EP1331199B1 - Steuervorrichtung, insbesondere für den Einsatz bei hydraulisch arbeitenden Hubeinrichtungen - Google Patents

Steuervorrichtung, insbesondere für den Einsatz bei hydraulisch arbeitenden Hubeinrichtungen Download PDF

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Publication number
EP1331199B1
EP1331199B1 EP02025356A EP02025356A EP1331199B1 EP 1331199 B1 EP1331199 B1 EP 1331199B1 EP 02025356 A EP02025356 A EP 02025356A EP 02025356 A EP02025356 A EP 02025356A EP 1331199 B1 EP1331199 B1 EP 1331199B1
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EP
European Patent Office
Prior art keywords
pressure
throttle valve
unblocking
valve
control
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.)
Expired - Lifetime
Application number
EP02025356A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1331199A2 (de
EP1331199A3 (de
Inventor
Hermann Albert
Peter Bruck
Alois Hoffmann
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
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Filing date
Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP1331199A2 publication Critical patent/EP1331199A2/de
Publication of EP1331199A3 publication Critical patent/EP1331199A3/de
Application granted granted Critical
Publication of EP1331199B1 publication Critical patent/EP1331199B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B20/002—Electrical 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • 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
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/41581—Flow control characterised by the connections of the flow control means in the circuit being connected to 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/575—Pilot pressure control
    • F15B2211/5756—Pilot pressure control for opening a valve
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7052—Single-acting output members
    • 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
    • F15B2211/72—Output members, e.g. hydraulic motors or cylinders or control therefor having locking means

Definitions

  • the invention relates to a control device, in particular for use in hydraulically operated lifting devices for raising and lowering loads, with a connected to a return line of the lifting device, electrically controllable throttle valve and a pressure compensator, which is provided with at least one blocking and a control position and which cooperates with an unlocking device.
  • a pertinent hydraulic control device is known from DE 44 23 644 C2.
  • the known hydraulic control device is intended for use in the area of lifting devices, in particular for lifting masts of forklifts, having a feed pump connected to a reservoir for hydraulic fluid as a pressure supply and connected to a return line control piston which acts as a pressure compensator, and in which the return line is connected to the reservoir.
  • the control piston has an inlet which is connected in the conveying direction of the pump behind a check valve to a pump connecting to the lifting conveyor line and which is connected via a control line to a connecting line between the pump and the check valve, that the control piston is formed in the lowering direction as a discharge pressure balance and in the stroke direction as a circulation pressure balance.
  • the control piston is loaded by a spring to the opposing acting a biasing spring is arranged, which is taken over its spring force interconnection of a control piston as an open pressure balance on the one hand in the idle state without external action a passage position, and as a closed pressure balance on the other is taken in the resting state without external action, a blocking position, pretends.
  • the control arrangement is designed in the lowering direction of the lifting device as a two-way - current regulator and in the stroke direction as a three-way current regulator. For a switching of the control piston from the function as a discharge pressure balance in the function as a circulation pressure balance, an evaluation of a pressure difference in the region of the check valve is made.
  • a metering orifice designed as a throttle valve is arranged between the control piston and the lifting device, and the throttle valve itself forms a two-way valve.
  • a valve arrangement in whose housing a spring-loaded in the closing direction valve body is arranged.
  • the pertinent valve body controls the flow through a fluid channel whose input can be connected to a constant-displacement pump and whose outlet can be connected to a tank.
  • On the not acted upon by the pump pressure side of the valve body is a control chamber.
  • a throttle is arranged between the fluid channel and the control chamber.
  • a switching valve connects in its rest position the control chamber with the Tank and interrupts this connection in his working position.
  • a switchable abutment for the spring increases in the working position of the switching valve, the bias of the spring relative to the rest position of the valve.
  • valve body and the slide of the switching valve are arranged in a common bore, wherein a spring is guided between the valve body and the slide.
  • the slide of the switching valve is used at least at interrupted connection between the control chamber and the tank as an abutment for the spring.
  • the valve assembly in particular as a relief valve for a supplied by a constant pump consumer used, for example in the form of a conventional forklift, the known hydraulic valve assembly in addition to an operating state “hold” for the fork, the operating conditions “lifting slowly” and “Lifting fast”, as well as “lowering slowly” and “lowering fast” allows.
  • the invention has the object, while maintaining the advantages of the known solution, namely to provide a compact constructive control device at low manufacturing costs available, which allows a high lowering speed with empty fork in normal operation, so to further improve in that even in the event of an accident, the safety is significantly increased and there can not be an undesired lowering of the lifting device with or without load.
  • This object is achieved by a hydraulic control device with the features of claim 1 in its entirety.
  • the pressure balance in its normal position, the return line blocks that by controlling the unblocking the pressure compensator when lowering the load assumes its control position and rouge.
  • a failure of the throttle valve by means of the unbolting the pressure compensator in its locked position brought is or in case of failure of the pressure balance, the throttle valve assumes its blocking position, the actual load holding function by two series-connected closed hydraulic actuators, which are individually controlled electrically realized.
  • both a hydraulic and an electrical redundancy of the load-holding function is given. Due to the redundant arrangement, the lowering movement is stopped automatically and safely even if one of the two electric or one of the two hydraulic actuators of pressure compensator and throttle valve fails.
  • the throttle valve is closed in the normal position and is electrically driven preferably via a proportional pressure control valve.
  • the pressure compensator is designed as a discharge pressure balance so that it also remains closed in the normal position and occupies the open control position only when pressing the lowering function.
  • the pressure compensator piston is held in the normal position by a spring in the blocking position. Only by controlling an unblocking device via a directional control valve with pending lowering signal is the unlocking of the piston and the pressure compensator can regulate. If, for example, the piston of the throttle valve then remains in the open position in the event of an error after switching off the lowering signal, the load movement is stopped by closing the pressure compensator (fail-safe position).
  • the solution according to the invention can be implemented inexpensively and, secondly, the lowering speed when lowering without load is not unnecessarily reduced by an additional flow resistance.
  • the unblocking device is a Entsperrzylinder with an energy storage, preferably in the form of a compression spring, which seeks to keep the pressure balance in its locked position, wherein a pressure supply via a switch-engageable counteracts with its fluid pressure of the pertinent force direction of the unlocking.
  • the unlocking device is thus able to push the pressure compensator in the direction of its blocking position via its force accumulator and to hold it securely in this blocking position.
  • the Entsperrzylinder and the pressure compensator are mechanically coupled to each other via an actuating piston of the unlocking cylinder.
  • a control line is connected to the return line between the lifting device and the throttle, which passes the pending hydraulic pressure as a control signal to the pressure compensator, wherein by means of a tap line of the upcoming hydraulic pressure between the throttle valve and pressure compensator as another control signal the opposite Direction of action is passed to the pressure compensator.
  • FIG. 1 shows in the manner of a circuit diagram an embodiment of the hydraulic control device, wherein the structural components shown there are shown only insofar as they relate to the lowering function for a hydraulically operating lifting device 10 with a load compensation and a redundant safety switching device.
  • the lifting device 10 is constructed in the manner of a hydraulic working cylinder with a working piston 12 and an actuating rod 14.
  • the actuating rod 14 is connected at its one free end to the working piston 12 and at its other free end with a load receiving device 16, for example, with a piece goods 18 is loaded as a load.
  • the working piston 12 within the cylinder housing divides this into a piston chamber 20 and a rod space 22.
  • the lifting device 10 is intended represent a mast from a forklift truck; However, it could well consist of a hydraulically operated Aufzug Surprise od. Like. Exist, with several lifting devices 10 in apparent successive series or series arrangement could trigger one or more lifting operations (not shown).
  • valve block 28 Between the lifting device 10 and a fluid reservoir 24 (tank), a valve block designated as a whole by 28 is connected in a return line 26.
  • the valve block 28 in this case has a connection A for the connection of the lifting device 10 and a connection T for the connection of the fluid reservoir 24.
  • the valve control block 28 has a connection point P for pressure supply, for example in the form of a hydraulic pump 30, the with its suction side to the fluid reservoir 24 is also connected. The pressure supply could also be done internally via the hydraulic circuit of the forklift.
  • the valve block 28 has a connected to the return line 26 pressure compensator 32, which is also referred to with discharge pressure balance on.
  • the pressure compensator 32 is shown in its unactuated normal position 34 in FIG. 1, in which it blocks the return line 26 from the fluid reservoir 24. In addition to this normal or blocking position 34, the pressure compensator 32 has a control position 36 with throttle function. On its one side actuation with pressure control spring 40, the pressure compensator 32 is connected to a tap line 42 which is connected in the return line 26 between the throttle and pressure compensator 32.
  • the pressure compensator 32 cooperates with an unlocking device 44, which is constructed in the manner of an unlocking cylinder with a piston rod part 46, which via an energy store 48 in the form of a compression spring, the pressure compensator 32 in its normal or to keep blocking position 34.
  • the energy accumulator 48 is arranged in the piston chamber 50, in particular in the form of a piston ring space, the unlocking cylinder and the rod annulus 52 of the unlocking cylinder is connected via a fluid-conducting connection line 54 to the output X of a switching device 56 in the form of a custom-built 3/2-way valve.
  • the switching device 56 is connected via the terminal P to the pressure supply 30. According to the illustration of Figure 1, the switching device 56 is shown in its blocking the connection of connecting line 54 with the pressure supply 30, wherein in the pertinent blocking position, the connecting line 54 is connected via the drain line 58 to the return line 26 and thus to the fluid Storage container 24.
  • a throttle valve 60 is connected, which consists of a 2/2-way proportional slide valve with a pilot unit 62 which is permanently connected via a direct connection 64 to the pressure supply 30.
  • the pilot unit 62 which is formed in the manner of a proportional pressure regulating valve, is connected to the fluid reservoir 24, and on its output side Y, the pilot unit 62 is in driving connection with the operating side of the throttle valve 60
  • the pressure compensator 32 is held in its locked position, which is ensured at no pressure in the line 54 that the unlocking device 44 brings the pressure compensator 32 in its locked position.
  • the energy storage 48 can relax and pushes the piston rod part 46 with the result that the pressure compensator 32 reaches the normal or blocking position 34.
  • the existing residual stress the energy storage 48 is sufficient in any case, reliable in any operating situation to bring the pressure compensator piston 68 in its blocking position.
  • a first safety step is already fulfilled and so ensured that in case of failure not accidentally the pressure compensator 32 remains in its open position 38 or control position 36.
  • a control line 66 is connected to the connection point Z, which passes on the pending hydraulic pressure as a control signal to the pressure compensator 32. If the throttle valve 60 remains in its closed position shown in FIG. 1, the volume flow displaced from the piston chamber 20 when the load 18 is lowered would be picked up at the connection point Z and passed on to the control line 66, which then acts in the same effective direction as the energy store 48 would then seek to hold the pressure compensator 32 in its blocking position 34 or to bring it to.
  • FIG. 2 firstly shows the normal position of the lowering function, as represented in the circuit diagram in FIG.
  • the discharge pressure compensator 32 is shown in its normal or blocking position 34, in which the tank connection T is decoupled from the return line 26.
  • the unlocking device 44 is with its piston rod part 46 in abutment with the control piston 68 of the Pressure compensator 32 and the energy storage in the form of the compression spring 48 is relaxed to a predeterminable residual stress.
  • the throttle valve 60 with the Wegeschieberkolben 70 is in operative connection with the pilot unit 61, wherein the terminal A is separated via the return line 26 from the tank port T.
  • a lowering signal is given via a corresponding actuating device, such as a joy stick (not shown), and the switching device 56 is activated simultaneously and automatically, the pressure supply 30 being pressurized during operation is connected to the connecting line 54.
  • the fluid pressure of the pressure supply 30 then penetrates into the rod annulus 52 of the unlocking device 44 and pushes the piston rod part 46 in the direction of the Fig.1 seen to the right against the action of the energy storage 48 in the corresponding housing parts. But then comes the control position 36 of the pressure compensator 32 in the fluid-conducting connection position between the piston chamber 20 and the fluid reservoir 24 via the return line 26.
  • the load device 16 could be lowered in an uncontrolled manner with its load 18 in the control position according to FIG.
  • the switching device 56 is no longer activated, this assumes their blocking position shown in Figure 1 and the connecting line 54 to the unlocking device 44 is held without pressure. In this case, in turn pushes the energy storage 48, the piston rod unit 46 and brings the pressure compensator 32 in its normal or blocking position 34. Should this lead to a malfunction, for example, the switching device 56 should remain in its switched-position or the pressure compensator 32 is an inhibition have, then still a shutdown via the throttle valve 60 is possible, which would assume its blocking position 63 shown in Figure 1 under the influence of its actuating spring.
  • the pressure compensator 32 is in any case able, via its mechanical unlocking cylinder unit 44, to interrupt the lowering function directly.
  • the pertinent interruption position is shown in Figure 4, in which the control piston 68, the connection between the return line 26 and junction T to the fluid reservoir 24 safely interrupts.
  • both the control piston 68 and the directional spool 70 is connected in an open passage position or in a throttle position, so that such to achieve a fast lowering function controlled. This takes place automatically when the load pressure is less than the control pressure.
  • the current controller according to the invention with redundant stop function thus allows a load-independent specification of the speed and a high lowering speed even when the fork is empty and at the same time sensitively metering the lowering speed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Transportation (AREA)
  • Analytical Chemistry (AREA)
  • Structural Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • Civil Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Lifting Devices For Agricultural Implements (AREA)
  • Control And Safety Of Cranes (AREA)
EP02025356A 2002-01-24 2002-11-14 Steuervorrichtung, insbesondere für den Einsatz bei hydraulisch arbeitenden Hubeinrichtungen Expired - Lifetime EP1331199B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10202607 2002-01-24
DE10202607A DE10202607C1 (de) 2002-01-24 2002-01-24 Steuervorrichtung, insbesondere für den Einsatz bei hydraulisch arbeitenden Hubeinrichtungen

Publications (3)

Publication Number Publication Date
EP1331199A2 EP1331199A2 (de) 2003-07-30
EP1331199A3 EP1331199A3 (de) 2004-05-12
EP1331199B1 true EP1331199B1 (de) 2006-09-13

Family

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Application Number Title Priority Date Filing Date
EP02025356A Expired - Lifetime EP1331199B1 (de) 2002-01-24 2002-11-14 Steuervorrichtung, insbesondere für den Einsatz bei hydraulisch arbeitenden Hubeinrichtungen

Country Status (5)

Country Link
US (1) US6786132B2 (es)
EP (1) EP1331199B1 (es)
AT (1) ATE339386T1 (es)
DE (2) DE10202607C1 (es)
ES (1) ES2271174T3 (es)

Cited By (1)

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DE102012107256B4 (de) 2012-05-07 2023-08-31 Buchholz Hydraulik Gmbh Hydraulischer Hubantrieb einer mobilen Arbeitsmaschine

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DE102007062649A1 (de) 2007-12-24 2009-06-25 Hydac Electronic Gmbh Ventilvorrichtung
DE102012010522A1 (de) * 2012-05-25 2013-11-28 Hydac Fluidtechnik Gmbh Ventil für Ventilanordnung
CN103629194B (zh) * 2013-12-10 2015-11-25 沈阳东北电力调节技术有限公司 机械式快动的集成式电液执行器
DE102014202436A1 (de) * 2014-02-11 2015-08-13 Franz Xaver Meiller Fahrzeug- Und Maschinenfabrik - Gmbh & Co Kg Hydraulisches Kippsystem für einen mittels eines Kippventils stetig steuerbaren, in der Senkgeschwindigkeit nicht durch das Kippventil begrenzten Senkbetrieb
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DE102017008359A1 (de) 2017-09-06 2019-03-07 Hydac Fluidtechnik Gmbh Ventil
DE102018104586A1 (de) * 2018-02-28 2019-08-29 Jungheinrich Aktiengesellschaft Flurförderzeug mit mindestens einem hydraulischen Masthubzylinder
CN108612700B (zh) * 2018-05-18 2020-11-24 安徽仕烽油压科技有限公司 插装式翻转控制阀
CN108488130B (zh) * 2018-05-18 2019-12-24 江苏南京白马现代农业高新技术产业园有限公司 一种控制阀装置

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DE29713293U1 (de) * 1997-07-25 1997-10-23 Heilmeier & Weinlein Magnetbetätigtes Ablaßventil
DE10010670C2 (de) * 2000-03-04 2003-11-06 Jungheinrich Ag Hydraulische Hubvorrichtung für batteriebetriebene Flurförderzeuge

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DE102012107256B4 (de) 2012-05-07 2023-08-31 Buchholz Hydraulik Gmbh Hydraulischer Hubantrieb einer mobilen Arbeitsmaschine

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EP1331199A3 (de) 2004-05-12
DE10202607C1 (de) 2003-07-31
ATE339386T1 (de) 2006-10-15
US20030136124A1 (en) 2003-07-24
ES2271174T3 (es) 2007-04-16
US6786132B2 (en) 2004-09-07
DE50208129D1 (de) 2006-10-26

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