EP1754682A1 - Dispositif électrohydraulique - Google Patents

Dispositif électrohydraulique Download PDF

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Publication number
EP1754682A1
EP1754682A1 EP05017521A EP05017521A EP1754682A1 EP 1754682 A1 EP1754682 A1 EP 1754682A1 EP 05017521 A EP05017521 A EP 05017521A EP 05017521 A EP05017521 A EP 05017521A EP 1754682 A1 EP1754682 A1 EP 1754682A1
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EP
European Patent Office
Prior art keywords
pressure compensator
valve
load
pressure
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.)
Granted
Application number
EP05017521A
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German (de)
English (en)
Other versions
EP1754682B1 (fr
Inventor
Martin Dipl.-Ing. Univ. Heusser
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.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Hawe Hydraulik GmbH and Co KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hawe Hydraulik GmbH and Co KG filed Critical Hawe Hydraulik GmbH and Co KG
Priority to EP20050017521 priority Critical patent/EP1754682B1/fr
Priority to DE200550000989 priority patent/DE502005000989D1/de
Publication of EP1754682A1 publication Critical patent/EP1754682A1/fr
Application granted granted Critical
Publication of EP1754682B1 publication Critical patent/EP1754682B1/fr
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Anticipated expiration legal-status Critical

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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
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
    • 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control

Definitions

  • the invention relates to an electro-hydraulic device specified in the preamble of claim 1. Art.
  • a load-holding device is provided as a safety function, and the two-way current regulator also serves as a so-called lowering brake when lowering, which limits the volume flow and thus the retraction speed of the hydraulic consumer.
  • the load holding device is actuated by a magnet so that when adjusting the neutral position of the directional control valve, the load is kept leak-free.
  • lowering the load holding device is switched to non-energized magnet to passage, so that the hydraulic medium flows from the hydraulic consumer through the load holding device, the regulating pressure compensator of the two-way flow regulator and finally the directional control valve to the return.
  • the load-holding device inevitably generates a dynamic pressure even in the flow-through position, which has an undesirable influence on the lowering speed at low when the two-way flow controller is fully open and the hand control valve is in the lowered position Load takes. That is, a small load of the hydraulic load to be lowered at high speed can not be moved at the desired maximum speed. It would have the load-holding device to be formed with an excessively large cross-section, which is expensive and unreasonably claimed a lot of installation space, and yet could not exclude an undesirable residual pressure.
  • the invention has for its object to provide an electro-hydraulic device of the type mentioned, in which the load-holding function is integrated so that it generates no additional undesirable back pressure during lowering.
  • the stacker-tight load-holding function is incorporated directly into the pressure balance and activated by the control circuit in the opening control side of the pressure balance magnetic switching valve, only two pressure-generating components are provided in the flow path from the hydraulic consumer via the pressure balance and the directional control valve to the return that anyway for the required functions are designed with a large cross-section so that the dynamic pressure arising especially when lowering at maximum speed and low load remains so minimal that the desired maximum speed is easily achieved despite low load or only under the load of the hydraulic consumer.
  • the control circuit magnetic switching valve which can be designed physically small and inexpensive due to low control volumes to be controlled, the integration of at least one additional safety function in the electro-hydraulic device without significant additional effort.
  • the magnetic switching valve is always energized when the directional control valve is deflected by hand from the neutral position, so that it then exerts no influence in the control circuit.
  • the magnetic switching valve is expediently used in the electrohydraulic device in order to automatically set the load holding function in the deactivated state of a functional component of the industrial truck and to switch off the regulating function of the pressure compensator. This will cause an unintentional Incorrect operation of the electro-hydraulic device excluded, both for lifting and lowering.
  • the additional safety function is linked to a seat occupancy indicator switch or sensor. If the seat is not occupied by the driver, then the electro-hydraulic device can be operated neither intentionally nor unintentionally, because the load holding function is set and the pressure compensator is rendered inoperative.
  • a circulation pressure compensator is provided between the pressure source and the return, which supplies, so to speak as a load regulator depending on the load, the directional control valve just required volume flow.
  • the directional control valve has a passage for relieving the closing control side of the circulation pressure compensator to the return and this passage is open in the neutral position and in the lowering position of the directional control valve.
  • the passivation of the circulation pressure compensator can be done both via the directional control valve and via the magnetic switching valve, however, when lowering only via the directional control valve.
  • the solenoid valve is designed to be stacker-tight at least at the connection of the control circuit to the control side of the pressure compensator.
  • Stacker leak has the meaning that only a minimal leakage per unit time is allowed, not comparable to the leakage, for example, in a slide valve.
  • the solenoid valve is even formed with a seat valve function at least at the connection of the control circuit to the control side of the pressure compensator, so that the magnetic switching valve in the second non-energized switching position leakproof is tight and any lowering of the hydraulic consumer is blocked.
  • the pressure compensator is formed with three sections, namely the load-holding and non-regulating shut-off section, and a second, together with a third regulating flow section, wherein the third flow section has the maximum flow cross-section with minimal back pressure.
  • the fixed orifice of the two-way flow regulator is defined by the third flow control section of the pressure compensator, which can be designed to be optimally large and therefore produces only minimal back pressure.
  • the diaphragm can be placed as fixed diaphragm in the strand between the pressure balance and the hydraulic consumer and formed with a passage cross-section which generates only minimal back pressure. In this case, branches off from the strand of the control circuit to the control side between the pressure compensator and the fixed orifice, while the control circuit branches off to Zuumbleseite between the fixed orifice and the hydraulic consumer.
  • the two-way flow controller and the magnetic switching valve are expediently combined in a housing block which can be linked to the directional control valve.
  • This housing block can be combined with various manually operable directional control valves as needed and requires little installation space.
  • Fig. 1 illustrates the usual practice in the preparation of an electro-hydraulic device S for a material handling vehicle with a one-sided acted upon by a load hydraulic consumers H, for example a lifting cylinder.
  • a manual control valve which is manually adjustable from the neutral position (holding position) shown in two switching positions (a: lifting, b: lowering) by means of a hand lever 1 is connected to a pressure source P and to a return R.
  • the directional control valve W includes a passage 21, for example, for a so-called non-pressurized circulation in the neutral position and in the sink position.
  • an electrical transducer 2 is provided on the directional control valve W, which reports the deflection of the directional control valve from the neutral position by means of a corresponding signal to a higher-level control, not shown, with the example, a solenoid 10 of an electromagnetically actuated load-holding device EM can be controlled. From the directional control valve W, a lifting, holding and lowering strand 3 leads to the hydraulic consumer H.
  • a two-way flow regulator R is arranged, consisting of a two-section pressure compensator 4 with a diaphragm 5, a control spring 6 and a control circuit from the strand 3 to the control side and a control circuit 8 from the strand 3 to the Zu Kunststoffseite a pressure compensator 4 of the two-way current controller R is formed.
  • the electromagnetic load-holding device EM is arranged between the pressure compensator 4 and the hydraulic consumer H in the strand 3 and formed, for example, as a 2/2-solenoid valve whose solenoid 10 (via a hydraulic pilot control) against the force of a spring 11 a Flow setting.
  • the actuating spring 11 is in non-energized solenoid 10, the load-holding position shown, in which the load of the hydraulic consumer is kept leak-free on a check valve in the seat valve design.
  • the solenoid 10 is energized, for example, by the higher-level control in accordance with the signal of the odometer 2 at least in the lowering position b of the directional control valve W. Since in the flow position of the electromagnetically actuated load-holding device EM, the entire working hydraulic medium must pass, inevitably arises relatively high back pressure, which prevents the achievement of the maximum lowering speed at low load.
  • FIG. 2 The embodiment of the electrohydraulic device according to the invention shown in FIG. 2 has substantially the same functions as the prior art device explained with reference to FIG. 1, so that matching components have the same reference numerals.
  • the pressure compensator 4 of the two-way flow regulator R (for both flow directions) is formed with three sections.
  • the first section 12 is a load-holding section at least in stacker-tight execution in order to realize a load-holding function in the strand 3.
  • the second and third sections 13, 14 are flow control sections, wherein the flow control section 13 includes a variable metering orifice 5 and the maximum flow section flow section 14 cooperates with a fixed orifice 5 'shown in strand 3 between the pressure compensator 4 and the hydraulic consumer H.
  • the two pressure control sections 13, 14 regulate the flow together as a function of the adjustment of the pressure compensator in Aufwinraum Vietnamese under the force of the control spring 6 and the pilot pressure in the control circuit 7 to the control side on the one hand and the pilot pressure in the control circuit 8 to Zuumbleseite on the other.
  • the control circuit 7 branches from strand 3 (in the symbolic dissolved representation in Fig. 2) between the pressure compensator 4 and the fixed orifice 5 'from the strand 3, while the control circuit branches off to the Zuêtseite from the strand 3 between the fixed aperture 5' and the hydraulic consumer H.
  • a 3/2-solenoid valve 15 with a solenoid 17 is included, which is additionally connected to an outlet via a control line 16 to the return R.
  • the solenoid switching valve 15 is, for example, a 3/2-solenoid seat valve 26, the non-energized, as shown, under the force of a spring occupies a second switching position, in which the branched off from the strand 3 control circuit 7 is shut off and the Zuumbleseite the pressure compensator 4 is relieved via the control line 16 to the return.
  • the solenoid switching valve 15 assumes a first switching position, in which the control circuit 7 is continuous and the control line 16 to the return R is locked.
  • the electrical odometer 2 on the directional control valve W is connected to a controller or logic circuit C.
  • the solenoid 17 of the magnetic switching valve 15 is connected via a control line 18, for example, also with the controller C, expediently to achieve an additional safety function via a breaker 19, which is then actuated by a functional component 20, such as a seat occupancy indicator switch or sensor of the industrial truck, and interrupts when the function component is deactivated or the seat is not occupied.
  • control valve W pressure from the pressure source P via the passage 21 of the directional control valve W is reduced.
  • the system is depressurised (non-pressurized circulation).
  • the solenoid 17 is not energized.
  • the Zuumbleseite the pressure compensator 4 is relieved via the control line 16 to the return.
  • the pressure compensator 4 is held by the control spring 16 of the flow position shown.
  • the solenoid switching valve 15 is energized, so that the solenoid 17 sets the first switching position (control circuit 7 continuously, control pressure line 16 blocked).
  • the hydraulic medium flows through the flow section 14 and the fixed panel 5 'to the hydraulic consumer H (lifting).
  • the pressure difference across the fixed orifice 5 ' is tapped, so that the control circuit 7 performs a higher control pressure on the control side than the control pressure tapped off downstream of the fixed orifice 5' in the control circuit 8 on the supply side.
  • the pressure compensator 4 controls the volume flow so that, for example, depending on the deflection of the directional control valve, the hydraulic consumer is moved in the lifting direction at a certain speed, which is kept independent of the load.
  • the pressure compensator 4 operates in its control range.
  • the directional control valve on the hand lever 1 is moved to the neutral position (as shown).
  • the pressure of the pressure source P is reduced via the passage 21.
  • the solenoid 17 is de-energized.
  • the solenoid switching valve 15 goes into the second switching position shown.
  • the control side of the pressure compensator 4 is depressurized to the return R.
  • the pilot pressure in the control circuit 8 switches the pressure balance 4 in its Absperrsetation 12.
  • the load pressure is maintained.
  • the pilot pressure in the control circuit 7 between the strand 3 and the connection of the solenoid valve 15 (here a seat valve 26) is kept free of leaks.
  • the pressure compensator 4 controls with the flow control sections 13, 14, wherein a lowering brake function with limitation of the maximum speed in accordance with the now reversed pressure difference on the fixed aperture 5 'is executed. Since the fixed orifice 5 'belongs to the flow section 14, only slight back pressure is built up, so that the maximum desired speed is achieved even at low load.
  • the breaker 19 interrupts the current application of the switching magnet 17 instantaneously.
  • the pressure compensator 4 is placed on the load holding section 12. The load is held and stops moving.
  • the functional component be a seat occupancy switch or sensor
  • the pressure compensator 4 automatically performs the load holding function with the load holding section 12 so that the hydraulic consumer can neither retract nor can be extended.
  • the solenoid switching valve 15 does not necessarily have to be formed as a seat valve 26. It may be sufficient to use a switching valve (3/2-way valve) in stapler-tight design.
  • Fig. 3 illustrates the concrete, unresolved symbolized representation of the electro-hydraulic device S of Fig. 2, such that the fixed orifice 5 'is contained in the pressure compensator 4, and the control circuit 8 to Zuêtseite between the pressure compensator 4 and the hydraulic consumer H from the strand 3 branches off, while the control circuit 7 branches off to the control side between the pressure compensator 4 and the directional control valve W from the strand 3. Since in FIG. 3 only the fixed diaphragm 5 'can produce a back pressure during lowering, which is predetermined from the outset by the maximum flow cross section, the maximum speed can be achieved without problems even at low load. The outflowing volume flow has only two components to pass to the return R.
  • Fig. 4 illustrates a modified embodiment of the electro-hydraulic device S according to the invention, in which the manual control lever 1 manually adjustable directional control valve W formed in contrast to FIGS. 2 and 3 without Wegmessvorraum and provided a circulation pressure compensator 22 between the pressure source P and the return R. is.
  • the circulation pressure compensator 22 is acted upon from the pressure source via a control circuit 24, and in the opposite direction via a control spring 23 and a control circuit 25 in the lifting switching position of the directional control valve W from a tap 31 via a control line 30 from the fed into the strand 3 consumer pressure is fed.
  • a further control line 29 is guided to the control line 30 via a shuttle valve, which is the load pressure of an optionally further, not shown, the hydraulic consumer reports.
  • the shuttle valve ensures that the respective higher load pressure is brought to the delivery side of the circulation pressure compensator 22. Should no further load pressure control line 29 be provided, the shuttle valve can be omitted.
  • the control circuit 25 is connected to a port 28 of the magnetic switching valve 15 in the control circuit 7, such that in the shown, not energized second switching position of the magnetic switching valve 15 (a 4/2-switching valve in staplerêtr execution) both the control side of the pressure compensator 4 and the Zuumbleseite the circulation pressure compensator 22 are relieved via the control line 16 to the return. This corresponds to the neutral position of the directional control valve W and / or the deactivation of an optionally provided as in Fig. 2 functional component 20 (response of the breaker 19).
  • Fig. 4 is an exploded view of the symbol in which the fixed orifice 5 'of the flow control section 14 is shown in the strand 3 between the pressure compensator 4 and the hydraulic consumer. Accordingly, the control circuits 7, 8 branches off from the strand 3 on both sides of the fixed diaphragm 5 '. In a concrete, not shown embodiment, however, the fixed aperture 5 'is arranged in the pressure compensator 4 itself, analogous to fig. 3. Then, the control circuit 8 branches off from the strand 3 between the pressure compensator 4 and the hydraulic consumer H, while the control circuit 7 branches off from the strand 3 between the pressure compensator 4 and the directional control valve W.
  • the functions are similar as explained with reference to FIGS. 2 and 3, but with the difference that the passage 21 in the neutral position and in the lowering position of the directional control valve relieves the control line 30 to the return, so that the circulation pressure compensator 22 is put into circulation and no supply pressure is pending.
  • the solenoid 17 is not energized in the neutral position of the directional control valve W, but in the lifting position and in the lowering position of the directional control valve W.
  • Fig. 4 illustrates a valve block B with a housing 32 in which, for example, of the electro-hydraulic device S in Fig. 3, the pressure compensator 4 and the solenoid switching valve 15 are housed. 33 denotes a knob for the bias of the control spring 6 of the pressure compensator 4.
  • the housing block 32 can be with various manually operated directional control valves W in conventional block design combine.
  • the connections H and R in the housing block 32 are connected to the hydraulic consumer H and the return R.
  • the directional control valve W with the manual operation 1 can be designed with or without control function.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Transportation (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid-Pressure Circuits (AREA)
EP20050017521 2005-08-11 2005-08-11 Dispositif électrohydraulique Active EP1754682B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20050017521 EP1754682B1 (fr) 2005-08-11 2005-08-11 Dispositif électrohydraulique
DE200550000989 DE502005000989D1 (de) 2005-08-11 2005-08-11 Elektrohydraulische Vorrichtung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20050017521 EP1754682B1 (fr) 2005-08-11 2005-08-11 Dispositif électrohydraulique

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Publication Number Publication Date
EP1754682A1 true EP1754682A1 (fr) 2007-02-21
EP1754682B1 EP1754682B1 (fr) 2007-07-04

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3258116A1 (fr) * 2016-06-15 2017-12-20 HAWE Hydraulik SE Module hydraulique avec soupape de régulation 2-voies contrôlé par pression

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102162268A (zh) * 2011-04-20 2011-08-24 山重建机(济宁)有限公司 履带式液压挖掘机行走控制装置

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5325761A (en) * 1991-03-25 1994-07-05 Friedrich Wilh. Schwing Gmbh Switching arrangement for controlling the speed of hydraulic drives
DE19814147A1 (de) * 1997-03-31 1998-11-26 Toyoda Automatic Loom Works Schwenkzylindersteuerungseinrichtung
US5907991A (en) * 1997-12-22 1999-06-01 Caterpillar Inc. Quick drop valve control
DE19923345A1 (de) * 1999-05-21 2000-11-23 Mannesmann Rexroth Ag Elektrohydraulische Steuereinrichtung
JP2001040713A (ja) * 1999-08-03 2001-02-13 Shin Caterpillar Mitsubishi Ltd クレーン機能付建設機械
US6427721B1 (en) * 1999-07-06 2002-08-06 Sauer-Danfoss (Nordberg) A/S Hydraulic valve arrangement with locking function
EP1369598A1 (fr) 2002-06-03 2003-12-10 HAWE Hydraulik GmbH & Co. KG Dispositif électro-hydraulique de commande de levage pour véhicules de manutention
EP1387089A2 (fr) * 2002-07-30 2004-02-04 Kobelco Construction Machinery Co., Ltd. Circuit pour un vérin hydraulique
DE10303385A1 (de) 2003-01-29 2004-08-05 Buchholz Hydraulik Gmbh Steuereinrichtung für eine Hub- und Senksteuerung
WO2004088144A1 (fr) * 2003-03-31 2004-10-14 Hitachi Construction Machinery Co., Ltd. Dispositif d'entrainement hydraulique pour vehicule motorise fonctionnant

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5325761A (en) * 1991-03-25 1994-07-05 Friedrich Wilh. Schwing Gmbh Switching arrangement for controlling the speed of hydraulic drives
DE19814147A1 (de) * 1997-03-31 1998-11-26 Toyoda Automatic Loom Works Schwenkzylindersteuerungseinrichtung
US5907991A (en) * 1997-12-22 1999-06-01 Caterpillar Inc. Quick drop valve control
DE19923345A1 (de) * 1999-05-21 2000-11-23 Mannesmann Rexroth Ag Elektrohydraulische Steuereinrichtung
US6427721B1 (en) * 1999-07-06 2002-08-06 Sauer-Danfoss (Nordberg) A/S Hydraulic valve arrangement with locking function
JP2001040713A (ja) * 1999-08-03 2001-02-13 Shin Caterpillar Mitsubishi Ltd クレーン機能付建設機械
EP1369598A1 (fr) 2002-06-03 2003-12-10 HAWE Hydraulik GmbH & Co. KG Dispositif électro-hydraulique de commande de levage pour véhicules de manutention
EP1387089A2 (fr) * 2002-07-30 2004-02-04 Kobelco Construction Machinery Co., Ltd. Circuit pour un vérin hydraulique
DE10303385A1 (de) 2003-01-29 2004-08-05 Buchholz Hydraulik Gmbh Steuereinrichtung für eine Hub- und Senksteuerung
WO2004088144A1 (fr) * 2003-03-31 2004-10-14 Hitachi Construction Machinery Co., Ltd. Dispositif d'entrainement hydraulique pour vehicule motorise fonctionnant

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 19 5 June 2001 (2001-06-05) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3258116A1 (fr) * 2016-06-15 2017-12-20 HAWE Hydraulik SE Module hydraulique avec soupape de régulation 2-voies contrôlé par pression

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EP1754682B1 (fr) 2007-07-04

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