (fr) 2010-12-15 2013-02-13 HAWE Hydraulik SE Soupape à siège anti-retour déverrouillable de manière hydraulique

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