EP3936470B1 - Entraînement de levage hydraulique d'une machine de travail mobile - Google Patents

Entraînement de levage hydraulique d'une machine de travail mobile Download PDF

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Publication number
EP3936470B1
EP3936470B1 EP21181370.4A EP21181370A EP3936470B1 EP 3936470 B1 EP3936470 B1 EP 3936470B1 EP 21181370 A EP21181370 A EP 21181370A EP 3936470 B1 EP3936470 B1 EP 3936470B1
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EP
European Patent Office
Prior art keywords
pressure compensator
pressure
line
control
lifting drive
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EP21181370.4A
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German (de)
English (en)
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EP3936470A1 (fr
Inventor
Markus Schwab
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STILL GmbH
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STILL GmbH
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    • 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

Definitions

  • the invention relates to a hydraulic lifting drive of a mobile working machine, in particular an industrial truck, for raising and lowering a load handling device, the lifting drive having a lifting cylinder device and a control valve for controlling the lowering operation of the lifting drive, which is connected to a consumer line leading to the lifting cylinder device and to a consumer line leading to a connected to the tank line that runs from the tank, with an outflow pressure compensator being arranged in the tank line that runs from the control valve to the tank, which pressure compensator is influenced by a spring device and the pressure present in the tank line between the control valve and the outflow pressure compensator in the direction of a flow position and by the pressure in the consumer line Pressure is applied in the direction of a blocking position.
  • a load handling device For handling loads, industrial trucks are provided with a load handling device, which is generally formed by a lifting carriage that can be raised and lowered on the mast and an attachment attached thereto.
  • the attachment can be designed, for example, as a load fork consisting of forks, by means of which a load, for example a pallet, can be driven under.
  • the deflection of the control valve in lowering mode determines the lowering speed of the load-carrying device.
  • a legally prescribed limit value of 0.6 m/s is prescribed for a maximum lowering speed of the load handling device or a load.
  • the control valve is actuated into an open position.
  • the discharge pressure compensator is connected in series with the control valve. When the control valve opens, a sink volume flow begins to flow from the lifting cylinder device to the container via the control valve and the outflow pressure compensator, and the load handling device is lowered.
  • the maximum flow rate for lowering of the load handling device is limited by the adjustment of the discharge pressure compensator.
  • the pressure in the consumer line upstream of the control valve acts on the discharge pressure compensator on one side in the direction of a blocking position, and the spring force of the spring device and the pressure in the tank line between the control valve and the discharge pressure compensator and thus the pressure downstream on the other side in the direction of a flow position the control valve.
  • the sink volume flow increases until a maximum pressure drop of 4 bar, for example, occurs at the control valve, which corresponds to the spring force of the discharge pressure compensator.
  • the discharge pressure compensator goes into the control position and moves in the direction of the blocking position until this pressure drop of 4 bar, for example, is kept constant at the control valve.
  • the object of the present invention is to provide a lifting drive of the type mentioned at the outset, in which higher lowering speeds of the load-carrying means can be achieved in a simple manner at low load pressures.
  • this object is achieved in that a line leading to the container is connected to the container line between the control valve and the discharge pressure compensator another container line is connected, in which a pressure compensator is arranged, which is acted upon by a spring device in the direction of a flow position and by the pressure present in the consumer line in the direction of a blocking position, the spring device of the pressure compensator being set to a limit load pressure of the lifting drive, so that in lowering operation of the lifting drive below the limit load pressure, a lowering volume flow flowing out of the lifting drive flows out via the outlet pressure compensator and the pressure compensator into the container and in lowering operation of the lifting drive above the limit load pressure a lowering volume flow outflowing from the lifting drive flows out exclusively via the outflow pressure compensator into the container.
  • the idea according to the invention is therefore to arrange a pressure compensator parallel to the discharge pressure compensator and to set the pressure compensator to a load limit pressure up to which the pressure compensator is open, so that when the lifting drive is lowering below the load limit pressure, a lowering volume flow flowing out of the lifting drive via the discharge pressure compensator and the pressure compensator can flow into the container.
  • the discharge pressure compensator and the pressure compensator are connected directly after the lowering valve in the tank line or the further tank line.
  • the maximum opening cross section of the control valve can be designed and adjusted to be larger than in the case of generic control valves.
  • the pressure compensator is open up to the limit load pressure, for example a load pressure of approx. 25 bar. Up to this limit load pressure, the sink volume flow flows parallel through the pressure compensator and the discharge pressure compensator via the larger opening cross section of the control valve. In total, at load pressures up to the limit load pressure, a higher volume flow can flow from the lifting cylinder device to the container when lowering, since the dynamic pressure via the control valve, the discharge pressure compensator and the pressure compensator connected in parallel to the discharge pressure compensator is smaller. If the limit load pressure is exceeded when lowering, the load pressure closes the pressure compensator completely.
  • the discharge pressure compensator alone limits the lowering volume flow via the lowering valve.
  • an increased lowering speed of the load-carrying means can thus be achieved in a simple manner at low load pressures.
  • a throttle device in particular an orifice plate, is arranged in the container line between the control valve and the discharge pressure compensator. Since the maximum opening cross section of the control valve can be designed and set larger in the lifting drive according to the invention than in generic control valves, the result is that the same maximum volume flow at 100% lowering speed for lowering via the control valve no longer causes a pressure drop of 4 bar, for example, but causes a reduced pressure drop of, for example, 2 bar.
  • a safety device which, in a safety position, interrupts the pressure applied to the outflow pressure compensator by the pressure present between the control valve and the outflow pressure compensator and reduces the spring prestressing of the spring devices of the outflow pressure compensator and the pressure compensator.
  • the loading of the discharge pressure compensator is interrupted by the pressure present between the control valve and the discharge pressure compensator in the tank line and the spring preloads of the spring devices of the discharge pressure compensator and the pressure compensator are reduced.
  • the discharge pressure compensator and the pressure compensator can thus be actuated into the respective blocking positions even at low load pressures in the consumer line in order to stop the lowering movement of the load handling device.
  • the safety device has a first piston that is operatively connected to the spring device of the outflow pressure compensator and a second piston that is operatively connected to the spring device of the pressure compensator, the first piston and the second piston each having a direction of increasing the spring preload have the control pressure chamber acting on the spring device, a safety valve being provided to control the loading of the control pressure chamber of the first piston and the control pressure chamber of the second piston.
  • the safety valve is connected to the tank line between the control valve and the discharge pressure compensator by means of a connecting line, to the control pressure chamber of the first piston and to the control pressure chamber of the second piston by means of a control line, and to the tank by means of a discharge line.
  • the pressure present in the container line between the control valve and the discharge pressure compensator can thus be used as control pressure, which is present in the control pressure chamber of the first piston and in the control pressure chamber of the second piston, in order to preload the spring devices on the discharge pressure compensator and on to increase the pressure compensator, and by connecting the control line to the container, the control pressure chamber of the first piston and the control pressure chamber of the second piston are relieved in order to reduce the spring preload of the spring devices on the discharge pressure compensator and on the pressure compensator.
  • control line is connected to a control pressure chamber of the discharge pressure compensator that acts in the direction of the flow position.
  • the safety valve can also be used to pressurize the control pressure chamber of the outflow pressure compensator acting in the direction of the flow position with the pressure in the tank line between the control valve and the outflow pressure compensator be controlled and by connecting the control line to the tank line, the pressurization of the control pressure chamber of the discharge pressure compensator acting in the direction of the flow position is interrupted with the pressure in the tank line between the control valve and the discharge pressure compensator and the control pressure chamber of the discharge pressure compensator is relieved to the tank.
  • the safety valve connects the connection line to the control line in an operating position and the safety valve connects the control line to the container in a safety position.
  • the control pressure chamber of the discharge pressure compensator which acts in the direction of the flow position, can be pressurized with the pressure in the tank line between the control valve and the discharge pressure compensator, and the spring preload of the spring devices on the discharge pressure compensator and on the pressure compensator can be increased, and in the safety position, the pressure can be relieved Control pressure chamber of the discharge pressure compensator to the container and a reduction in the spring preloads of the spring devices on the discharge pressure compensator and on the pressure compensator can be achieved.
  • the safety valve is acted upon by a spring in the safety position and by an actuating device, in particular a switching magnet, in the operating position.
  • an actuating device in particular a switching magnet
  • the invention has a number of advantages.
  • the parallel connection of the discharge pressure compensator and the pressure compensator makes it possible to increase the lowering speed of the load handling device with and without partial load, especially in the free lift of a mast, with little additional construction work. As a result, an increase in the handling capacity of the working machine can be achieved.
  • FIG 1 is a schematic structure of a hydraulic lifting drive 1 according to the invention of a mobile working machine, not shown in detail, for example an industrial truck.
  • the elevating drive 1 has a mast 2 on which a lifting device 3 is arranged such that it can be raised and lowered.
  • the load handling device 3 consists of a lifting carriage 4 that can be moved vertically on the mast 2 and to which, for example, a load fork 5 formed by forks is attached as an attachment.
  • the mast 2 consists of a fixed mast 2a and an extension mast 2b which can be raised and lowered on the fixed mast 2a and on which the load handling device 3 can be raised and lowered.
  • the mast 2 of figure 1 has at least two lifting stages.
  • a hydraulic lifting cylinder device 10a is provided for raising and lowering the load handling device 3 relative to the extending mast 2b.
  • the lifting cylinder device 10a forms a first lifting stage (free lift).
  • a flexible traction device 6, for example a lifting chain is provided figure 1 is attached at a first end to the lifting carriage 4, is guided via a deflection roller 7 on the extendable piston rod of the lifting cylinder device 10a and is attached at a second end to the extension mast 2b.
  • a hydraulic lifting cylinder device 10b is used to raise and lower the extension mast 2b relative to the stationary mast 2a.
  • the lifting cylinder device 10b forms a second lifting stage (mast lift).
  • the Lift cylinder device 10a is connected to the lift cylinder device 10b by means of a pressure medium line 11 .
  • the lifting cylinder device 10a, 10b can be actuated by means of a control valve device 12 for raising and lowering the load-carrying means 3.
  • the control valve device 12 has a control valve 13 for controlling the lifting operation of the lifting drive 1 and a control valve 14 for controlling the lowering operation of the lifting drive 1 .
  • the control valve 14 for controlling the lowering operation of the lifting drive 1 is connected to the pressure medium line 20 leading to the lifting cylinder device 11 and to a container line 21 leading to the container 18 .
  • the control valve 14 has a blocking position 14a and a lowering position 14b.
  • the control valve 14 is designed as a proportional valve which throttles in intermediate positions and can be actuated electrically.
  • a discharge pressure compensator 30 is arranged in the tank line 21 leading from the control valve 14 to the tank 18 .
  • the outflow pressure compensator 30 is designed as a proportional valve which throttles in intermediate positions and has a flow position 30a and a blocking position 30b.
  • the discharge pressure compensator 30 is actuated by a spring device 31 and the pressure present in the tank line 21 between the control valve 14 and the discharge pressure compensator 30 and thus the pressure present in the tank line 21 downstream of the control valve 14 in the direction of the flow position 30a.
  • a corresponding control line 32 is routed from the tank line 21 to a control pressure surface of the outflow pressure compensator 30 acting in the direction of the flow position 30a.
  • the spring device 31 is set to a value of 4 bar, for example.
  • the outflow pressure compensator 30 is in the direction of the pressure present in the consumer line 20 and thus the pressure present in the consumer line 20 upstream of the control valve 14 the blocking position 30b actuated.
  • a corresponding control line 34 is routed from the consumer line 20 to a control pressure surface of the discharge pressure compensator 30 acting in the direction of the blocking position 30b.
  • a further tank line 35 leading to tank 18 is connected to tank line 21 between control valve 14 and discharge pressure compensator 30, in which tank line 21 a pressure compensator 40 is arranged.
  • the tank line 35 branches off from the tank line 21 between the control valve 14 and the outflow pressure compensator 30 .
  • the pressure compensator 40 is designed as a proportional valve which throttles in intermediate positions and has a flow position 40a and a blocking position 40b.
  • the pressure compensator 40 is acted upon by a spring device 41 in the direction of the flow position 40a and by the pressure present in the consumer line 20 in the direction of the blocking position 40b.
  • a corresponding control line 42 is routed from the consumer line 20 or the control line 34 to a control pressure surface of the pressure compensator 40 acting in the direction of the blocking position 40b.
  • the spring device 41 of the pressure compensator 40 is set to a limit load pressure of the lifting drive 1, for example to a value of 25 bar.
  • a throttle device 45 for example an orifice plate, is arranged in the tank line 21 between the control valve 14 and the outflow pressure compensator 30 .
  • the maximum opening cross section of the control valve 14 of the lifting drive 1 according to the invention is preferably set larger than a lifting drive of the prior art, which does not have the container line 35 with the pressure compensator 40 .
  • the consequence of this is that the same maximum volume flow at 100% lowering speed for lowering via the control valve 14 is no longer possible generates a pressure drop of 4 bar, for example, but only causes 2 bar, for example.
  • the pressure compensator 40 is open up to the limit load pressure of approximately 25 bar, for example.
  • the lowering volume flow flowing out of the lifting cylinder device 10a, 10b flows via the larger opening cross section from the control valve 14 in parallel through the pressure compensator 40 and through the throttle device 45 and the discharge pressure compensator 30.
  • a sink volume flow flowing out of the lifting drive 1 flows out via the outlet pressure compensator 30 and the pressure compensator 40 into the container 18 .
  • the load pressure present in the control line 42 presses the pressure compensator 40 into the closed position 40b and closes the pressure compensator 40 completely.
  • a lowering volume flow flowing out of the lifting drive 1 can thus flow out into the container 18 exclusively via the discharge pressure compensator 30 .
  • the outlet pressure compensator 30 thus limits above the limit load pressure alone the volume flow via the lowering valve 14 due to the constant pressure drop across the lowering valve 14 and the throttle device 45.
  • the pressure drop across the lowering valve 14 and the throttle device 45 is preferably a total of 4 bar at 100% lowering speed and thus the Value of the spring device 31 of the discharge pressure compensator 30.
  • figure 2 is a further development of figure 1 shown, with the same components being provided with the same reference numbers.
  • FIG 2 is also a safety device 50 provided in a safety position, the loading of the discharge pressure compensator 30 from the in the Container line 21 between the control valve 14 and the discharge pressure compensator 30 interrupts pending pressure and the spring preloads of the spring devices 31, 41 of the discharge pressure compensator 30 and the pressure compensator 40 are reduced.
  • the safety device 50 has a first piston 51 which is operatively connected to the spring device 31 of the outflow pressure compensator 30 and a second piston 52 which is operatively connected to the spring device 41 of the pressure compensator 40 .
  • the first piston 51 and the second piston 52 each have a control pressure chamber 53, 54 which acts in the direction of increasing the spring preload of the spring device 31 or 41, respectively.
  • a safety valve 55 is provided to control the loading of the control pressure chamber 53 of the first piston 51 and the control pressure chamber 54 of the second piston 52 .
  • the safety valve 55 is connected by means of a connecting line 56 to the tank line 21 between the control valve 14 and the outflow pressure compensator 30, in the exemplary embodiment shown to the tank line 21 between the throttle device 45 and the outflow pressure compensator 30.
  • the safety valve 55 is also connected to the control pressure chamber by means of a control line 57 53 of the first piston 51 and to the control pressure chamber 54 of the second piston 52.
  • the safety valve 55 is also connected to the container 18 by means of a drain line 58 .
  • the control line 57 is also connected to the control pressure chamber 59 of the discharge pressure compensator 30, which acts in the direction of the flow position 30a and in which the spring device 31 is arranged.
  • a control pressure chamber 60 opposite the control pressure chamber 53 of the first piston 51 is relieved by means of a line 61 to the container 18 .
  • a control pressure chamber 62 opposite the control pressure chamber 54 of the second piston 52 and the control pressure chamber 63 of the pressure compensator 40 acting in the direction of the flow position 40a, in which the spring device 41 is arranged, is relieved by means of a line 64 to the container 18 .
  • the safety valve 55 has an operating position 55a in which the connecting line 56 is connected to the control line 57 and the drain line 58 is locked.
  • the control pressure chambers 53, 54 of the two pistons 51, 52 are acted upon by the pressure in the tank line 21 between the control valve 14 and the outflow pressure compensator 30, so that the spring devices 31, 41 are prestressed to the desired prestresses.
  • the discharge pressure compensator 30 on the spring side is acted upon by the pressure in the tank line 21 between the control valve 14 and the discharge pressure compensator 30 by means of the control line 57 .
  • the safety valve 55 also has a safety position 55b, in which the control line 57 is connected to the drain line 58 and thus to the container 18 and the connection line 56 is shut off.
  • the safety position 55b the control pressure chambers 53, 54 of the two pistons 51, 52 are thus relieved, so that the spring pretensions of the spring devices 31, 41 are reduced and preferably the spring device 31, 41 is completely relieved.
  • the loading of the discharge pressure compensator 30 is interrupted by the pressure present in the tank line 21 between the control valve 14 and the discharge pressure compensator 30 and the control pressure chamber 59 of the discharge pressure compensator 30 is relieved to the tank 18 .
  • the safety valve 55 is acted upon by a spring 70 into the safety position 55b and by an actuating device 71, in particular a switching magnet, into the operating position 55a.
  • control valve 14 and the safety valve 55 are not energized, so that the control valve 14 is in the blocking position 14a and the safety valve 55 is in the safety position 55b.
  • control valve 14 is driven into the lowering position 14b and the safety valve 55 is energized and thus driven into the operating position 55a.
  • the load pressure is passed after the control valve 14 into the control pressure chambers 53, 54 of the two pistons 51, 52, so that the pistons 51, 52 set the spring devices 31, 41 of the discharge pressure compensator 30 and the pressure compensator 40 to the desired Adjust preloads.
  • the load pressure after Control valve 14 passed into the control pressure chamber 59 of the outflow pressure compensator 30, whereby the flow rate through the outflow pressure compensator 30 can be regulated.
  • the safety valve 55 By actuating the safety valve 55 into the safety position 55b, in the event of a fault, for example a control valve 14 jammed in the lowering position 14b, the lowering movement of the load-carrying means 3 can be stopped.
  • the safety valve 50 relieves the two pistons 51, 52, so that the spring devices 31, 41 of the discharge pressure compensator 30 and the pressure compensator 40 are no longer pretensioned and there is no longer any load pressure on the discharge pressure compensator 30 in the control pressure chamber 39 downstream of the control valve 14.
  • a very small load pressure in the service line 20 and thus upstream of the lowering valve 14 is sufficient to actuate the pressure compensator 40 and the discharge pressure compensator 30 into the blocking position 30b, 40b.
  • a lowering movement of the load handling device 3 can thus be stopped at any time by not energizing the safety valve 55 even when the control valve is jammed in the lowering position 14b.
  • the throttle device 45 can be dispensed with if the pressure compensator 40, which is arranged parallel to the discharge pressure compensator 30, already leads to the desired higher lowering speeds of the load handling device 3 when lowering with load pressures below the limit load pressure, so that the maximum opening cross section of the control valve 14 is not set to be larger Must.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
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  • Mechanical Engineering (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (8)

  1. Entraînement de levage hydraulique (1) d'une machine de travail mobile, notamment d'un chariot de manutention, pour le levage et l'abaissement d'un moyen de réception de charge (3), l'entraînement de levage (1) présentant un dispositif de cylindre de levage (10a ; 10b) et une soupape de commande (14) pour commander le mode d'abaissement de l'entraînement de levage (1), qui est raccordée à une conduite de consommateur (20) menant au dispositif de cylindre de levage (10a, 10b) et à une conduite de réservoir (21) menant à un réservoir (18), une balance de pression de sortie (30) étant agencée dans la conduite de réservoir (21) menant de la soupape de commande (14) au réservoir (18), qui est sollicitée par un dispositif à ressort (31) et par la pression présente dans la conduite de réservoir (21) entre la soupape de commande (14) et la balance de pression de sortie (30) en direction d'une position d'écoulement (30a) et par la pression présente dans la conduite de consommateur (20) en direction d'une position de blocage (30b), caractérisé en ce qu'une autre conduite de réservoir (35) menant au réservoir (18) est raccordée à la conduite de réservoir (21) entre la soupape de commande (14) et la balance de pression de sortie (30), dans laquelle est agencée une balance de pression (40) qui est sollicitée par un dispositif à ressort (41) en direction d'une position d'écoulement (40a) et par la pression présente dans la conduite de consommateur (20) en direction d'une position de blocage (40b), le dispositif à ressort (41) de la balance de pression (40) étant réglé sur une pression de charge limite de l'entraînement de levage (1), de telle sorte qu'en mode d'abaissement de l'entraînement de levage (1), en dessous de la pression de charge limite, un flux volumique d'abaissement sortant de l'entraînement de levage (1) sort par l'intermédiaire de la balance de pression de sortie (30) et de la balance de pression (40) dans le réservoir (18) et qu'en mode d'abaissement de l'entraînement de levage (1), au-dessus de la pression de charge limite, un flux volumique d'abaissement sortant de l'entraînement de levage (1) sort exclusivement par l'intermédiaire de la balance de pression de sortie (30) dans le réservoir (18).
  2. Entraînement de levage hydraulique selon la revendication 1, caractérisé en ce qu'un dispositif d'étranglement (45), notamment un diaphragme, est agencé dans la conduite de réservoir (21) entre la soupape de commande (14) et la balance de pression de sortie (30).
  3. Entraînement de levage hydraulique selon la revendication 1 ou 2, caractérisé en ce qu'un dispositif de sécurité (50) est prévu qui, dans une position de sécurité (55b), interrompt la sollicitation de la balance de pression de sortie (30) par la pression présente entre la soupape de commande (14) et la balance de pression de sortie (30) et réduit les précontraintes de ressort des dispositifs à ressort (31, 41) de la balance de pression de sortie (30) et de la balance de pression (40).
  4. Entraînement de levage hydraulique selon la revendication 3, caractérisé en ce que le dispositif de sécurité (50) présente un premier piston (51) en liaison active avec le dispositif à ressort (31) de la balance de pression de sortie (30) et un deuxième piston (52) en liaison active avec le dispositif à ressort (41) de la balance de pression (40), le premier piston (51) et le deuxième piston (52) présentant chacun une chambre de pression de commande (53, 54) agissant en direction d'une augmentation de la précontrainte de ressort du dispositif à ressort (31, 41), une soupape de sécurité (55) étant prévue pour commander la sollicitation de la chambre de pression de commande (53) du premier piston (51) et de la chambre de pression de commande (54) du deuxième piston (52).
  5. Entraînement de levage hydraulique selon la revendication 4, caractérisé en ce que la soupape de sécurité (55) est raccordée au moyen d'une conduite de raccordement (56) à la conduite de réservoir (21) entre la soupape de commande (14) et la balance de pression de sortie (30), est raccordée au moyen d'une conduite de commande (57) à la chambre de pression de commande (53) du premier piston (51) et à la chambre de pression de commande (54) du deuxième piston (52) et est raccordée au moyen d'une conduite d'évacuation (58) au réservoir (18) .
  6. Entraînement de levage hydraulique selon la revendication 5, caractérisé en ce que la conduite de commande (57) est raccordée à une chambre de pression de commande (59) de la balance de pression de sortie (30) agissant en direction de la position d'écoulement (30a).
  7. Entraînement de levage hydraulique selon la revendication 5 ou 6, caractérisé en ce que la soupape de sécurité (55), dans une position de fonctionnement (55a), relie la conduite de raccordement (56) à la conduite de commande (57) et, dans une position de sécurité (55b), relie la conduite de commande (57) au réservoir (18).
  8. Entraînement de levage hydraulique selon la revendication 7, caractérisé en ce que la soupape de sécurité (55) est sollicitée par un ressort (70) dans la position de sécurité (55b) et par un dispositif d'actionnement (71), notamment un aimant de commutation, dans la position de fonctionnement (55a).
EP21181370.4A 2020-07-09 2021-06-24 Entraînement de levage hydraulique d'une machine de travail mobile Active EP3936470B1 (fr)

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Application Number Priority Date Filing Date Title
DE102020118139.6A DE102020118139A1 (de) 2020-07-09 2020-07-09 Hydraulischer Hubantrieb einer mobilen Arbeitsmaschine

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EP3936470A1 EP3936470A1 (fr) 2022-01-12
EP3936470B1 true EP3936470B1 (fr) 2023-01-25

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DE102022103785A1 (de) 2022-02-17 2023-08-17 Still Gesellschaft Mit Beschränkter Haftung Hydrauliksystem, insbesondere eines Flurförderzeugs

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DE102012005432A1 (de) * 2012-03-17 2013-09-19 Jungheinrich Aktiengesellschaft Flurförderzeug mit mindestens einem Hubzylinder
DE102017107365A1 (de) * 2017-04-06 2018-10-11 Still Gmbh Hydraulischer Hubantrieb einer mobilen Arbeitsmaschine, insbesondere eines Flurförderzeugs

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EP3936470A1 (fr) 2022-01-12

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