EP2980006B1 - Installation hydraulique d'une machine de travail mobile, notamment d'un chariot de manutention - Google Patents

Installation hydraulique d'une machine de travail mobile, notamment d'un chariot de manutention Download PDF

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Publication number
EP2980006B1
EP2980006B1 EP15179000.3A EP15179000A EP2980006B1 EP 2980006 B1 EP2980006 B1 EP 2980006B1 EP 15179000 A EP15179000 A EP 15179000A EP 2980006 B1 EP2980006 B1 EP 2980006B1
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EP
European Patent Office
Prior art keywords
pressure medium
valve
hydraulic system
control
charging
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
EP15179000.3A
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German (de)
English (en)
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EP2980006A1 (fr
Inventor
Peter Magsaam
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.)
Linde Material Handling GmbH
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Linde Material Handling GmbH
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Filing date
Publication date
Application filed by Linde Material Handling GmbH filed Critical Linde Material Handling GmbH
Publication of EP2980006A1 publication Critical patent/EP2980006A1/fr
Application granted granted Critical
Publication of EP2980006B1 publication Critical patent/EP2980006B1/fr
Not-in-force legal-status Critical Current
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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
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • B66F9/12—Platforms; Forks; Other load supporting or gripping members
    • B66F9/14—Platforms; Forks; Other load supporting or gripping members laterally movable, e.g. swingable, for slewing or transverse movements
    • B66F9/146—Side shift, i.e. both forks move together sideways relative to fork support
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7135—Combinations of output members of different types, e.g. single-acting cylinders with rotary motors

Definitions

  • the invention relates to a hydraulic system of a mobile work machine, in particular of a truck, with a working hydraulics comprising a lifting drive and a side slide, wherein the hydraulic system comprises a working hydraulic pump which is provided for supplying the lifting drive with pressure medium, wherein the hydraulic system comprises a pressure fluid reservoir.
  • a hydraulic system of a truck is out of the DE 102 24 731 B4 known.
  • Work machines designed as industrial trucks have working hydraulics which, as consumers, are a lifting drive for lifting and lowering a load receiving means, for example a forklift, a tilting drive for tilting the load receiving means or a lifting frame on which the load receiving means can be raised and lowered, and one or more Additional consumer includes.
  • the additional consumers are usually formed by different attachments with which additional function of the lifting device are controllable, for example, a side slide for lateral displacement of the lifting device, or a rotating device for rotating the lifting device.
  • the additional consumers can have different demands on the pressure and the flow rate and thus the volume flow requirement.
  • a side shifter has a relatively low flow rate, whereas a rotary device requires a relatively high flow rate.
  • the lifting drive, the tilt drive and the additional consumers are each controllable by means of a control path valve which communicates with the supply line of the working hydraulic pump for the supply of pressure medium.
  • control valves for controlling the linear actuator, the tilt drive and the additional consumers are in this case installed in a control valve block, for example, a Monoventilblock cast or layered construction of brazed segment plates, the control way valve of the additional consumer is designed for the additional consumer with the largest possible flow rate.
  • the working hydraulics is usually provided with an inlet pressure compensator, which is controlled by the highest load pressure of the load of the working hydraulics and allows the working hydraulic pump promotes non-actuated consumers in a single circulation to a container and funded actuated by consumers of the working hydraulic pump Excessive volume flow that exceeds the demand of the consumers of the working hydraulics can be discharged to the container.
  • the DE 199 03 174 A1 discloses an attachment designed as a side slide, which supplies pressure medium from a pressure medium accumulator arranged in the lifting slide becomes.
  • the arranged in the lifting pressure fluid accumulator is mitaufêt during lifting of the lifting cylinder with pressure medium.
  • the present invention has for its object to provide a hydraulic system of the type mentioned is available, which is improved in terms of energy efficiency in the operation of the side shifter.
  • the accumulator is charged by means of a charging circuit of the working hydraulic pump with pressure medium, wherein the charging circuit has a biasing valve, which ensures the preferred supply of pressure fluid accumulator with pressure medium of the working hydraulic pump, the bias valve on the input side with a delivery line of the hydraulic pump in Connection stands and the biasing valve is connected on the output side to a supply line leading to control valves of the working hydraulics as well as to a charge line guided to the accumulator, wherein the side shifter is connected to the accumulator for supplying pressure medium.
  • the supply of the side slide is thus detached from the working hydraulic pump with pressure medium from the accumulator, which was charged by the working hydraulic pump with pressure medium.
  • the side shifter can be supplied as required with the required volume flow and the required amount of pressure medium, so that the sole operation of the side slide throttling an excess amount of the inlet pressure compensator and the associated energy losses are avoided.
  • the heat input into the pressure medium is also reduced in the invention, whereby further a low cooling demand for the pressure medium can be achieved.
  • the supply of the side shifter according to the invention has a high energy efficiency.
  • the side shifter is controllable by means of a control path valve which is connected to the supply of pressure fluid to supply with pressure medium.
  • a control way valve With a control way valve, the moving speed and the moving direction of the side shifter can be easily controlled.
  • the control valve to the flow rate requirement and thus the flow rate demand adapt the side shifter and interpreted accordingly, so that in the invention, an improved metering of the movement of the side shifter by the operation and deflection of a setpoint specification device, such as a joystick can be achieved.
  • the charging circuit of the pressure medium accumulator on the charging line which is connectable to charge the accumulator with the delivery line of the working hydraulic pump, wherein in the charging line a check valve, in particular, a check valve opening in the direction of the accumulator is arranged, wherein the control path valve of the side shifter is connected to the supply of pressure medium from the accumulator to the charge line between the accumulator and the check valve.
  • a check valve in particular, a check valve opening in the direction of the accumulator is arranged
  • the control path valve of the side shifter is connected to the supply of pressure medium from the accumulator to the charge line between the accumulator and the check valve.
  • control valve of the side valve is electrically actuated, wherein an electronic control device is provided for driving the control path valve of the side shifter, the input side with a set point for the side shifter, such as a joystick, is in active connection.
  • control path valve of the side slide by means of an electrical actuating device, such as electromagnets, actuated, directly actuate a spool of the control valves.
  • an electrical actuating device such as electromagnets, actuated
  • directly actuate a spool of the control valves directly actuate a spool of the control valves.
  • the charging circuit of the accumulator is installed in a storage charging section and the control path valve of the side shifter installed in the accumulator charging section.
  • the construction cost can be further reduced and it is achieved that at one the control valves of the remaining consumers the Hydraulic control valve block containing no changes to the installation of the control valves of the side valve are required.
  • the accumulator charging section is attached to a control valve block of the working hydraulics.
  • Such coding can be formed according to an advantageous embodiment of the invention of special fittings.
  • special fittings for the consumer connections of the control valves and the side valve can be achieved in a simple manner that only the side shifter can be connected to the control valves of the side valve of the hydraulic system according to the invention.
  • the hydraulic system comprises a hydraulic steering device and the pressure medium reservoir is provided for supplying the steering device with pressure medium.
  • the accumulator thus continues to serve to supply a hydraulic steering device of the working machine, whereby the energy efficiency of the hydraulic system can be further improved.
  • FIG. 1 is a hydraulic circuit diagram of a hydraulic system 1 according to the invention a mobile machine, for example, designed as a counterbalanced forklift truck illustrated.
  • the hydraulic system 1 of the industrial truck comprises a working hydraulics 2, a hydraulic steering device 3 and a hydraulic braking device 4.
  • the hydraulic system 1 of the industrial truck further comprises a hydrostatic drive 5 of the industrial truck.
  • the hydrostatic drive 5 comprises a drive pump 6, which is connected in a closed circuit to traction motors 7a, 7b which are in operative connection with the driven wheels 9a, 9b of the industrial truck.
  • the drive pump 6 is designed as a variable displacement in the variable displacement pump, to the adjustment of the delivery volume, an adjusting device 10 is provided.
  • the closed circuit of the hydrostatic drive is further provided with a feed device 11.
  • the adjusting device 10 and the feeding device 11 are connected to the supply of pressure medium with a supply line 12 in connection.
  • the hydraulic steering device 3 comprises a hydraulic steering cylinder 15 which can be actuated by means of a steering valve 16.
  • the steering valve 16 is formed in the illustrated embodiment as Lenkorbitrol, which is mechanically actuated and is for actuating with a steering actuator 17, such as a steering wheel, in mechanical operative connection.
  • the steering valve 16 is connected to the supply of pressure medium with a supply line 18 in connection.
  • An output of the steering valve 16 is connected to a guided to a container 20 drain line 19.
  • the hydraulic braking device 4 has a load 30 as a consumer, for example, a spring brake, which is associated with the driven wheels 9a, 9b and by means of a brake valve 31 is actuated.
  • the brake valve 31 is formed in the illustrated embodiment as a mechanically actuated pressure control valve which controls the brake release pressure in a brake line 32 which is connected to a force acting in the direction of a release position pressure chamber of the spring brake.
  • the brake valve 31 is for actuating with a brake actuator 33, such as a brake pedal, in mechanical operative connection.
  • the brake valve 31 is connected to a supply line 34, to a guided to the container 20 drain line 35 and to the brake pipe 32.
  • the working hydraulics 2 comprises in the illustrated embodiment, a lifting drive 40, a tilt drive 41 and a side gate 43 as hydraulic consumers. Furthermore, the working hydraulics 2 may include an additional consumer 42 as a further hydraulic consumer.
  • a working hydraulic pump 45 is provided, which is driven by a drive motor 46.
  • the drive motor 46 is formed in the illustrated embodiment as an internal combustion engine. However, it is alternatively possible to execute the drive motor 46 as an electric motor.
  • the drive motor 46 continues to drive the drive pump 6 of the hydrostatic drive 5.
  • the drive motor 46 further serves to drive an auxiliary pump 47, which serves to supply the braking device 4, the adjusting device 10 of the drive pump 6 and the feed device 11 of the hydrostatic drive 5.
  • the auxiliary pump 47 is operated in the open circuit and sucks pressure medium via a suction line 48 from the container 20 and promotes the pressure medium in a delivery line 49 to which the supply line 34 of the braking device 4 and the supply line 12 of the adjusting device 10 and the feeding device 11 are connected ,
  • the working hydraulic pump 45 is operated in an open circuit and sucks pressure medium via a suction line 48 from the container 20 and conveys the pressure medium in a delivery line 50.
  • the delivery line 50 is connected to a port P of Control valve block 51 of the working hydraulics 2 connected.
  • the working hydraulic pump 45 is formed as adjustable in the delivery volume variable displacement pump, to whose adjustment of the delivery volume, an adjusting device 45a is provided. For supply with pressure medium, the adjusting device 45a is connected to the delivery line 49 of the auxiliary pump 47.
  • the control valve block 51 of the working hydraulics 2 includes a control-way valve 52 for controlling the lifting drive 40, a control-way valve 53 for controlling the tilting drive 41, and a control-way valve 54 for controlling the optional additional consumer 42.
  • the port P is in the control valve block 51 - as in FIG. 2 can be seen - connected to a supply line 60, to which by means of appropriate prinzweig effeten the control valves 52, 53, 54 are connected.
  • a port T of the control valve block 51 to which a tank line 61 led to the tank 20 is connected, communicates in the control valve block 51 with a tank line 62 to which the control directional valves 52, 53, 54 are connected by means of tank branch lines.
  • the control travel valve 52, 53, 54 are designed as load-sensing directional control valves, wherein upon activation of the control travel valves 52, 53, 54 and thus an actuation of the consumer 40, 41, 42, the highest load pressure is reported in a load pressure reporting line 63 of the working hydraulics 2 ,
  • the control valves 52, 53, 54 are designed as pilot-operated control valves and each electro-hydraulically actuated.
  • electrically actuatable pilot valves 52a, 52b are provided for actuating the control travel valve 52
  • electrically actuatable pilot valves 53a, 53b are provided for actuating the control travel valve 53
  • electrically actuatable pilot valves 54a, 54b are provided for actuating the control travel valve 54.
  • the pilot valves 52a, 52b, 53a, 53b, 54a, 54b are designed, for example, as pressure-reducing valves which can be actuated by means of a proportional magnet.
  • the pilot valves 52a, 52b, 53a, 53b, 54a, 54b are on the input side to supply with a control pressure with a control pressure line 68 of the control valve block 51 in connection, which is guided to a port Z of the control valve block 51. Via a supply line 69 connected to the connection Z, the control pressure line 68 communicates with the delivery line 49 of the auxiliary pump 47. at an electric control and thus an operation to generate the pilot valves 52a, 52b, 53a, 53b, 54a, 54b from the pending in the control pressure line 68 control pressure an actuating pressure, the corresponding control way valve 52, 53, 54 in a corresponding control position for actuating the consumer 40th , 41, 42 charged.
  • the load pressure detection line 63 is guided to a flow control device 70 of the control valve block 51.
  • the flow control device 70 is designed as an inlet pressure balance, which is arranged in a connecting line 71 connecting the feed line 60 with the tank line 62.
  • the inlet pressure compensator is in this case acted upon in the direction of a blocking position by the load pressure of the consumers 40, 41, 42 present in the load pressure signaling line 63 and a spring 72. In the direction of a flow position, the inlet pressure compensator can be acted upon by the delivery pressure present in the feed line 60.
  • the control valve block 51 has a release valve 73 for releasing the control travel valves 52, 53, 54 and the corresponding movements of the consumers 40, 41, 42.
  • the release valve 73 controls the control pressure line 68 and the load pressure detection line 63 and is electrically actuated.
  • the hydraulic system 1 comprises a pressure medium reservoir 80, which serves to supply the side slide 43 with pressure medium and which can be connected to the working hydraulic pump 2 for charging with pressure medium to the working hydraulic pump.
  • a charging circuit 81 For loading the accumulator 50, a charging circuit 81 is provided.
  • the charging circuit 81 is installed in a accumulator charging section 82 which is attached to the control valve block 51 of the working hydraulic system 2.
  • the charging circuit 81 has a biasing valve 84, which ensures the preferred supply of the accumulator 80 with pressure medium of the working hydraulic pump 45.
  • the biasing valve 84 is the input side to the delivery line 50 of the working hydraulic pump 45 in connection.
  • the biasing valve 84 is the output side to the guided to the control directional valves 52, 53, 54 of the working hydraulics 2 Inlet line 60 and connected to a guided to the accumulator 80 charge line 83.
  • a charging valve 85 of the charging circuit 81 is arranged, by means of which the loading operation of the pressure medium accumulator 80 is controllable.
  • the charging valve 85 is formed in the illustrated embodiment as an electrically controllable pressure reducing valve.
  • the pressure reducing valve is connected at one connection to the section of the charge line 83 guided to the pretensioning valve 84 and at another connection to the section of the charge line 83 leading to the pressure medium reservoir 80.
  • a further connection of the pressure reducing valve is connected to the container line 62.
  • the charging valve 85 is connected to the control with an electronic control device 90 in operative connection.
  • a pressure sensor 91 is provided, which communicates with the electronic control device 90.
  • check valve 89 is arranged in the illustrated embodiment as a check valve, such as spring-biased check valve.
  • the side shifter 43 is controllable by means of a control valve 100 which is connected to the pressure medium accumulator 80 for supply with pressure medium.
  • the control valve 100 of the side valve 43 is connected to the supply of pressure medium from the accumulator 80 by means of a supply line 101 to the charging line 83 between the accumulator 80 and the check valve 89. Further connections of the control-way valve 100 are connected by means of a drain line 102 to the tank line 62 of the control valve block 51.
  • the side shifter 43 is designed as a double-acting consumer, to whose connection to the control-way valve 100 hydraulic connections A4, B4 are provided.
  • the control-way valve 100 is designed as a longitudinal slide valve with a spool.
  • the control-way valve 100 has a neutral position 100a in the form of a middle position, in which the supply line 101, the discharge line 102 and the hydraulic connections A4, B4 are shut off.
  • a first control position 100b the supply line 101 is connected to the hydraulic connection A4 and the discharge line 102 is connected to the hydraulic connection B4.
  • a second control position 100c the supply line 101 is connected to the hydraulic port B4 and the drain line 102 to the hydraulic port A4.
  • the control-way valve 100 is designed as a proportional valve throttling in intermediate positions.
  • the hydraulic connections A4, B4 in the invention include a coding, for example by means of special fittings, which allows only the connection of the side shifter 43 to the control-way valve 100.
  • the control-way valve 100 of the side shifter 43 is electrically operated.
  • the control-way valve 100 of the side-shifter 43 is connected to the electronic control device 90 for activation.
  • the control device 90 is on the input side with a setpoint input device 105 for the side shifter, such as a joystick in operative connection.
  • the additional consumer 42 can be controlled in a second direction of movement.
  • another setpoint input device 106 such as a joystick in combination.
  • the control travel valve 100 of the side slider 43 is acted upon by springs in the neutral position 100a.
  • two electromagnets 104a, 104b are provided in the illustrated embodiment as an electrical actuating device, which actuate and deflect the spool of the control travel valve 100 directly.
  • the control-way valve 100 of the side shifter 43 is disposed and installed in the accumulator charging section 82 together with the valves of the charging circuit 81 of the accumulator 80.
  • the pressure fluid accumulator 80 continues to supply the hydraulic steering device 3 with pressure medium.
  • the supply line 18 of the steering device 3 is connected to the charging line 83 between the check valve 89 and the accumulator 80.
  • the supply according to the invention of the side slide 43 with pressure medium from the pressure medium reservoir 80 of the hydraulic system 1 has a number of advantages.
  • the control-way valve 100 of the side-shifter 43 can be adapted and adjusted to the flow-rate requirement of the side-shifter 43, whereby a good metering of the movements of the side-shifter 43 can be achieved by deflection of the setpoint-setting device 105. Since the side slider 43 has only a small volume flow requirement, results in a small and compact design control travel valve 100, which allows a reduction in the space of the control valve block 51 compared to hydraulic systems of the prior art.
  • the side shifter 43 can be supplied with the required quantity of pressure medium from the accumulator 80 when the control travel valve 100 is activated. Restricting excess flow rate of the working hydraulic pump 45 to the input pressure compensator 70 is prevented, which results in advantages in terms of energy efficiency. In addition, the heat input is reduced in the pressure medium of the hydraulic system 1, whereby the cooling demand decreases.
  • the side shifter 43 can be operated in parallel and independently to a charging operation of the accumulator 80 by the working hydraulic pump 45.
  • control path valve 100 of the side gate 43 in the accumulator charging section 82 offers advantages in the design of the control valve block 51 of the working hydraulics 2, since the control valve block 51 remains unchanged in variants of trucks with or without sideshift 43.

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

Claims (9)

  1. Installation hydraulique (1) pour un engin de travail mobile, en particulier un chariot de manutention, comprenant un système hydraulique de travail (2) qui comprend un entraînement de levage (40) et un coulisseau latéral (43), l'installation hydraulique (1) présentant une pompe hydraulique de travail (45) qui est prévue pour alimenter l'entraînement de levage (40) en fluide sous pression, l'installation hydraulique (1) comprenant un accumulateur de fluide sous pression (80), caractérisée en ce que l'accumulateur de fluide sous pression (80) peut être chargé au moyen d'un circuit de charge (81) en fluide sous pression par la pompe hydraulique de travail (45), le circuit de charge (81) présentant une soupape de précontrainte (84) assurant l'alimentation préférée de l'accumulateur de fluide sous pression (80) en fluide sous pression de la pompe hydraulique de travail (45), la soupape de précontrainte (84) étant en liaison du côté de l'entrée avec une conduite de refoulement (50) de la pompe hydraulique de travail (45) et la soupape de précontrainte (84), du côté de la sortie, étant raccordée à une conduite d'alimentation (60) guidée vers des soupapes de distribution de commande (52, 53, 54) du système hydraulique de travail (2) ainsi qu'à une conduite de charge (83) guidée vers l'accumulateur de fluide sous pression (80), le coulisseau latéral (43) étant raccordé à l'accumulateur de fluide sous pression (80) en vue de l'alimentation en fluide sous pression.
  2. Installation hydraulique selon la revendication 1, caractérisée en ce que le coulisseau latéral (43) peut être commandé au moyen d'une soupape de distribution de commande (100), qui est raccordée à l'accumulateur de fluide sous pression (80) en vue de l'alimentation en fluide sous pression.
  3. Installation hydraulique selon la revendication 2, caractérisée en ce que le circuit de charge (81) de l'accumulateur de fluide sous pression comprend la conduite de charge (83) qui peut être connectée à la conduite de refoulement (50) de la pompe hydraulique de travail (45) pour charger l'accumulateur de fluide sous pression (80), une soupape d'arrêt (89), en particulier un clapet antiretour s'ouvrant dans la direction de l'accumulateur de fluide sous pression (80), étant disposé(e) dans la conduite de charge (83), la soupape de distribution de commande (100) du coulisseau latéral (43) étant raccordée à la conduite de charge (83) entre l'accumulateur de fluide sous pression (80) et la soupape d'arrêt (89) en vue de l'alimentation en fluide sous pression à partir de l'accumulateur de fluide sous pression (80).
  4. Installation hydraulique selon la revendication 2 ou 3, caractérisée en ce que la soupape de distribution de commande (100) du coulisseau latéral (43) peut être actionnée électriquement, un dispositif de commande électronique (90) étant prévu pour commander la soupape de distribution de commande (100) du coulisseau latéral (43), lequel est en liaison fonctionnelle du côté de l'entrée avec un dispositif de prescription de valeur de consigne (105) pour le coulisseau latéral (43), par exemple un joystick.
  5. Installation hydraulique selon l'une quelconque des revendications 2 à 4, caractérisée en ce que la soupape de distribution de commande (100) du coulisseau latéral (43) peut être actionnée au moyen d'un dispositif d'actionnement électrique, par exemple des électroaimants (104a ; 104b) qui actionnent directement un coulisseau de commande de la soupape de distribution de commande (100).
  6. Installation hydraulique selon l'une quelconque des revendications 2 à 5, caractérisée en ce que le circuit de charge (81) de l'accumulateur de fluide sous pression (80) est intégré dans une section de charge d'accumulateur (82) et la soupape de distribution de commande (100) du coulisseau latéral (43) est intégrée dans la section de charge d'accumulateur (82).
  7. Installation hydraulique selon la revendication 6, caractérisée en ce que la section de charge d'accumulateur (82) est montée sur un bloc de soupape de commande (51) du système hydraulique de travail (2).
  8. Installation hydraulique selon l'une quelconque des revendications 2 à 7, caractérisée en ce que pour le raccordement du coulisseau latéral (43) à la soupape de distribution de commande (100) sont prévus des raccords hydrauliques (A4, B4), les raccords hydrauliques (A4, B4) étant munis d'un codage, lesquels autorisent seulement un raccordement du coulisseau latéral (43) et empêchent un raccordement d'un autre consommateur hydraulique.
  9. Installation hydraulique selon l'une quelconque des revendications 1 à 8, caractérisée en ce que l'installation hydraulique (1) comprend un dispositif de direction hydraulique (3) et l'accumulateur de fluide sous pression (80) est prévu pour l'alimentation du dispositif de direction (3) en fluide sous pression.
EP15179000.3A 2014-08-01 2015-07-30 Installation hydraulique d'une machine de travail mobile, notamment d'un chariot de manutention Not-in-force EP2980006B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014110972.4A DE102014110972A1 (de) 2014-08-01 2014-08-01 Hydraulikanlage einer mobilen Arbeitsmaschine, insbesondere eines Flurförderzeugs

Publications (2)

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EP2980006A1 EP2980006A1 (fr) 2016-02-03
EP2980006B1 true EP2980006B1 (fr) 2018-11-21

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EP15179000.3A Not-in-force EP2980006B1 (fr) 2014-08-01 2015-07-30 Installation hydraulique d'une machine de travail mobile, notamment d'un chariot de manutention

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DE (1) DE102014110972A1 (fr)

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2741496A1 (de) * 1977-09-15 1979-03-29 Jungheinrich Kg Flurfoerderfahrzeug mit einer hydraulischen hubzylinderkolbeneinrichtung fuer ein hubgeruest
DE19903174C2 (de) * 1999-01-27 2001-05-31 Kaup Gmbh & Co Kg Anbaugerät für Flurförderzeuge, mit einem Hubmast, insbesondere für Gabelstapler
DE10224731B4 (de) 2001-06-29 2012-09-20 Linde Material Handling Gmbh Hydrostatisches Antriebssystem
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DE102014110972A1 (de) 2016-02-04

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