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
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EP
European Patent Office
Prior art keywords
pressure
valve
lifting module
control
conduit
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.)
Active
Application number
EP14180521.8A
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German (de)
French (fr)
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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
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Hawe Hydraulik SE
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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
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/004Fluid pressure supply failure
    • BPERFORMING OPERATIONS; TRANSPORTING
    • B66HOISTING; LIFTING; HAULING
    • B66FHOISTING, 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
    • B66F9/00Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06Devices 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
    • B66F9/075Constructional features or details
    • B66F9/20Means for actuating or controlling masts, platforms, or forks
    • B66F9/22Hydraulic devices or systems
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30505Non-return valves, i.e. check valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/30525Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053In combination with a pressure compensating valve
    • F15B2211/3055In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/3056Assemblies of multiple valves
    • F15B2211/30565Assemblies 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/32Directional control characterised by the type of actuation
    • F15B2211/327Directional control characterised by the type of actuation electrically or electronically
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/35Directional control combined with flow control
    • F15B2211/351Flow control by regulating means in feed line, i.e. meter-in control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/35Directional control combined with flow control
    • F15B2211/353Flow control by regulating means in return line, i.e. meter-out control
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/405Flow control characterised by the type of flow control means or valve
    • F15B2211/40523Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053Flow control characterised by the type of flow control means or valve with flow dividers using valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/40Flow control
    • F15B2211/415Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/505Pressure control characterised by the type of pressure control means
    • F15B2211/50563Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572Pressure 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/50Pressure control
    • F15B2211/575Pilot pressure control
    • F15B2211/5756Pilot pressure control for opening a valve
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76Control of force or torque of the output member
    • F15B2211/761Control of a negative load, i.e. of a load generating hydraulic energy
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/80Other types of control related to particular problems or conditions
    • F15B2211/86Control during or prevention of abnormal conditions
    • F15B2211/863Control during or prevention of abnormal conditions the abnormal condition being a hydraulic or pneumatic failure
    • F15B2211/8633Pressure source supply failure

Description

  • The invention relates to a lifting module according to the preamble of claim 1.
  • 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.
  • 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 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 stated object is achieved with the features of claim 1.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 ,
  • 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.
  • 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.
  • 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.
  • 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
  • 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.
  • 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.
  • Function:
  • 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 Active 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

Family

ID=51298653

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EP14180521.8A Active EP2985473B1 (en) 2014-08-11 2014-08-11 Lifting module

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EP (1) EP2985473B1 (en)

Families Citing this family (1)

* 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
Title
None *

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