EP2910515B1 - Chariot de manutention - Google Patents

Chariot de manutention Download PDF

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Publication number
EP2910515B1
EP2910515B1 EP15153739.6A EP15153739A EP2910515B1 EP 2910515 B1 EP2910515 B1 EP 2910515B1 EP 15153739 A EP15153739 A EP 15153739A EP 2910515 B1 EP2910515 B1 EP 2910515B1
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EP
European Patent Office
Prior art keywords
shut
hydraulic
consumer
control valve
valve device
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
EP15153739.6A
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German (de)
English (en)
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EP2910515A1 (fr
Inventor
Markus Schwab
Caspar Tügel
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.)
STILL GmbH
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STILL GmbH
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Publication date
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Publication of EP2910515A1 publication Critical patent/EP2910515A1/fr
Application granted granted Critical
Publication of EP2910515B1 publication Critical patent/EP2910515B1/fr
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Classifications

    • 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
    • B66F9/07513—Details concerning the chassis
    • B66F9/0754—Battery removal arrangements
    • 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 an industrial truck, in particular counterbalance forklift, with a working hydraulics, which comprises at least one hydraulic consumer, which is actuated by means of a control directional valve, and a battery compartment for receiving a power supply unit, in particular a battery pack, wherein the power supply unit by means of a hydraulic adjusting device between an operating position , in which the power supply unit is located in the battery compartment, and a change position in which the power supply unit is partially or completely outside the battery compartment, is movable, wherein the hydraulic actuator for supplying pressure medium to the hydraulic consumers of the working hydraulics actuated control way valve can be connected ,
  • a battery block, a fuel cell unit or a hybrid drive unit can be provided as the energy supply unit.
  • the energy supply unit present in the truck is moved partially or completely out of the battery compartment of the truck in the horizontal and lateral direction.
  • the power supply unit can then be raised in this change position, for example, with a hall crane and transported on.
  • the hydraulic extension of the power supply device is in this case usually formed by a movable in the transverse direction of the truck thrust carriage, on which the power supply unit stands, wherein the sliding carriage by means of a hydraulic adjusting device between the operating position in which the thrust slide is located with the power supply unit located thereon within the battery compartment, and a change position is movable, in which the thrust slide with the power supply unit at least partially in lateral Direction out of the battery compartment is moved.
  • From the DE 10 2012 104 586 A1 is an industrial truck, in particular a counterbalance forklift, known, which is provided with a battery compartment for receiving a power supply unit, in particular a battery pack.
  • the power supply unit is movable by means of a hydraulic adjusting device between an operating position in which the power supply unit is located in the battery compartment, and a change position in which the power supply unit is at least partially outside the battery compartment.
  • the power supply unit To supply the hydraulic actuator of the hydraulically driven Ausschubs the power supply unit, it is from the EP 1 925 512 B1 known to arrange on the slide carriage a compact hydraulic unit, which is formed by a tank, a hydraulic pump, a hydraulic pump driving the electric motor and a valve block.
  • a compact hydraulic unit which is provided in addition to the working hydraulics of the truck, but requires additional space on the hydraulic Ausschub and has a high construction cost.
  • the switching valve has only the function to direct the allocated from the control valve valve pressure medium flow either to the load of the working hydraulics or the hydraulic actuator of Ausschubs the power supply unit.
  • the hydraulic actuator is to be operated for pushing out and pushing only at a slow speed to avoid possible damage to the Ausschub, for example a support roller by means of which the displaceable Ausschub on the road surface, and the power supply unit.
  • the control valve which is based on the volumetric flow requirement of the Load of the working hydraulics is designed, which is usually much higher than the volume flow demand of the hydraulic actuator of the hydraulically driven Ausschubs the power supply unit, however, the desired slow movement speed of the hydraulic actuator can be adjusted only with difficulty.
  • the present invention has for its object to provide an industrial truck of the type mentioned, in which the control of the speed of movement of the hydraulic actuator is improved.
  • the hydraulic adjusting device is connected by means of a proportional flow control valve device to the hydraulic consumers of the working hydraulic actuated control way valve.
  • the hydraulic actuator is connected with the interposition of a proportional flow control valve device to the hydraulic consumers of the working hydraulics actuated control way valve.
  • the proportional flow control valve device assumes the function of controlling the pressure medium flow rate and thus the speed of movement of the hydraulic actuator.
  • the proportional flow control valve device has a blocking position and a throttle position, wherein in the blocking position, the hydraulic connection of the hydraulic actuator is shut off with the control way valve and in the throttle position, the hydraulic actuator is hydraulically connected to the control path valve.
  • the blocking position of the flow control valve means no pressure fluid can flow from the operated control way valve to the hydraulic actuator, so that upon actuation of the consumer of the working hydraulics at driven control way valve actuation of the hydraulic actuator can be safely and effectively prevented.
  • the Throttle position of the flow control valve device can be limited and controlled in a simple manner by means of the flow control valve means of the open control travel valve of the hydraulic actuator inflowing fluid flow, so that the movement speed of the hydraulic actuator can be sensitively controlled and limited.
  • the blocking position of the proportional flow control valve means in the direction of the hydraulic actuator locking blocking valve, in particular check valve has.
  • the proportional flow control valve device is electrically actuated in the direction of the throttle position and is in the non-activated state in the blocking position.
  • the hydraulic load of the working hydraulics of a double-acting consumer is formed, which is connected by means of a first consumer line and a second consumer line to the control way valve, wherein the hydraulic adjusting device is connected by means of at least one branch line to the load lines and in the at least a branch line, the proportional flow control valve device is arranged, wherein a consumer lines associated shut-off valve device is provided, by means of which the hydraulic connection of the consumer is shut off with the control valve.
  • branching branch line can with little Construction costs, the hydraulic actuator with pressure medium via the control valves of the working hydraulics are supplied.
  • shut-off valve device With the consumer lines associated shut-off valve device is achieved in a simple manner to shut off the consumer lines, so that upon actuation of the hydraulic actuator no pressure fluid can flow to the hydraulic consumer and thus actuation of the hydraulic load safely and effectively prevented upon actuation of the hydraulic actuator can.
  • the shut-off valve device has a first shut-off valve arranged in the first connecting line and a second shut-off valve arranged in the second connecting line.
  • the check valves are each designed as switching valves with a blocking position and a flow position. With such check valves can be easily secured in the locked position of the hydraulic consumer with controlled control valves against unwanted actuation and in the flow position actuation of the hydraulic load with controlled control valves are possible.
  • the shut-off valve device is electrically actuated.
  • the hydraulic actuating device comprises a double-acting hydraulic cylinder, wherein a branch line is provided, which is arranged on the first or the second connecting line, and the proportional flow control valve device comprises a single proportional flow control valve, which is arranged in the branch line, wherein the Control of the direction of movement of the hydraulic cylinder is provided a switching valve device.
  • the branch line is connected according to an embodiment of the invention to a first consumer side of the hydraulic cylinder, wherein the second consumer side is connected to a guided to a container tank line and a connecting line connecting the branch line to the container line is provided, the switching valve device having a shut-off valve arranged in the connecting line and a further shut-off valve arranged in the container line between the connection of the connecting line and the container.
  • a switching valve device formed from two simple shut-off valves makes it possible with little construction effort to control the direction of movement of the hydraulic actuator.
  • shut-off valves are designed as switching valves with a blocking position and a flow position, whereby the construction costs for the changeover valve device, with which the direction of movement of the hydraulic actuating device can be controlled, can be further reduced.
  • the switching valve device is electrically actuated.
  • an electrical control can easily by a corresponding Operation of the switching valve device, the direction of movement of the hydraulic actuator are selected and thus controlled.
  • the hydraulic adjusting device comprises a double-acting hydraulic cylinder, wherein a first consumer side of the hydraulic cylinder is connected by a first branch line to the first connecting line and a second consumer side of the hydraulic cylinder is connected by means of a second branch line to the second connecting line, wherein the proportional flow control valve means comprises a first proportional flow control valve disposed in the first branch line and a second proportional flow control valve disposed in the second branch line.
  • the proportional flow control valve device is actuated into the blocking position for operating the hydraulic consumer and the shut-off valve device is actuated into the flow position.
  • the hydraulic consumer can be actuated in a control of the control travel valve, wherein the located in the blocking position proportional flow control valve device shuts off the hydraulic actuator against unwanted actuation.
  • the proportional flow control valve device is actuated in the direction of the throttle position and the shut-off valve device is actuated to the blocking position for operating the hydraulic adjusting device.
  • the hydraulic actuating device can be actuated with the movement speed predetermined by the proportional flow control valve device, wherein the shut-off valve device located in the blocking position shuts off the hydraulic consumer against unintentional actuation.
  • FIG. 1 is an inventive, designed as a counterbalance forklift truck 1 shown in a perspective view.
  • a battery compartment 6 for receiving a power supply device 7 designed, for example, as a battery block is formed in a middle section of a vehicle body 5 of the industrial truck 1 formed by a frame 2, a counterweight 3 and a driver's protective roof 4, a battery compartment 6 for receiving a power supply device 7 designed, for example, as a battery block is formed.
  • the vehicle body 5 is provided with a side opening 8, through which the power supply unit 7 in lateral and horizontal directions - as in the FIG. 1 is illustrated by the arrow - for changing the power supply unit 7 from the battery compartment 6 at least partially moved out or can be moved into the battery compartment 6.
  • a change position is shown, in which the power supply unit 7 is at least partially laterally outside the battery compartment 6. In an operating position, the power supply unit 7 is completely in the battery compartment 6.
  • a hydraulically driven extension 10 is provided for moving the power supply unit 7 between the operating position and the change position
  • the extension 10 has a slide carriage 9, on which the energy supply unit 7 stands up.
  • the slide carriage 9 can be moved out of the battery compartment 6 of the industrial truck 1 in the lateral direction or moved into the battery compartment 6.
  • the slide carriage 9 is by means of a means of in the FIG. 1 not shown hydraulic adjusting device between the operating position in which the thrust slide 9 is located within the battery compartment 6 and the change position in which the thrust slide 9 is at least partially outside of the battery compartment 6.
  • FIG. 2 a hydraulic circuit diagram of a first embodiment of the truck 1 according to the invention is shown.
  • the truck 1 has a working hydraulics 15, which comprises a plurality of hydraulic consumers 17-20.
  • the consumer 17 is a single-acting lifting drive of a lifting device and as a consumer 18, a double-acting tilt drive, such as a mast, provided.
  • the working hydraulics 15 further comprises at least one designed as an additional drive consumer 19 or 20.
  • the consumer 19 forms a first auxiliary drive, which is formed by a double-acting drive, and the consumer 20, a second auxiliary drive, which is formed by a further double-acting drive.
  • the consumer 17 is controllable by means of a control valve 21.
  • the consumer 18 is controllable by means of a control valve 22.
  • the consumer 19 is controllable by means of a control valve 23.
  • the consumer 20 is controllable by means of a control valve 24.
  • the control travel valves 21-24 preferably each have a neutral position, is blocked in the associated consumer 17-20, a first control position for a first direction of movement of the associated consumer 17-20 and a second control position for a second direction of movement of the associated consumer 17-20 , In the illustrated embodiment, the control way valves 21-24 are combined to form a control valve block 25.
  • a pump 26 is provided.
  • the pump 26 is on the suction side with a container 27 in communication and conveys into a delivery line 28.
  • the pump 26 is connected to the drive with a drive motor 29 in connection, for example an electric motor.
  • the pump 26 continues to supply a hydraulic steering system 30.
  • a priority valve 31 is arranged on the output side by means of a delivery branch 32a with the steering system 30 and by means of a delivery branch line 32b with the Control valve block 25 is connected.
  • the control valve block 25 is connected to the container 27 by means of a tank line 33.
  • control valves 23, 24 thus form an additional hydraulic system, by means of which consumers designed as attachments 19, 20 can be supplied by the pump 26 with pressure medium.
  • the hydraulic actuator 40 is formed by a double-acting hydraulic cylinder 41.
  • the hydraulic cylinder 41 has an acting in the direction of the operating position pressure chamber 41 a, which forms a first consumer side A, and acting in the direction of the change position pressure chamber 41 b, which forms a second consumer side B.
  • the hydraulic cylinder 41 is preferably arranged with a cylinder housing on the vehicle body 5 and is connected to an extendable or retractable piston rod 41c with the slide carriage 9 in operative connection.
  • a branch line 42 is provided, which is connected to a first connecting line 43 a, by means of which the consumer 19 is connected to the control-way valve 23.
  • the designed as a double-acting actuator load 19 is further connected by means of a second connecting line 43 b with the control valve 23.
  • a proportional flow control valve device 45 is provided, by means of which the hydraulic cylinder 41 is connected to the control-way valve 23.
  • the proportional flow control valve device 45 of the FIG. 2 is formed by a arranged in the branch line 42 proportional flow control valve 46.
  • the branch line 42 is connected to the pressure chamber 41 a of the hydraulic cylinder 41.
  • the pressure chamber 41 b of the hydraulic cylinder 41 is connected by means of a container line 47 to the container 27.
  • a switching valve device 50 For controlling the direction of movement of the hydraulic cylinder 41, a switching valve device 50 is provided.
  • the switching valve device 50 comprises a shut-off valve 51 a, which is arranged in a connection line 52 connecting the branch line 42 to the container line 47.
  • the connection line 52 is connected to the branch line 42 between the proportional flow control valve device 45 and the pressure chamber 41 a.
  • a check valve 53 is further arranged in the branch line 42, for example, in the direction of the pressure chamber 41 a opening check valve.
  • the switching valve device 50 comprises a further shut-off valve 51 b, which is arranged in the container line 47 between the connection of the connecting line 52 and the container 27.
  • the shut-off valves 51 a, 51 b are each designed as switching valves with a blocking position and a flow position.
  • the switching valve device 50 is electrically actuated.
  • the shut-off valves 51 a, 51 b in each case by means of an electrical actuator 54 a, 54 b, for example, a solenoid actuated.
  • the shut-off valves 51 a, 51 b are each actuated by a spring in the flow position and actuated by the electrical actuator 54 a, 54 b in the blocking position.
  • the consumer lines 43a, 43b routed to the consumer 19 are assigned a shut-off valve device 60, by means of which the hydraulic connection of the consumer 19 to the control-way valve 23 can be shut off.
  • the shut-off valve device 60 has a first shut-off valve 61 a arranged in the first connecting line 43 a and a second shut-off valve 61 b arranged in the second connecting line 43 b. That in the connection line 43a arranged check valve 61 a is disposed in the connecting line 43 a between the connection of the branch line 42 and the consumer 19.
  • the check valves 61 a, 61 b are each formed as switching valves with a blocking position and a flow position.
  • the shut-off valve device 60 is electrically actuated.
  • the check valves 61 a, 61 b are each actuated by means of an electrical actuator 62 a, 62 b, for example, a solenoid.
  • the check valves 61 a, 61 b are each actuated by a spring in the blocking position and actuated by the electrical actuator 62 a, 62 b in the flow position.
  • FIG. 3 a hydraulic circuit diagram of a second embodiment of the truck according to the invention is shown. The same components are provided with the same reference numbers.
  • FIG. 3 differs from the embodiment of FIG. 2 with regard to the hydraulic connection of the hydraulic adjusting device 40 of the Ausschubs 10 to the control-way valve 23 of the load 19 of the working hydraulics 15th
  • a first branch line 42a is provided, which is connected to the first connecting line 43a, by means of which the load 19 is connected to the control-way valve 23.
  • the first branch line 42a is connected to the pressure space 41a of the hydraulic cylinder 41.
  • a second branch line 42 b is provided, which is connected to the second connecting line 43 b, by means of which the consumer 19 is connected to the control-way valve 23.
  • the second branch line 42 b is connected to the pressure chamber 41 b of the hydraulic cylinder 41.
  • the proportional flow control valve device 45 has a first proportional flow control valve 46a disposed in the first branch line 42a, and a second proportional flow control valve 46b disposed in the second branch line 42b.
  • the proportional flow control valves 46, 46a and 46b of Figures 2 and 3 each have a blocking position 70 and a throttle position 71. In the non-activated state, the flow control valves 46, 46 a and 46 b are in the blocking position 70, in which the hydraulic connection of the hydraulic adjusting device 40 is shut off with the control-way valve 23.
  • the blocking position 70 of the proportional flow control valves 46, 46a and 46b each have a blocking in the direction of the hydraulic actuator 40 check valve 72, for example, check valve on.
  • the proportional flow control valves 46, 46 a and 46 b are each electrically actuated in the direction of throttle position 71.
  • the flow control valves 46, 46a and 46b are each provided by means of an electrical actuating device 73, for example a proportional magnet.
  • the flow control valves 46, 46 a and 46 b are actuated in each case by means of a spring 74.
  • the shut-off valve device 60 has the first shut-off valve 61 a arranged in the first connecting line 43 a and the second shut-off valve 61 b arranged in the second connecting line 43 b.
  • the blocking valve 61 a arranged in the connecting line 43 a is arranged in the connecting line 43 a between the connection of the branch line 42 a and the consumer 19.
  • the check valve 61b arranged in the connection line 43b is arranged in the connection line 43b between the connection of the branch line 42b and the load 19.
  • the check valves 61 a, 61 b of FIG. 3 are in terms of the construction with the check valves 61 a, 61 b of FIG. 2 identical.
  • the proportional flow control valve 46 is not activated and is in the blocking position 70.
  • the check valves 61a, 61b are driven and are each in the flow position.
  • the Consumer 19 are actuated.
  • the hydraulic actuator 40 is hydraulically shut off from the connecting line 43a, so that upon actuation of the consumer 19, an unwanted operation of the hydraulic actuator 40 is prevented.
  • the check valves 61a, 61b are each actuated into the blocking position.
  • the pilot valve 23 is controlled so that the connecting line 43 a is connected to the pump 26.
  • the proportional flow control valve 46 By operating the proportional flow control valve 46 in the direction of the throttle position 71 of the hydraulic actuator 40 inflowing fluid flow and thus the speed of movement of the hydraulic actuator 40 can be controlled and limited. Even in an operating state in which the pump 26 delivers a flow rate that exceeds the demand of the hydraulic actuator 40, it is thus achieved that the proportional flow control valve 46 limits the pressure medium volume flow required by the hydraulic actuator 40 to a maximum value.
  • the switching valve device 50 the direction of movement of the hydraulic actuator 40 can be controlled.
  • the check valve 51 a is in the flow position and the check valve 51 b is actuated in the blocking position.
  • the shut-off valve 51 b is in the flow position and the check valve 51 a is actuated in the blocking position.
  • the consumer 19 is hydraulically shut off, so that upon actuation of the hydraulic actuator 40, an unwanted operation of the consumer 19 is prevented.
  • the proportional flow control valves 46a, 46b are not activated and is in each case in the blocking position 70.
  • the check valves 61a, 61b are activated and are each in the flow position.
  • the consumer 19 can be actuated.
  • the hydraulic actuator 40 is hydraulically shut off from the connecting lines 43a, 43b, so that at a Operation of the consumer 19 an unwanted operation of the hydraulic actuator 40 is prevented.
  • the check valves 61 a, 61 b are each actuated in the blocking position.
  • the control path valve 23 is controlled such that the connecting line 43 b is connected to the pump 26 and the connecting line 43 a to the container 27.
  • the proportional flow control valve 46b By actuating the proportional flow control valve 46b in the direction of the throttle position 71 of the hydraulic actuator 40 on the load side B incoming flow of fluid and thus the speed of movement of the hydraulic actuator 40 can be controlled and limited. Even in an operating state in which the pump 26 delivers a flow rate that exceeds the demand of the hydraulic actuator 40, it is thus achieved that the proportional flow control valve 46b limits the pressure medium volume flow required by the hydraulic actuator 40 to a maximum value.
  • the proportional flow control valve 41 a is not activated and is in the blocking position 70. The flowing from the consumer side A of the hydraulic cylinder 41 pressure medium flow rate flows through the opening check valve 72 in the connecting line 43 a, which via the control valve 23rd is connected to the container 27.
  • the control-way valve 23 is controlled such that the connecting line 43 a to the pump 26 and the connecting line 43 b is connected to the container 27.
  • the proportional flow control valve 46a By operating the proportional flow control valve 46a in the direction of the throttle position 71 of the hydraulic actuator 40 on the load side A inflowing fluid flow and thus the speed of movement of the hydraulic actuator 40 can be controlled and limited. Even in an operating state in which the pump 26 delivers a flow rate that exceeds the demand of the hydraulic actuator 40, it is thus achieved that the proportional flow control valve 46a limits the pressure medium volume flow required by the hydraulic actuator 40 to a maximum value.
  • the proportional flow control valve 41 b is not activated and is in the blocking position 70. The pressure medium volume flow flowing out of the consumer side B of the hydraulic cylinder 41 flows via the opening blocking valve 72 into the connecting line 43b, which is connected to the container 27 via the control-way valve 23.
  • the load 19 is hydraulically shut off, so that upon extension and retraction of the piston rod 41 c of the hydraulic cylinder 41, an unwanted actuation of the consumer 19 is prevented.
  • the invention makes it possible with simple construction and low space requirement, the pressure medium supply of the hydraulic actuator 40 of Ausschubs 10 of the power supply unit 7 via a control way valve 21-24 by the pump 26 to perform the work hydraulics 15 and the movement speed of the hydraulic actuator 40 to control sensitive or on to limit a certain maximum value.

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  • Structural Engineering (AREA)
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Claims (16)

  1. Chariot de manutention (1), et plus particulièrement, chariot élévateur à fourche à contrepoids, comportant un système hydraulique de travail (15) qui comprend au moins un consommateur hydraulique (17-20), qui peut être actionné au moyen d'une vanne de commande (21-24), et comportant un compartiment pour batterie (6) destiné à recevoir une unité d'alimentation en énergie (7), et plus particulièrement, un bloc-batteries, dans lequel l'unité d'alimentation en énergie (7) est mobile au moyen, d'un dispositif de réglage hydraulique (10) entre une position de fonctionnement, à laquelle l'unité d'alimentation en énergie (7) se trouve dans le compartiment pour batterie (6), et une position de remplacement, à laquelle l'unité d'alimentation en énergie (7) se trouve partiellement ou entièrement à l'extérieur du compartiment pour batterie (6), dans lequel le dispositif de réglage hydraulique (10) peut être raccordé à la vanne de commande (21-24) actionnant le consommateur hydraulique (17-20) du système hydraulique de travail (15) pour l'alimentation en agent de compression, caractérisé en ce que le dispositif de réglage hydraulique (10) est raccordé au moyen d'un dispositif à vanne de régulation proportionnelle de débit (45) à la vanne de commande (21-24) actionnant le consommateur hydraulique (17-20) du système hydraulique de travail (15).
  2. Chariot de manutention selon la revendication 1, caractérisé en ce que le dispositif à vanne de régulation proportionnelle de débit (45) présente une position de blocage (70) et une position d'étranglement (71), dans lequel, à la position de blocage (70), la liaison hydraulique du dispositif de réglage hydraulique (10) est bloquée au moyen de la vanne de commande (21-24) et, à la position d'étranglement (71), le dispositif de réglage hydraulique (10) est hydrauliquement relié à la vanne de commande (21-24).
  3. Chariot de manutention selon la revendication 2, caractérisé en ce que la position de blocage (70) du dispositif à vanne de régulation proportionnelle de débit (45) présente une vanne de blocage (72) produisant un blocage dans une direction orientée vers le dispositif de réglage hydraulique (10), et plus particulièrement, une vanne de non-retour.
  4. Chariot de manutention selon la revendication 2 ou 3, caractérisé en ce que le dispositif à vanne de régulation proportionnelle de débit (45) peut être actionné électriquement dans la direction de la position d'étranglement (71) et se trouve à l'état non commandé à la position de blocage (70).
  5. Chariot de manutention selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le consommateur hydraulique (19) du système hydraulique de travail (15) est formé par un consommateur à double action, qui est relié au moyen d'une première ligne de consommateur (43a) et d'une seconde ligne de consommateur (43b) à la vanne de commande (23), dans lequel le dispositif de réglage hydraulique (10) est raccordé au moyen d'au moins une dérivation (42 ; 42a, 42b) aux lignes de consommateurs (43a, 43b) et le dispositif à vanne de régulation proportionnelle de débit (45) est raccordé à ladite au moins une dérivation (42 ; 42a, 42b), dans lequel il est prévu un dispositif à vanne de blocage (60) associé aux lignes de consommateurs (43a, 43b), au moyen duquel la liaison hydraulique du consommateur (19) peut être bloquée au moyen de la vanne de commande (23).
  6. Chariot de manutention selon la revendication 5, caractérisé en ce que le dispositif à vanne de blocage (60) présente une première vanne de blocage (61a) disposée dans la première ligne de liaison (43a) et une seconde vanne de blocage (61b) disposée dans la seconde ligne de liaison (43b).
  7. Chariot de manutention selon la revendication 6, caractérisé en ce que la vanne de blocage (61a ; 61b) est disposée dans la ligne de liaison (43a ; 43b) entre le raccord de la dérivation (42 ; 42a, 42b) et le consommateur (19).
  8. Chariot de manutention selon la revendication 6 ou 7, caractérisé en ce que les vannes de blocage (61a, 61b) sont respectivement réalisées sous la forme d'une vanne de commutation ayant une position de blocage et une position de passage.
  9. Chariot de manutention selon l'une quelconque des revendications 5 à 8, caractérisé en ce que le dispositif à vanne de blocage (60) peut être actionné électriquement.
  10. Chariot de manutention selon l'une quelconque des revendications 1 à 9, caractérisé en ce que le dispositif de réglage hydraulique (10) comprend un vérin hydraulique à double action (41), dans lequel il est prévu une dérivation (42) qui est disposée dans la première ou la seconde ligne de liaison (43a ; 43b), et le dispositif à vanne de régulation proportionnelle de débit (45) comprend une vanne de régulation proportionnelle de débit (46) unique, qui est disposée dans la dérivation (42), dans lequel il est prévu un dispositif à vanne d'inversion (50) pour commander la direction de déplacement du vérin hydraulique (41).
  11. Chariot de manutention selon la revendication 10, caractérisé en ce que la dérivation (42) est raccordée à un premier côté consommateur (A) du vérin hydraulique (41), dans lequel le second côté consommateur (B) du vérin hydraulique (41) est relié à une ligne de récipient (47) acheminée vers un récipient (27) et il est prévu une ligne de liaison (52) reliant la dérivation (42) à la ligne de récipient (47), dans lequel le dispositif à vanne d'inversion (50) présente une vanne de blocage (51a) disposée dans la ligne de liaison (52) et une autre vanne de blocage (51b) disposée dans la ligne de récipient (47) entre le raccord de la ligne de liaison (52) et le récipient (27).
  12. Chariot de manutention selon la revendication 11, caractérisé en ce que les vannes de blocage (51a, 51b) sont respectivement réalisées sous la forme d'une vanne de commutation ayant une position de blocage et une position de passage.
  13. Chariot de manutention selon l'une quelconque des revendications 10 à 12, caractérisé en ce que le dispositif à vanne d'inversion (50) peut être actionné électriquement.
  14. Chariot de manutention selon l'une quelconque des revendications 1 à 9, caractérisé en ce que le dispositif de réglage hydraulique (10) comprend un vérin hydraulique à double action (41), dans lequel un premier côté consommateur (A) du vérin hydraulique (41) est raccordé au moyen d'une première dérivation (42a) à la première ligne de liaison (43a) et un second côté consommateur (B) du vérin hydraulique (41) est raccordé au moyen d'une seconde dérivation (42b) à la seconde ligne de liaison (43b), dans lequel le dispositif à vanne de régulation proportionnelle de débit (45) présente une première vanne de régulation proportionnelle de débit (46a), qui est disposée dans la première dérivation (42a), et une seconde vanne de régulation proportionnelle de débit (46b), qui est disposée dans la seconde dérivation (42b).
  15. Chariot de manutention selon l'une quelconque des revendications 1 à 14, caractérisé en ce que, pour faire fonctionner le consommateur hydraulique (19), le dispositif à vanne de régulation proportionnelle de débit (15) est actionné à la position de blocage (70) et le dispositif à vanne de blocage (60) est actionné à la position de passage.
  16. Chariot de manutention selon l'une quelconque des revendications 1 à 15, caractérisé en ce que, pour faire fonctionner le dispositif de réglage hydraulique (10), le dispositif à vanne de régulation proportionnelle de débit (45) est actionné dans la direction de la position d'étranglement (71) et le dispositif à vanne de blocage (60) est actionné à la position de blocage.
EP15153739.6A 2014-02-19 2015-02-04 Chariot de manutention Not-in-force EP2910515B1 (fr)

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EP3677540B1 (fr) * 2018-12-31 2024-05-01 STILL GmbH Chariot de manutention

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DE10347065A1 (de) 2003-10-09 2005-05-12 Linde Ag Flurförderzeug mit einem seitlich entnehmbaren Batterieblock
DE102006055361A1 (de) 2006-11-23 2008-05-29 Still Gmbh Flurförderzeug mit seitlich entnehmbarer Batterie
DE102012104586A1 (de) * 2012-05-29 2013-12-05 Linde Material Handling Gmbh Flurförderzeug

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