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EP1369598B2 - Dispositif électro-hydraulique de commande de levage pour véhicules de manutention - Google Patents

Dispositif électro-hydraulique de commande de levage pour véhicules de manutention Download PDF

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Publication number
EP1369598B2
EP1369598B2 EP03002659.5A EP03002659A EP1369598B2 EP 1369598 B2 EP1369598 B2 EP 1369598B2 EP 03002659 A EP03002659 A EP 03002659A EP 1369598 B2 EP1369598 B2 EP 1369598B2
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EP
European Patent Office
Prior art keywords
pressure
pilot
valve
way
proportional
Prior art date
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Application number
EP03002659.5A
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German (de)
English (en)
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EP1369598B1 (fr
EP1369598A1 (fr
Inventor
Martin Dipl.-Ing. Univ. Heusser
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Hawe Hydraulik GmbH and Co KG
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Hawe Hydraulik GmbH and Co KG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/008—Valve failure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/003—Systems with load-holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/4159—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source, an output member and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/465—Flow control with pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance valves

Definitions

  • the invention relates to an electro-hydraulic stroke control device specified in the preamble of claim 1 Art.
  • the three-way flow regulator in the sink branch downstream with the tank and connected to the suction side of the pump for energy recovery.
  • the speed of the hydraulic cylinder is controlled by the speed of the pump, only one black / white 2/2 solenoid valve is provided.
  • From the lifting strand branches off a drain line with a 2/2-way solenoid valve to the tank, which is electrically connected to the passageway during sinking, if no additional consumer is to be supplied. If the three-way current regulator gets stuck in lowering mode as a result of pollution, the lifting cylinder will stop moving in an uncontrolled manner.
  • EP 0 546 300 A EP 0 893 607 A . US 5,701,618 A ,
  • the invention has for its object to provide an electro-hydraulic stroke control device of this type, the reliability is increased against disturbances due to contamination of the hydraulic medium or developing mechanical damage hydraulic switching elements with minimal effort.
  • an additional activatable braking function or intentional active disconnection of one or both current regulator is desirable, or should adjust the supply pressure for at least one other hydraulic consumer in a simple manner with minimal effort leave as eg for lifting control.
  • the mentioned effort relates mainly to magnets as a valve actuator.
  • the reliability of the electro-hydraulic Hub horrettivorides is increased because the redundancy switching element then actively engages when at least one other electrically actuated switching element should not work properly. Due to the active engagement of the redundancy switching element, in particular uncontrolled load movements or unintentional lowering of the load are avoided.
  • the proportional pressure control valve remains stuck in the lowering control or the lifting control, so that it can no longer be adjusted by its proportional magnet (the lifting hydraulic cylinder would then either move under the load or extend against the load), then the effective redundancy switching element is brought in the open position either the pressure compensator of the two-way flow regulator in the load-holding shut-off position (stopping the sinking Hubhydraulikzylinders) or the pressure compensator of the three-way flow regulator in the open position (deriving the flow to the tank, so that the hydraulic cylinder stops).
  • the redundancy switching element With proper function of the Proportionaldruckregelventiis the redundancy switching element has no influence in the respective pilot circuit, since it is energized with energization of the respective proportional solenoid and holds its closed position.
  • the redundancy switching element is an easy-to-integrate safety component and requires only minimal effort. For this function, only the magnet of the switching element and hydraulically a simple, small-sized valve for the pilot oil is required for the control electronics.
  • the redundancy switching element offers further advantageous possibilities, it being necessary to assume that the electronic control provided in modern industrial trucks contains a microprocessor that offers many possibilities for individual program routines or functions.
  • the lowering movement can be additionally braked individually by the pressure compensator of the two-way flow regulator is brought in another way in the closed position, as by the pressure difference of the proportional pressure control valve.
  • a similar individual braking could also be done in the lift control via the pressure compensator of the three-way current controller.
  • the redundancy switching element can actively activate the two-way current controller or the three-way current controller, ie bring the respective pressure compensator into the closed position or full open position.
  • the redundancy switching element as a variable pressure limiting valve change the pilot pressure of the pressure compensator of the three-way flow regulator, which adjusts the supply pressure for at least one further hydraulic consumer, which is lower than that of the lifting hydraulic cylinder. It opens up the redundancy switching element in conjunction with the control electronics possibilities for a more universal control of the industrial truck, the inherent performance of the parent electronics is used without additional effort.
  • the redundancy switching element can, performed by the control electronics and when designed as a proportional pressure control valve, fulfill the function of an electrically adjustable pressure limiting valve, so that the pressure compensator of the three-way flow regulator adjusts a lower supply pressure for further hydraulic consumers. All the aforementioned functions can be achieved with a small valve and a magnet.
  • the redundancy switching element in a fault, for example, the three-way current regulator in the lowering control in its open position as soon as the proportional solenoid of the three-way current regulator is de-energized, the hydraulic cylinder stroke could yield very slowly over the pilot circuit despite the load-holding function of the pressure compensator , For this reason, it is expedient to form the redundancy switching element as a 4/2-way switching valve with a solenoid as the actuator and shut off the pilot line to Senkzweig at least stacker-tight, while the opening pilot side of the pressure compensator is relieved directly to the tank. This results in a perfect load-holding function of the pressure balance, so that the lifting hydraulic cylinder remains reliably stopped even when stuck proportional-pressure relief valve.
  • the redundancy switching element In order to ensure this high safety standard even if the redundancy switching element is to perform the function of reducing the pressure for other consumers, it is expedient to form the redundancy switching element even as a 4/3-way proportional pressure control valve with a proportional solenoid as the actuator and the separate two pilot control lines from Senkzweig and from the closing pilot side of the pressure compensator of the two-way current controller separately. If the 4/3-way proportional pressure control valve de-energized when canceling the lowering control, then it assumes its shutdown, in which relieves the opening pilot side of the pressure compensator of the two-way flow regulator to the tank and the pressure compensator is set to load. This shift position is also assumed when the lift control is canceled.
  • the closing pilot side of the pressure compensator of the three-way flow regulator is relieved to the tank, so that the pressure compensator, if supply pressure is present, is set in the closed position.
  • the proportional solenoid of the 4/3-way proportional pressure control valve is also fully energized. The switching position generated thereby sets the pilot line from the Senkzweig to the opening pilot side of the pressure compensator of the two-way flow regulator on passage and interrupts the connection of the pilot line to the closing pilot side of the pressure compensator of the three-way flow regulator to the tank.
  • the proportional solenoid of the 4/3-way proportional pressure control valve is subjected to a desired current reduction in accordance with the desired pressure reduction against the control spring and the pilot pressure, with which a control function for reducing the pilot pressure for the pressure compensator of Three-way current controller is running. All these functions are achieved with a single valve and a single proportional solenoid.
  • the 4/2-way switching valve or the 4/3-way proportional pressure control valve is designed as a slide valve in stapler-tight design. This means that the valve fulfills the requirement valid for the stacker leak criterion.
  • the redundancy switching element To get along with the smallest possible and weak and therefore cost-effective solenoids or proportional magnets for the redundancy switching element, it is expedient to provide a pressure-balanced with respect to the tank pressure valve slide in the slide valve. If the redundancy switching element also controls the pressure limit for the other consumers, it is particularly expedient to let the pilot pressure, against which the proportional solenoid operates, act only on a small partial area of the valve slide.
  • the electro-hydraulic stroke control device is usable with this design both for lift trucks with an internal combustion engine and an electric motor.
  • the Hublichvorraum can be used without or with energy recovery (Nutzsenken).
  • Nutzsenken For payload operation in which the electric motor is operated as a generator via the pump, it is only necessary to connect the Senkzweig upstream of the pressure compensator of the two-way flow regulator via a Nutztechnisch with the suction side of the pump, and to arrange a check valve between the pump and the tank , At high load pressure and without additional connected hydraulic consumers, the full amount (controlled by the pressure compensator of the two-way flow regulator) can be pumped through the pump.
  • the pressure compensator of the two-way current regulator regulates a current through the pump when it is used, which corresponds to the current demand.
  • the redundancy switching element does not intervene in case of proper function, but only in the case of a fault, and occasionally in the pressure reduction for the other consumers.
  • the electrically operable components of the stroke control device should be connected to an electronic controller including a microprocessor or logic circuit which executes the different operating routines as needed, as selected, or according to an automated scheme.
  • a hydraulic cylinder Z for lifting control from a pressure source P (hydraulic pump) is supplied, which is driven for example by electric motor or diesel engine M and, if no other hydraulic consumers are to be supplied, in the lowering control of the hydraulic cylinder Z may be, or ( Fig. 4 ) then to recover energy as an engine is running.
  • the hydraulic pump sucks from a tank T and acts on a lifting strand 1, in which a three-way flow regulator R1 is provided.
  • the three-way flow regulator R1 consists of a proportional pressure control valve 3, with which the lifting speed is adjusted by a proportional solenoid 4, and a pressure compensator 5 between the lifting strand 1 and the tank T.
  • the pressure control valve 3 is acted upon by spring loading in the direction of the shut-off position. Between the hydraulic cylinder Z and the pressure control valve 3, a pilot control line 6 branches off to the closing pilot side (at which a control spring also acts) of the pressure compensator 5. From the lifting strand 1 branches off upstream of the pressure control valve 3, a further pilot line 7 to the opening pilot side of the pressure compensator 5 from.
  • the two-way flow regulator R2 consists of a pressure control valve 8, with which the lowering speed can be adjusted by means of a proportional solenoid 9, and a pressure compensator 10.
  • the pressure control valve 8 is acted upon by spring force in the direction of the shut-off position in which it is able to keep the load pressure leak-free .
  • a pilot line 11 to closing pilot pressure side 22 of the pressure compensator 10
  • a pilot line 12 to the opening pilot side 19 of the pressure compensator 10 leads.
  • At the opening pilot pressure side also acts a control spring.
  • the two-way current controller R2 is assigned an electrically operable redundancy switching element A, which is energized when the proportional magnet 9 is energized.
  • this is a 2/2-way valve 14 of poppet style, i. with leak-free closed position, which can be brought by a black / white magnet 15 against the derived on its opening pilot side 21 from the pilot pressure in the pilot line 12a pressure in the closed position shown.
  • the redundancy switch A is e.g. arranged parallel to the pressure relief valve 13 in the wiring harness.
  • the load pressure is held by the pressure regulating valve 8.
  • the proportional solenoid 9 receives current whose strength corresponds to the desired lowering speed.
  • the black / white magnet 15 is energized by a higher-level control, not shown, so that the redundancy switching element A assumes its shut-off position (as shown).
  • the pressure control valve 8 can flow with the energization of the proportional solenoid 9 via a metering orifice pressure medium, the pressure compensator 10 keeps the pressure difference across the orifice and thus the lowering speed constant.
  • the pressure compensator 10 adjusts itself to a position which depends on the pilot control pressures in the pilot control lines 11 and 12 and its control spring (load independence).
  • the de-energization of the proportional solenoid 9 and the black / white magnet 15 of the redundancy switching element A is de-energized, so that the redundancy switching element A abruptly by the pilot pressure in the pilot line 12a in its open position and the pilot pressure to the tank ,
  • the pressure compensator 10 is brought from the pilot pressure in the pilot control line 11 in its closed position and holds the load pressure.
  • the hydraulic cylinder Z comes to a stop.
  • the redundancy switching element A could also be energized and de-energized once or several times in the event of the pressure compensator 10 getting stuck in order to make the pressure balance 10 common again.
  • the redundancy switching element A is assigned to the three-way current regulator R1 for lifting control. That is, the redundancy switching element A is contained in a branched from the pilot line 6 to Schellervor Kunststoffseite 20 of the pressure compensator 5 pilot line 6a to the tank and provides a way to actively intervene in the event of a fault. For example, should the pressure compensator 5 become stuck due to a malfunction in a middle position, further extension of the hydraulic cylinder Z could be prevented by bringing the pressure control valve 3 into its closed position by means of the proportional magnet 4.
  • the pressure control valve 3 should hang, then the hydraulic cylinder Z would possibly be brought to a halt by switching off the motor M, but then not reliable, if at the same time other hydraulic consumers from the pressure source must be supplied with.
  • the 2/2-way valve 14 from the pilot pressure in the pilot line 6, 6a brought quickly into its open position, so that the pilot pressure is abruptly reduced to the tank and the pressure compensator 5 is brought by the prevailing pressure in the lifting strand 1 via the pilot line 7 in the full open position in which the pressure fluid from the lifting strand 1 derived to the tank and the hydraulic cylinder Z is brought to a standstill.
  • the redundancy switching element A could be used in repeated energization and de-excitation to make the hanging pressure compensator 5 common again.
  • Fig. 3 is the electrohydraulic stroke control device S combined with additional controls SH, SH 'for further hydraulic consumers of the industrial truck with common supply from the pressure source P is present.
  • the control SH is used, for example, to actuate a further hydraulic consumer Z ', for example a tilting cylinder or a gripper cylinder, which requires a lower supply pressure than the hydraulic cylinder Z.
  • the load pressure via a pilot line 6b to the pilot line 6 and then brought to Sch.vor Kunststoffseite 20 of the pressure compensator 5, via a shuttle valve 16, the respective higher control pressure to the closing pilot side 20 of the pressure compensator 5 transmits.
  • the pressure compensator 5 regulates the respectively required pressure.
  • the redundancy switch A in this embodiment is operatively associated alternately with both the two-way current regulator R2 and the three-way current regulator R1 via a shuttle valve 17 (or, as in FIG 4 and 5 shown via two separate pilot control lines).
  • a shuttle valve 17 or, as in FIG 4 and 5 shown via two separate pilot control lines.
  • From the pilot control line 12 of the two-way flow controller R2 branches off a pilot line 12 'to the shuttle valve 17.
  • a pilot line 6 ' which branches off from the pilot line 6 of the three-way current regulator R1.
  • the respective higher pilot pressure is transmitted to the pilot line 18, in which optionally the pressure relief valve 13 and the redundancy switching element A are arranged.
  • the redundancy switch A is in Fig. 3 a 2/2-way proportional pressure control valve 14 ', which is acted upon by the pilot pressure in the pilot line 18 in the opening direction at its ⁇ réellesvor Tavernseite 21, and can be adjusted by a proportional solenoid 15' in the direction of the closed position shown.
  • the energization of the proportional magnet 15 ' takes place simultaneously with the energization of the proportional magnet 4 in the lifting control, while in the lowering control simultaneously with the energization of the proportional magnet 9.
  • the proportional solenoid 15' can not only set the closed position of the redundancy switching element A, but let Optionally, depending on a weaker energization with sole or additional actuation of the hydraulic cylinder Z 'set intermediate positions to lower the pilot pressure in the pilot line 18 for the pressure compensator 5.
  • the redundancy switching element fulfills the function of an electrically adjustable pressure relief valve for adjusting the pilot pressure at the closing pilot side 20 of the pressure compensator 5, e.g. in order to set a lower supply pressure for the further hydraulic consumer Z '.
  • the redundancy switch A of this design could also be used for intentionally reducing the pilot pressure level for the lift and / or lower control.
  • the shuttle valve 17 In the lift control, the shuttle valve 17 is in its left position, so that prevails in the pilot line 18, the pilot pressure from the pilot line 6. If the pressure control valve 3 get stuck, although the proportional solenoid 4 is de-energized, the proportional solenoid 15 'is de-energized, so that the redundancy switching element A via the pilot pressure in the pilot line 18 abruptly assumes its open position and degrades the pilot pressure to the tank.
  • the pressure compensator 5 is abruptly in its open position in which the pressure medium is discharged directly to the tank and the hydraulic cylinder Z stops its extension movement, wherein the load pressure of a check valve downstream of the pressure control valve 3 and the pressure control valve 8 is maintained.
  • the shuttle valve 17 assumes the position shown, so that in the pilot line 18, the pressure of the pilot line 12 and 12 'prevails. If the pressure control valve 8 get stuck, then, as explained above, via the going into its open position redundancy switching element A, the pressure compensator 10 is brought into its closed position and held the load pressure of the hydraulic cylinder Z.
  • the proportional electronic control unit 15' is supplied with current only to such an extent by the superordinate electronic controller CU, which expediently contains a microprocessor or another logic circuit, that the pressure regulating valve 14 'assumes an intermediate position and regulates one Part of the pressure medium from the pilot pressure line 18 to the tank discharges to reduce the pilot pressure at the closing pilot side 20 of the pressure compensator 5, so that the pressure compensator 20 now controls relatively more pressure fluid to the tank and reduces the supply pressure in the pressure line 1 '.
  • redundancy switching element A which shuts off the pilot line 12 to Senkzweig 2 with de-energized solenoid 15 or proportional solenoid 15 'and the opening pilot side 19 of the pressure compensator 10 via a pilot line 12 b relieved directly to the tank.
  • the redundancy switching element A is a 4/2-way switching valve 14 "with a solenoid 15 as an actuator against a spring 26.
  • the redundancy switching element A is not used to set a lower supply pressure for other hydraulic consumers, but to secure the current regulator R1, R2 in the case of a fault and possibly for arbitrary release of the respective pressure balance for other reasons, eg for the purpose of individual braking or other security reasons.
  • the 4/2-way switching valve 14 is a spool valve having a spool 27 which is pressure balanced with respect to tank pressure.”
  • the switching valve 14 is between the two pilot lines 12 (from the drawstring 2) and 6a (from the closing pilot side 20) of the pressure compensator 5 and optionally the shuttle valve 16 and the tank T and the pilot control line 12b to the opening pilot side 19 of the pressure compensator 10 are arranged.
  • de-energized solenoid 15 (this may be a simple black and white solenoid) is the switching position shown in which the pilot lines 12, 12b separated from each other and the pilot lines 6a and 12b are relieved together in a bypass 24 in the valve spool 27 to the tank T.
  • a switching position is set in which the pilot line 6a separated from the tank T and the pilot lines 12, 12b are connected to each other.
  • a Nutzsenk effet 2 a which branches off between the proportional pressure control valve 8 and the pressure compensator 10 from the Senkstrang 2 and is connected to the suction side of the pump P.
  • a check valve V is indicated, which blocks in the direction of the tank to promote the lowering of the pressure fluid through the pump P and to drive this as a motor for the then working as a generator electric motor for energy recovery.
  • the pressure medium then flows via the pressure compensator 20 to the tank, or, if further hydraulic consumers are connected and supplied, on. If a speed-controllable pump P is used, the pressure compensator 10 is set in the case of the connection of additional hydraulic consumers, the amount just required each time by the pump P.
  • the pay reduction option can be easily integrated into any embodiment shown.
  • the redundancy switch A is a 4/3-proportional pressure control valve 14 "having the proportional solenoid 15 'as an actuator of the valve spool 27' against the force of a spring 26 and the pilot pressure in a pilot line 6c branching from the pilot line 6a further interconnection corresponds to in Fig. 4 shown and already explained.
  • the valve spool 27 ' is pressure balanced with respect to the tank pressure via the pilot line 25, expediently over the entire surface, while the pilot pressure from the pilot line 6c expediently only a portion of the surface of the valve spool 27 against the proportional magnet 15' applied to a weak and compact or inexpensive proportional magnet 15th 'to be able to use.
  • pilot pressure at the closing pilot side 20 of the pressure compensator 5 in the lift control or in controlling further hydraulic consumers to reduce their supply pressure e.g. the proportional solenoid 15 'in accordance with the desired pilot pressure in the pilot line 6a energized weaker than in the protection of the respective current regulator to take between end positions with significant coverage regulating intermediate switch positions in which both the pilot lines 12, 12b are connected to each other and the pilot line 6a directly connected to the tank.

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

Claims (6)

  1. Dispositif électro-hydraulique de commande de levage (S) pour véhicules de manutention, en particulier des chariots élévateurs, avec une ligne de levage (1) entre une source de pression (P) et un cylindre hydraulique (Z), avec un régulateur de débit à trois voies (R1), actionnable électriquement au moins pour la commande de levage, avec un aimant proportionnel et une balance de pression (5), et avec une ligne d'abaissement (2), en dérivation de la ligne de levage (1) en direction du réservoir, qui comporte pour la commande d'abaissement un régulateur de débit à deux voies (R2) actionnable électriquement avec un aimant proportionnel et une balance de pression (10), caractérisé en ce qu'un organe de commutation redondant (A), actionnable activement par voie électrique par un actuateur entre des positions finales de fermeture et d'ouverture, est prévu entre le réservoir (T) et un côté pilote d'ouverture (19) de la balance de pression (10) du régulateur de débit à deux voies (R2) et un côté pilote de fermeture (20) de la balance de pression (5) du régulateur de débit à trois voies (R1), que l'organe de commutation redondant (A) est une soupape de commutation à 4/2-voies (14'') avec un aimant par tout ou rien (15), ou une soupape de regulation de pression proportionnelle à 4/3-voies (14'''), avec un aimant proportionnel (15'), le aimant par out ou rien (15) ou le aiment proportionnel (15') entant qu' actuateur pour actionner l'organe de commutation redundant (A) dans une direction de commutation entre des positions finales de fermeture et d'ouverture, que séparées une premiere conduite pilote (12) etends à la ligne d'abaissement (2), une deuxieme conduite pilote (6a) etends au côté pilote de fermeture (20) de la balance de pression (5) du régulateur de débit à trois voies (R1), une troisieme conduit pilote etends au réservoir (T), et une quatrieme conduite pilote (12b) etends, au côté pilote d'ouverture (19) de la balance de pression (10) du régulateur de débit à deux voies (R2), que l'organe de commutation redondant (A) sépare les deuxieme et troisieme conduites pilotes et relie les premiere et quatrieme conduites pilotes (12, 12b) dans une position de commutation finale, et sépare les premiere et quatrieme conduites pilotes (12, 12b) et relie les deuxieme et troisieme conduites pilotes (6a, 12b) avec la réservoir (T) dans une autre position de commutation finale, que l'organe de commutation redondant (A) qui est la soupape de regulation de pression proportionelle à 4/3-voies (14''') est actionnée par l'aimant proportionnell (15'), dans des positions de commutation intermédiaires entre les positions de commutation finales pour le réglage d'une pression pilote voulue dans la deuxieme conduite pilote (6a), par relient les premiere et quatrieme conduites pilotes et les deuxieme et troisieme conduites pilotes, que la balance de pression (5) du régulateur de débit à trois voies (R1) est disposée en supplément pour la commande, indépendant de la charge, d'au moins un autre consommateur hydraulique (Z'), alimenté par la même source de pression (P), et qu'une pression d'alimentation plus basse pour l'autre consommateur hydraulique (Z'), qu'au moins pour la commande de levage du cylindre hydraulique (Z), est réglable par l'intermédiaire de l'organe de commutation redondant (A) et de la balance de pression (5) du régulateur de débit à trois voies (R1).
  2. Dispositif électro-hydraulique de commande de levage suivant la revendication 1, caractérisé en ce que la soupape de commutation à 4/2-voies (14'') ou la soupape de régulation de pression proportionnelle à 4/3-voies (14''') est une soupape à coulisse en réalisation étanche au chariot élévateur.
  3. Dispositif électro-hydraulique de commande de levage suivant la revendication 1, caractérisé en ce que la soupape de commutation à 4/2-voies (14'') comporte une coulisse de soupape (27) équilibrée en pression aux deux extrémités, sur une grande surface, par rapport au réservoir (T).
  4. Dispositif électro-hydraulique de commande de levage suivant la revendication 1, caractérisé en ce que la soupape de régulation de pression proportionnelle à 4/3- voies (14''') comporte une coulisse de soupape (27') équilibrée en pression aux deux extrémités/ sur toute la surface, par rapport au réservoir (T), qui n'est sollicitée en pression pilote dans la conduite pilote (6a) que sur une surface partielle contre l'aimant proportionnel (15').
  5. Dispositif électro-hydraulique de commande de levage suivant l'une au moins des revendications 1 à 4, caractérisé en ce que la source de pression (B) présente une pompe à vitesse de rotation réglable avec un moteur électrique (M), qui peut fonctionner par l'intermédiaire de la pompe, lors de la commande d'abaissement, en tant que générateur pour la récupération d'énergie, qu'une soupape anti-retour (V) , fermant en direction du réservoir, et prévue entre la pompe et le réservoir (T), et qu'une conduite d'abaissement utile (2a), en dérivation de la ligne d'abaissement (2) en amont de la balance de pression (10) du régulateur de débit à deux voies (R2), est raccordée à la pompe en aval de la soupape anti-retour (V).
  6. Dispositif électro-hydraulique de commande de levage suivant l'une au moins des revendications précédentes, caractérisé en ce que les composants (4, 9, 15, 15', M), actionnables activement par voie électrique du dispositif de commande de levage (S), sont reliés à une commande électronique (CU) qui comporte un microprocesseur ou un circuit logique.
EP03002659.5A 2002-06-03 2003-02-11 Dispositif électro-hydraulique de commande de levage pour véhicules de manutention Expired - Lifetime EP1369598B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE20208577U 2002-06-03
DE20208577U DE20208577U1 (de) 2002-06-03 2002-06-03 Elektrohydraulische Hubsteuervorrichtung für Flurförerfahrzeuge

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EP1369598A1 EP1369598A1 (fr) 2003-12-10
EP1369598B1 EP1369598B1 (fr) 2007-09-26
EP1369598B2 true EP1369598B2 (fr) 2015-08-19

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US (1) US6837045B2 (fr)
EP (1) EP1369598B2 (fr)
JP (1) JP3785159B2 (fr)
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016209509A1 (de) 2016-06-01 2017-12-07 Robert Bosch Gmbh Hydraulisches Antriebssystem für Gabelstapler

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10357631B4 (de) 2003-01-29 2019-05-16 Buchholz Hydraulik Gmbh Steuereinrichtung für eine Hub- und Senksteuerung
DE10303385B4 (de) 2003-01-29 2018-11-29 Buchholz Hydraulik Gmbh Steuereinrichtung für eine Hub- und Senksteuerung
ATE398302T1 (de) * 2003-02-28 2008-07-15 Gottwald Port Tech Gmbh Verfahren und vorrichtung zum sicherheitsabschalten von elektroantrieben
DE10344480B3 (de) * 2003-09-24 2005-06-16 Sauer-Danfoss Aps Hydraulische Ventilanordnung
DE102004005402B4 (de) * 2004-02-03 2006-01-05 Jungheinrich Aktiengesellschaft Ventilanordnung für das Heben und Senken eines Hubzylinders
DE102004039848A1 (de) * 2004-08-17 2006-03-09 Jungheinrich Ag Fluidschaltung und Flurförderzeug mit Fluidschaltung
DE102004042881A1 (de) * 2004-09-04 2006-03-09 Jungheinrich Aktiengesellschaft Vorrichtung zur Notabsenkung eines Lasttragmittels bei einem Stapler
DE202004014030U1 (de) 2004-09-08 2006-01-12 Hawe Hydraulik Gmbh & Co. Kg Elektrohydraulische Steuervorrichtung
DE502005000989D1 (de) 2005-08-11 2007-08-16 Hawe Hydraulik Gmbh & Co Kg Elektrohydraulische Vorrichtung
DE102006003414B3 (de) * 2006-01-24 2007-08-02 Sauer-Danfoss Gmbh & Co Ohg Hydraulische Schaltungsanordnung
US7657814B2 (en) * 2006-02-23 2010-02-02 Rockwell Automation Technologies, Inc. Optimizing availability and safety by reconfiguring and auto-adjusting redundancy
DE102006060351B8 (de) * 2006-12-20 2008-07-24 Sauer-Danfoss Gmbh & Co Ohg Hydraulische Schaltungsanordnung mit Energierückgewinnung
DE102007028864A1 (de) * 2007-03-27 2008-10-02 Robert Bosch Gmbh Hydraulische Steueranordnung
JP2009022651A (ja) * 2007-07-23 2009-02-05 Ge Medical Systems Global Technology Co Llc 昇降装置およびその制御方法、並びに撮影装置
DE102007034746B4 (de) 2007-07-25 2022-11-17 Still Gesellschaft Mit Beschränkter Haftung Hydrostatisches Antriebssystem
ATE521568T1 (de) 2009-04-03 2011-09-15 Hawe Hydraulik Se Hubmodul
GB2469484B (en) * 2009-04-15 2013-09-18 Ge Aviat Systems Ltd Landing gear actuation control system
EP2325390B2 (fr) * 2009-10-20 2019-06-26 Joseph Vögele AG Poutre lisseuse et finisseuse de route
US9360023B2 (en) * 2013-03-14 2016-06-07 The Raymond Corporation Hydraulic regeneration system and method for a material handling vehicle
EP2985473B1 (fr) 2014-08-11 2017-10-11 HAWE Hydraulik SE Module de levage
CN104179460B (zh) * 2014-08-18 2016-04-13 阿特拉斯科普柯(南京)建筑矿山设备有限公司 牙轮钻机的塔架升降装置
EP3037678B1 (fr) * 2014-12-23 2017-05-24 HAWE Hydraulik SE Module de levage
DE102016003972A1 (de) * 2016-04-01 2017-10-05 Hydac System Gmbh Steuervorrichtung
DE102018202148B3 (de) * 2018-02-12 2019-03-07 Hawe Hydraulik Se Hydraulikventilverband mit Zwangsschaltung und Mobilhydrauliksystem
DE102018001303A1 (de) * 2018-02-20 2019-08-22 Hydac Fluidtechnik Gmbh Ventilvorrichtung
DE102019111295A1 (de) * 2019-05-02 2020-11-05 Jungheinrich Aktiengesellschaft Hydraulikanordnung für ein Flurförderzeug
US12188467B2 (en) * 2020-06-09 2025-01-07 Danfoss Power Solutions Inc. Hydraulic control system for linear actuation
IT202300003168A1 (it) * 2023-02-23 2024-08-23 Valvole Italia S R L Dispositivo di controllo discesa per un cilindro oleodinamico, in particolare per il controllo della discesa di un braccio operatore

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10045232A1 (de) † 2000-09-13 2002-03-28 Bosch Gmbh Robert Steuerungsvorrichtung für einen hydraulischen Volumenstrom
DE10224731A1 (de) † 2001-06-29 2003-01-16 Linde Ag Hydrostatisches Antriebssystem

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4401009A (en) * 1972-11-08 1983-08-30 Control Concepts, Inc. Closed center programmed valve system with load sense
US4065922A (en) * 1976-08-23 1978-01-03 Hyster Company Load lifting and lowering control system
JPS54162353A (en) * 1978-06-13 1979-12-22 Toshiba Corp Hydraulic circuit for driving cargo handling apparatus
DE3621854A1 (de) * 1986-06-30 1988-01-07 Rexroth Mannesmann Gmbh Steuerschaltung fuer ein hydraulisches kraftheber-regelsystem
DE4106845A1 (de) * 1991-03-04 1992-09-24 Deere & Co Hydrauliksystem zur steuerung einer einen verbraucher bewegenden kraft
DE4133892C1 (fr) * 1991-10-12 1992-12-24 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4140409A1 (de) 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Elektrohydraulische steuereinrichtung
DE4140408A1 (de) 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Elektrohydraulische steuereinrichtung
DE4239321C2 (de) * 1992-11-23 1995-11-09 Heilmeier & Weinlein Elektrohydraulisches Hubmodul
KR960010228B1 (ko) * 1993-10-25 1996-07-26 이희종 유압엘리베이터용 제어밸브장치
DE9317308U1 (de) 1993-11-11 1995-03-16 Brugger, Klaus, Dipl.-Ing., 83700 Rottach-Egern Hydrauliksystem für die hydraulische Betätigung eines Krankenwagen-Hubtisches
EP0877863A1 (fr) * 1996-01-30 1998-11-18 Mannesmann Rexroth AG Dispositif hydraulique de commande de la circulation d'un fluide hydraulique
DE29713293U1 (de) 1997-07-25 1997-10-23 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Magnetbetätigtes Ablaßventil
DE10010670C2 (de) 2000-03-04 2003-11-06 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10045232A1 (de) † 2000-09-13 2002-03-28 Bosch Gmbh Robert Steuerungsvorrichtung für einen hydraulischen Volumenstrom
DE10224731A1 (de) † 2001-06-29 2003-01-16 Linde Ag Hydrostatisches Antriebssystem

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016209509A1 (de) 2016-06-01 2017-12-07 Robert Bosch Gmbh Hydraulisches Antriebssystem für Gabelstapler

Also Published As

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DE50308262D1 (de) 2007-11-08
US20030221548A1 (en) 2003-12-04
US6837045B2 (en) 2005-01-04
EP1369598B1 (fr) 2007-09-26
DE20208577U1 (de) 2003-12-11
EP1369598A1 (fr) 2003-12-10
JP2004044795A (ja) 2004-02-12
JP3785159B2 (ja) 2006-06-14

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