EP1407086B1 - Systeme de commande hydraulique - Google Patents

Systeme de commande hydraulique Download PDF

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Publication number
EP1407086B1
EP1407086B1 EP02747163A EP02747163A EP1407086B1 EP 1407086 B1 EP1407086 B1 EP 1407086B1 EP 02747163 A EP02747163 A EP 02747163A EP 02747163 A EP02747163 A EP 02747163A EP 1407086 B1 EP1407086 B1 EP 1407086B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
accumulator
tank
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
EP02747163A
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German (de)
English (en)
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EP1407086A1 (fr
Inventor
Edwin Harnischfeger
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication date
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Publication of EP1407086A1 publication Critical patent/EP1407086A1/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
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • 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
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
    • 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
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • 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
    • 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
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2271—Actuators and supports therefor and protection therefor
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping

Definitions

  • the invention relates to a hydraulic control arrangement according to the preamble of claim 1.
  • Such control arrangements are for example as Stabilization module used in wheel loaders to the at To dampen driving occurring pitching vibrations.
  • a stabilization module known for wheel loader, where a boom over Hydraulic cylinder is supported. While driving are the in the support direction effective cylinder chambers of the hydraulic cylinder connected to a hydraulic accumulator. Between Cylinder chambers and the hydraulic accumulator is a valve assembly arranged with a logic valve in its Closed position the connection between the hydraulic accumulator and blocks the hydraulic cylinders.
  • One in the closing direction effective end face of a valve body of the logic valve can be via an electrically operated directional control valve Relieve, so that the logic valve by the opening direction effective pressure in the hydraulic accumulator and in the Cylinder spaces of the hydraulic cylinder in its open position can be brought.
  • the rod-side annular spaces of Hydraulic cylinders are via another logic valve with the Tank connected.
  • DE 39 09 205 C1 is a hydraulic control arrangement shown when driving a work machine the cylinder chambers of the hydraulic cylinder over a electrically operated directional control valve with a hydraulic accumulator and the rod-side annular spaces of the hydraulic cylinders connected to the tank.
  • a pressure reducing valve arranged over which the pressure in the hydraulic accumulator can be limited to a maximum value.
  • Hydraulic accumulator is prevented via the pressure reducing valve. This pressure reducing valve is in one of the hydraulic accumulator leading filling line arranged to the other Consumers are connected.
  • the invention is based on the object a hydraulic control arrangement for damping of To create driving vibrations of mobile tools by the damage to a hydraulic accumulator with minimal Device-technical effort can be prevented.
  • a valve with pressure limiting function arranged in the one Check valve is integrated.
  • the valve When exceeding one Limit pressure, the valve is in its pressure limiting position brought so that the pressure in the hydraulic accumulator up a maximum pressure is limited.
  • the connection of one The cylinder chambers to the hydraulic accumulator via the in the valve integrated check valve, this being Connected connection in the pressure limiting function is.
  • the integrated check valve makes it possible over the valve in its pressure limiting function to relieve the hydraulic accumulator to the tank, so that when, for example, caused by other consumers Pressure peaks get into the hydraulic accumulator, this be dismantled as soon as possible.
  • the operational safety The control arrangement according to the invention is thus opposite the conventional solutions significantly improved.
  • One Another significant advantage of the invention Solution is that due to the integration of the Check valve in the valve of the device technical Effort with superior function less than Prior art is.
  • the valve enabling the pressure limiting function is carried out with one or two working connections, with the bottom of the hydraulic cylinder or with the Piston rod receiving space of the hydraulic cylinder connected are, wherein the check valve in a valve body, preferably added to a valve spool of the valve is.
  • Valve body in the pressure limiting direction of a spring and the pressure in the memory and in the opposite direction of another spring and - depending on the position of the valve body - acted upon by the tank pressure or the accumulator pressure.
  • the acted upon with pressure medium end faces of the valve body formed with different effective areas. This is in an end portion of the valve body a Volumetric flask guided, with one from the valve body projecting end portion on a housing of the valve is supported.
  • a connection between the memory port and a pressure chamber turned on which is penetrated by the from the volumetric flask End face of the valve body is limited, so this End face is acted upon by the accumulator pressure.
  • the manufacturing effort can be further reduce this axial blind hole in a or multipart insert is formed in the End portion of the valve body is used.
  • Valve is a preferably electromagnetic operable directional control valve assigned via the as Control surfaces effective end faces of the valve body acted upon by the accumulator pressure or the tank pressure are.
  • the control arrangement according to the invention with a control valve are carried out over the rod side Space of the hydraulic cylinder connected to the tank can be.
  • FIG 1 is a simplified circuit diagram of a Control arrangement for controlling a boom a mobile implement, such as a wheel loader, supporting hydraulic cylinder, below Lifting cylinder 2 called, shown. This one is about one dot-dash line indicated Lader Herbertblock 4 with a Hydraulic pump 6 or a tank T connectable.
  • the illustrated control arrangement also has one dash-dotted lines indicated damping valve assembly 8, about the occurring during the ride of the wheel loader Vibrations, for example, pitching vibrations attenuated become.
  • This damping valve assembly 8 is such designed so that during the state of the lift cylinder 2 is connected to a hydraulic accumulator 10, so that the lifting cylinder 2 in the support direction of the pressure in Hydraulic accumulator 10 is acted upon.
  • the charger control block 4 has a pressure port P to the the hydraulic pump 6 is connected.
  • Two work connections A, B of the loader control block 4 are on the Damping valve assembly 8 with a cylinder chamber 12 and a rod-side annular space 14 of the hydraulic cylinder. 2 connectable.
  • the tank T is connected to a tank connection S.
  • the charger control block 4 has a 4/3-way valve executed electrically actuated control valve 16, the in its spring-biased basic position the work connections A, B with respect to the pressure port P and the Tank connection S shut off.
  • a first switching position a is to extend of the hydraulic cylinder 2, the pressure port P to the working port B and the work port A with the Tank connection S connected, so that pressure medium in the Cylinder chamber 12 and the annular space 14 to the tank T promoted becomes.
  • b is for retraction of the hydraulic cylinder 2 of the working port A with the Pressure port P and the tank port S with the working port B connected.
  • the loader control block 4 has a pressure relief valve 18, over which when a maximum pressure is exceeded, for example, 330 bar, the working port B with the tank connection S is connectable.
  • the damping valve assembly 8 has two with the working ports A, B connected input terminals R, U, a tank port T and a storage port P '.
  • the both input ports R, U are via channels 20, 22nd connected to the input terminals of a control valve 24.
  • the output terminals of the control valve 24 are on connected to the tank port T and a storage port P '.
  • the valve spool of the control valve 24 is by two springs 26, 28 in its illustrated basic position biased, in which the connection between the Work port R and the tank port T is shut off and the connection from the working port U to the storage port P 'in the direction of the hydraulic accumulator 10 is opened.
  • the pressure medium flow in the opposite direction, i. from the hydraulic accumulator 10 towards the consumer connection U and to the bottom of the cylinder is through a check valve 30 closed. This is in the control valve 24th integrated.
  • the damping valve assembly 8 further has a Directional control valve 32, in the illustrated embodiment is electromagnetically actuated.
  • a spring-loaded Basic position connects the directional control valve 32 a to the tank connection T connected control channel 34 with a control chamber of the control valve 24, by the in Figure 1 left end face of the valve spool of the control valve 24 is limited, so that in the illustrated Switching position of the directional valve 32, the tank pressure in the direction the spring 26 acts on the valve spool.
  • about another control channel 36 is the pressure at the storage port P 'tapped and in a reverse direction effective control space of the control valve 24 is performed, so that the resulting pressure in the direction of the further spring 28th (on the right in FIG. 1) acts.
  • the damping valve assembly 8 still has a pressure relief valve 38, via which the pressure in Hydraulic accumulator 10 even with switched path valve 32nd is limited to a maximum value.
  • This pressure increases due to the loading of the blade when working on, so the valve spool the control valve 24 from its spring-biased home position by the control pressure prevailing in the control channel 36, which corresponds to the pressure in the hydraulic accumulator in one Control position shifted with pressure reduction function, in the guided to the hydraulic accumulator 10 pressure on a Limit, for example, 120 bar is reduced.
  • This pressure reducing function will be the connection of Input terminal U to the memory port P 'controlled.
  • the effective in the direction of the spring 26 control pressure in Channel 32 is equal to the tank pressure, as the directional control valve 32 is still in its illustrated home position.
  • a filling of the hydraulic accumulator 10 over in the Pressure reduction function is set pressure out not possible, since the control valve 24 then in the is shown locked position.
  • the check valve 30 prevents a Releasing the pressure in the hydraulic accumulator 10.
  • control valve 16 is in its middle Neutral position brought in the connections A, B and P, S are locked against each other. Furthermore, that will Directional control valve 32 is switched so that both control surfaces the control valve 24 is acted upon by the accumulator pressure are.
  • valve spool then in the illustration of Figure 1 after shifted to the right so that the ports U and P 'as well R and T 'are turned on, i. the annulus 14 is then connected to the tank while the bottom side Cylinder chamber 12 is connected to the hydraulic accumulator 10.
  • the lifting cylinder 2 is by the pressure in the memory 10th held in its support position. Since the hydraulic accumulator 10 When switching on the system always pressurized is, a lowering of the boom is reliably prevented.
  • the pressure limiting function of the control valve 24 is in driving condition by the pressure relief valve 38th accepted.
  • FIG. 2 shows a longitudinal section through an embodiment a control valve 24 of the damping valve assembly 8.
  • the control valve 24 has a housing 40, the is penetrated by a valve bore 42.
  • the frontal End portions of the valve bore 42 are through Closure caps 44 closed.
  • In the valve bore 42 is the above-mentioned valve spool 46th guided, via the springs 26, 28 in its basic position is biased.
  • In the illustrated embodiment are the two springs 26, 28 in a common Spring chamber 47 was added.
  • the spring 26 acts as a compression spring, the valve spool 46 to the right ( Figure 2) acted upon while the spring 28, the valve spool 46 applied in the opposite direction.
  • annular spaces 52, 54, 56, and 58th formed, wherein the annular space 52 with the tank connection T, the annulus 54 with the rod-side port R, the annular space 56 with the bottom-side port U and the Annulus 58 are connected to the storage port P '.
  • the valve spool 46 has in the region of the annular space 52nd an annular groove 60 through which a control edge 62 is formed is. In the region of the annular space 56 is another Ring groove 64 is provided, via which a control edge 66 is trained.
  • valve spool 46 In the right in Figure 2 end portion of the valve spool 46 is an insert 68 with a volumetric flask 70 and the check valve 30 is inserted. One from the Valve slide 46 axially projecting end portion of the Measuring piston 70 is located on the right cap 44th at.
  • valve spool 46 has a right in the in Figure 3 End face opening bore 72, which in a channel 74 passes. This ends in a transverse bore, the bottom the annular groove 64 opens.
  • the bore 72 is radially stepped back to the channel 74, wherein the adjacent to the channel 74 end face as a valve seat 78 for a closing body 80 of the check valve 30 is formed.
  • the to the valve seat 78 adjoining room is over shell holes 82 of the Valve spool 46 with the annular space 58 connectable, so that pressure medium lifted off from the valve seat 78 Closing body 80 via the transverse bores 76, the channel 74th and the shell holes 82 to the storage port P ' can flow.
  • the insert 68 is in the illustrated embodiment executed in several parts and into the bore 72nd screwed.
  • the Insert 68 has a center piece 84 and an end piece 86, this with a shoulder on the right in Figure 3 End face of the valve spool 46 rests.
  • centerpiece 84 and tail 86 are from a Axialsacklochbohrung 88 passes, guided in the volumetric flask 70 is.
  • the middle piece 84 is further from a connection bore 90 interspersed, on the one hand in the Axialsacklochbohrung 88 and on the other hand in breakthroughs 92 opens.
  • a connection bore 90 interspersed, on the one hand in the Axialsacklochbohrung 88 and on the other hand in breakthroughs 92 opens.
  • the openings 92 in the valve spool 46th and the connection hole 90 is the axial blind hole 88 connected to the annular space 58.
  • a housing body 98 of the check valve 30 supported, in which the closing body 80th during the take off and in which the the Closing body 80 against the valve seat 78 biasing Closing spring 100 is mounted.
  • the adjacent to the tail 86 control chamber 102 is via a dashed line indicated tank channel 104 with the Tank connection connected so that in the illustrated Position of the control chamber 102 applied to tank pressure is.
  • the directional control valve 32 shown in Figure 1 and the Pressure relief valve 38 may also be in the housing 40 of the control valve 24 may be included.
  • the spring chamber 47 can be integrated in the housing 40 via the Directional valve 32 either with the tank pressure or be charged with the storage pressure.
  • valve spool 46 In a further axial displacement the valve spool 46 is the latter compound completely shut off and the radial leg 96 of the Flasks 70 are through the frontal peripheral edge the Axialsacklochbohrung 88 controlled so that the Control chamber 102 via the radial leg 96, the inner bore 94, the adjoining part of the Axialsacklochbohrung 88, the connection holes 90 and the openings 92 are connected to the storage port P ' is - the pressure in the hydraulic accumulator 10 can then on this Pressure medium path to the tank to be dismantled - the control valve is in its pressure limiting function.
  • the channel guide in the area the check valve 30 and the measuring piston 70 also on other than shown in Figures 2 and 3 respectively.
  • Slanted holes are used instead of the radial breakthroughs Slanted holes.
  • the feathers 28, 26 can in separate spring chambers (spring 26 in Spring chamber 47, spring 28 in the control chamber 102) was added be.
  • FIG. 3 shows a variant in which the Control valve 24 provided only with three connections is, depending on the position of the control valve 24, the bottom-side cylinder chamber 12 of the lifting cylinder 2 - as in the above-described embodiment - either with the hydraulic accumulator 10 or with the tank connectable or lockable.
  • the connection of the rod side Annulus 14 with the tank T via a Control valve 110 which in the illustrated in Figure 4 Embodiment is executed with Nachsaugfunktion.
  • the connection from the channel 20 to a tank channel 112 through the Control valve 110 shut off, while at a shortage a pressure medium flow from the tank to the channel 20 and thus to the annular space 14 via the integrated check valve the control valve 110 is enabled.
  • Control of the control valve 110 is the. Channel 20 directly connected to the tank channel 112, so that the pressure medium can flow from the annular space 14 to the tank.
  • the directional control valve 32 connects in its basic position the control channel 34 connected to the tank connection T. with the on the left end face of the valve spool 46th adjacent control room while on the opposite direction effective control surface of the valve spool via the control channel 36 subjected to the pressure in the hydraulic accumulator 10 is.
  • the directional control valve 32 When switching the directional control valve 32 are both control surfaces subjected to the pressure in the hydraulic accumulator 10, so that the valve spool is to the right in its open position is brought in which the ports U and P ' are directly connected. Otherwise corresponds the embodiment shown in Figure 4 the above-described embodiment, so that more Explanations are dispensable.
  • a hydraulic control arrangement for Damping of driving vibrations of a mobile implement, with a lifting tool supporting a lifting cylinder, its cylinder chambers via a control valve arrangement connectable with a pressure medium source or a tank are.
  • the hydraulic control assembly has a damping valve assembly with a control valve in the one Check valve is integrated, over which a bottom-side Space of the lifting cylinder with a hydraulic accumulator connectable is.
  • the Memory In the pressure limiting function, the Memory to be connected to a tank, so that the Memory pressure is limited to a maximum value.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Mechanical Engineering (AREA)
  • Transportation (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)

Claims (10)

  1. Système de commande hydraulique pour l'amortissement des oscillations en marche d'un engin de travail mobile, avec un vérin hydraulique (2) supportant un outil de travail, dont les chambres de vérin (12, 14) sont reliées, par un agencement de soupape de commande (4), à une source de moyen de pression (6, 10) ou un réservoir (T), et avec un agencement de soupape d'amortissement (8) pour relier une chambre de vérin (12) à un accumulateur hydraulique (10) et une autre chambre de vérin (14) au réservoir (T), dans lequel l'agencement de soupape d'amortissement (8) comporte une soupape (24) pour agir sur la pression dans l'accumulateur hydraulique (10) et un clapet antiretour (30) pour empêcher un reflux du moyen de pression de l'accumulateur hydraulique (10) vers la chambre de vérin (12), caractérisé en ce que la soupape (24) possède une fonction de limitation de pression au moyen de laquelle, en cas de dépassement d'une pression limite, une liaison entre l'accumulateur hydraulique (10) et le réservoir (T) est commandée, et en ce que le clapet antiretour (30) est disposé dans un canal (74, 82) de la soupape (24), au moyen duquel le raccordement (U) à une chambre de vérin peut être relié à un raccordement (P') de l'accumulateur relié à l'accumulateur hydraulique (10), de sorte que le canal (74, 82) est, en cas d'une commande de la soupape (24), commandé dans la direction de la fonction de limitation de pression.
  2. Système de commande selon la revendication 1, dans lequel la soupape (24) comporte un raccordement au réservoir, un raccordement relié à la chambre de vérin (12) du vérin de levage (2) du côté du fond, un raccordement à l'accumulateur ou les raccordements précités et un autre raccordement de travail relié à la chambre de vérin (14) du vérin hydraulique (2) du côté tige de piston, et le canal (74, 82) est intégré avec le clapet antiretour (30) dans le corps de soupape (46).
  3. Système de commande selon la revendication 2, dans lequel le corps de soupape (46) est sollicité, dans la direction de la limitation de pression, par un ressort (28) et la pression à l'intérieur de l'accumulateur et, dans la direction opposée, par un autre ressort (26) ainsi que la pression du réservoir ou la pression de l'accumulateur.
  4. Système de commande selon la revendication 3, dans lequel, dans une face frontale du corps de soupape (46), agissant dans la direction de la limitation de pression, est guidé un piston de mesure (70) qui s'appuie par une section d'extrémité sur un siège (40) de la soupape (24) et au dessus duquel est commandée une liaison entre le raccordement de l'accumulateur et une chambre de commande (102) adjacente à la face frontale.
  5. Système de commande selon la revendication 4, dans lequel le piston de mesure (70) est guidé dans un perçage axial à trou borgne (88) du corps de soupape 46), qui est relié par des perçages (90, 92) à un espace annulaire (58) associé au raccordement de l'accumulateur.
  6. Système de commande selon la revendication 5, dans lequel le canal (74, 82) débouche, dans la distance axiale par rapport aux perçages (90, 92), dans l'espace annulaire (58) et la zone où il débouche est commandée, pendant le déplacement du corps de soupape (46), dans la direction de la limitation de pression.
  7. Système de commande selon la revendication 5 ou 6, dans lequel le corps de soupape (46) comporte une pièce d'insert (68) en une ou plusieurs parties, dans laquelle le perçage axial à trou borgne (88) et au moins une section des perçages (90, 92) sont formés.
  8. Système de commande selon l'une quelconque des revendications 3 à 7, dans lequel un distributeur (32) à actionnement électromagnétique est associé à la soupape (24), au moyen duquel, dans une position de commutation, des faces de commande du corps de soupape sont sollicitées par la pression de l'accumulateur, tandis que, dans une position de base du distributeur (32) précontraint par ressort, une face de commande de la soupape (24) agissant en position d'ouverture est sollicitée par la pression du réservoir.
  9. Système de commande selon l'une quelconque des revendications précédentes, dans lequel il est prévu, entre l'accumulateur hydraulique (10) et la soupape (24), un limiteur de pression (38) au moyen duquel la pression est limitée dans l'accumulateur hydraulique (10).
  10. Système de commande selon l'une quelconque des revendications précédentes, comportant une soupape de réglage (110) par laquelle l'autre chambre de vérin (14) est reliée au réservoir.
EP02747163A 2001-07-13 2002-05-23 Systeme de commande hydraulique Expired - Lifetime EP1407086B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10133616 2001-07-13
DE10133616A DE10133616A1 (de) 2001-07-13 2001-07-13 Hydraulische Steueranordnung
PCT/DE2002/001871 WO2003006753A1 (fr) 2001-07-13 2002-05-23 Systeme de commande hydraulique

Publications (2)

Publication Number Publication Date
EP1407086A1 EP1407086A1 (fr) 2004-04-14
EP1407086B1 true EP1407086B1 (fr) 2005-10-26

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Application Number Title Priority Date Filing Date
EP02747163A Expired - Lifetime EP1407086B1 (fr) 2001-07-13 2002-05-23 Systeme de commande hydraulique

Country Status (7)

Country Link
US (1) US6938413B2 (fr)
EP (1) EP1407086B1 (fr)
JP (1) JP4204463B2 (fr)
KR (1) KR100897027B1 (fr)
AT (1) ATE307929T1 (fr)
DE (2) DE10133616A1 (fr)
WO (1) WO2003006753A1 (fr)

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DE102012208307A1 (de) 2012-05-18 2013-11-21 Robert Bosch Gmbh Dämpfungsvorrichtung

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DE102004012362A1 (de) * 2004-03-13 2005-09-22 Deere & Company, Moline Hydraulische Anordnung
US7165395B2 (en) * 2005-02-11 2007-01-23 Deere & Company Semi-active ride control for a mobile machine
DE102005033154A1 (de) * 2005-07-13 2007-01-18 Deere & Company, Moline Hydraulische Anordnung
DE102005038333A1 (de) 2005-08-11 2007-02-15 Deere & Company, Moline Hydraulische Anordnung
FR2923352B1 (fr) * 2007-11-12 2010-01-15 Signalisation Moderne Autoroutiere Sma Machine de fauchage/debroussaillage/elagage munie d'un moyen d'amortissement de chocs
US7793740B2 (en) 2008-10-31 2010-09-14 Caterpillar Inc Ride control for motor graders
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ATE307929T1 (de) 2005-11-15
DE50204694D1 (de) 2005-12-01
KR100897027B1 (ko) 2009-05-14
KR20040022221A (ko) 2004-03-11
WO2003006753A1 (fr) 2003-01-23
US6938413B2 (en) 2005-09-06
DE10133616A1 (de) 2003-01-30
JP2004534188A (ja) 2004-11-11
US20040216455A1 (en) 2004-11-04
JP4204463B2 (ja) 2009-01-07
EP1407086A1 (fr) 2004-04-14

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