EP2344700B1 - Dispositif de compensation des pressions différentielles hydrauliques - Google Patents

Dispositif de compensation des pressions différentielles hydrauliques Download PDF

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Publication number
EP2344700B1
EP2344700B1 EP09737365A EP09737365A EP2344700B1 EP 2344700 B1 EP2344700 B1 EP 2344700B1 EP 09737365 A EP09737365 A EP 09737365A EP 09737365 A EP09737365 A EP 09737365A EP 2344700 B1 EP2344700 B1 EP 2344700B1
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EP
European Patent Office
Prior art keywords
pressure
valve
piston
hydraulic
control
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Not-in-force
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EP09737365A
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German (de)
English (en)
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EP2344700A1 (fr
Inventor
Rüdiger HONSBEIN
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Hydac System GmbH
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Hydac System GmbH
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Publication of EP2344700A1 publication Critical patent/EP2344700A1/fr
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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
    • 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
    • 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
    • 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
    • F15B2211/625—Accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8616—Control during or prevention of abnormal conditions the abnormal condition being noise or vibration

Definitions

  • the invention relates to a device for compensating hydraulic effective pressures in a hydraulic accumulator and in a Hydroaktuator a hydraulic system with a directional control valve for blocking a fluid connection between the Hydroaktuator and the hydraulic accumulator, the directional control valve in its release state establishes a direct fluid connection between the hydraulic actuator and the hydraulic accumulator and this Disconnects fluid communication in its blocking state, and a control valve means having a leading from the directional control valve to the hydraulic accumulator storage line leading from a piston side of the lifting cylinder to the directional valve first line branch and leading from a rod side of the lifting cylinder to the directional control valve second line branch, in response to the transfer of the Directional valve can be activated in the blocking state, which makes a pressure equalization when exceeding a predetermined difference of the effective pressures and which contains a drain valve, the by a e, the predetermined size exceeding difference of the effective pressures can be blocked in its release state in which a pressure difference reducing discharge path to the tank side of the hydraulic system is
  • EP 1 571 267 A2 known.
  • the known suspension device is characterized in that the storage device is brought to approximately the same pressure before activating the suspension, which is present as a support pressure in the drive part, and that for the pertinent adjustment of the accumulator pressure, a differential pressure switch is used.
  • the pressure difference switch As control pressures are applied to the pressure difference switch on the one hand, the accumulator pressure of the memory device, which is tapped at a corresponding node, and on the other hand, the pressure in the connecting line between the drive part and the directional control valve, more precisely in the first leg.
  • Two further inputs of the differential pressure switch open respectively to the control input side of a charging valve and a discharge valve.
  • the accumulator pressure is increased via the charging valve or lowered via the drain valve.
  • the hydraulic accumulator is loaded as part of the storage device directly from the hydraulic system of the working machine, here a wheel telehandler.
  • the risk of uncontrolled movement when transferring the system from the state of the locked suspension is avoided in the state with released suspension because the respective effective pressures of the hydraulic accumulator and the Hydroaktuators are adapted to each other.
  • the object of the invention is to realize a compensation of hydraulic working pressures with a smaller number and a simpler, less susceptible to malfunctioning design of components.
  • a device according to the invention for compensating hydraulic effective pressures in a hydraulic accumulator and in a hydraulic actuator having at least one lifting cylinder of a hydraulic system is characterized in that in order to bypass the directional valve in the blocking state from the first and second line branch respectively a fluid path is guided to the storage line, and that in the respective fluid path directed to the piston or rod side check valve arranged such that from the piston or rod side of the lifting cylinder forth each of the higher differential pressure across the respective fluid path by opening the respective check valve at a pressure in the hydraulic accumulator excess pressure differential at the piston or Bar side is releasable, can be guided over the storage line to the hydraulic accumulator.
  • control valve device ensures that the equalization of the effective pressures not only by charging the hydraulic accumulator, but a charging of the hydraulic accumulator can be done only up to a pressure level at which the prescribed pressure difference is not exceeded, because upon reaching this pressure difference of the pressure compensation over the Discharge valve to the tank side of the system out.
  • Hydroaktuator at least one lifting cylinder of a working machine, the lifting force generating piston side and the rod side are connected to a control block of the machine, the piston side of the lifting cylinder via the directional control valve with the hydraulic accumulator is connected and the control valve means a connection to the hydraulic accumulator and fluid paths to the piston side and the rod side of the lift cylinder, both of which fluid paths contain check valves that release the fluid path only to the higher effective pressure side leading the lift cylinder.
  • the arrangement can be made such that a discharge valve is provided in the form of a pressure balance, which releases in the release state leading to the tank side discharge path from the connection with the hydraulic accumulator ago and released from the respective, leading to the lifting cylinder fluid path.
  • the arrangement may be such that the discharge process from the reservoir to the tank side only occurs when the pressure difference is slightly greater than zero. It can be effective on the pressure compensator a the effect of the closing pressure amplifying bias.
  • the pressure compensator on a spool which is loaded for its displacement in the locking position on a piston surface both with the closing pressure from the hydraulic circuit and is loaded with the force of a biasing spring.
  • the Fig. 1 shows a mobile machine in the form of a wheel loader 1, with the blade 3, a lifting cylinder 5 is coupled.
  • the lifting force for the blade 3 generating piston side 7 of the lifting cylinder 5 on the in Fig. 1 not shown hydraulic components with a in Fig. 1 only symbolically indicated hydraulic accumulator 9 in conjunction.
  • Fig. 2 to 5 show in symbol representation, the circuit of the hydraulic system in each case different operating conditions.
  • Fig. 2 shows the condition with released suspension.
  • a control block 13 of the working machine (wheel loader 1) with a pressure supply device, which is not shown, is connected to the controlled supply of the lifting cylinder 5 with the piston side 7 and the rod side 15.
  • a valve assembly 11 forming the main part of the hydraulic system has inputs 17 and 19 to which the piston side 7 and the rod side 15 of the lifting cylinder 5 are connected. At outputs 21 and 23 of the valve assembly 11 of the hydraulic accumulator 9 and the tank 25 of the hydraulic system are connected.
  • Fig. 2 the state of the released suspension is shown.
  • the piston side 7 is connected at the port 17 directly to the hydraulic accumulator 9 at the output 21 and the rod side 15 of the lifting cylinder 5 via the input 19 directly to the tank 25 at the output 23 are connected.
  • the other hydraulic components are not involved in the operation, ie that the system causes a conventional suspension / damping of the activity of the lifting cylinder 5.
  • suspension is unfavorable or harmful in certain work situations.
  • a blade 3 of a loader 1 When a blade 3 of a loader 1 is actuated, for example, a compression or rebounding with regard to the accuracy of the position adjustment of the blade 3 has an unfavorable effect.
  • the transfer of the system in the state of the locked suspension happens in such a way that by supplying a hydraulic control pressure via a control line 50, the directional control valve 27 is brought against the bias voltage 29 in the blocking state, which will be explained in more detail below.
  • the Fig. 3 to 5 illustrate three different operating modes with each suspension suspension.
  • This control connection 35 is referred to here as a second control connection.
  • first check valve 41 is opened so that about a storage line 43 of the memory 9 is charged at the output 21 to the pressure of the piston side 7.
  • the second check valve 45 is closed in the same direction as the first-mentioned check valve 41 between the storage line 43 and input 19.
  • This arrangement of the check valves 41 and 45 causes from the inputs 17 and 19 forth each of the higher effective pressure via a respective fluid path, which is formed by opening one or the other check valve 41, 45, in the system takes effect.
  • another check valve 46 is connected in the connecting line to the memory 9 between the two connection points of the first and second check valve 41 and 45, which is directed to the memory 9 in its pertinent closed position.
  • Another control port 47 of the drain valve 37 which is referred to here as the first control port, via a control valve 49, if this in his in Fig. 3 shown opening state is connected to the storage line 43, which in turn, according to one or the other fluid path, that is, depending on which of the check valves 41 or 45 is opened, is connected to the input 17 or the input 19.
  • the prevailing over the open control valve 49 at the first control port 47 pressure also serves as a hydraulic control pressure, the directional control valve 27, by its spring tension 29 in the opening state is biased, hydraulically in the in Fig. 3 shown closed state and thus brings the entire system in the state of the locked suspension.
  • the previously-mentioned released suspension state is the control valve 49 in its closed state, which is caused by its actuating magnet 51 is energized, so that the valve 49 is closed against its opening spring 52.
  • the first control connection 47 of the discharge valve 37 and the control line 50 of the directional valve 27 are depressurized by connection to the tank side 25.
  • the bias voltage 29 therefore keeps the directional control valve 27 in its open state. If the energization of the actuating magnet 51 is interrupted and the control valve 49 is opened, then via the control line 50, the directional control valve 27 against its bias 29 hydraulically controlled in the locked state and the system goes into the state of the locked suspension, as in Fig. 3 to 5 is shown.
  • the hydraulic accumulator 9 prevail at the first control port 47 and the second control port 35 of the discharge valve 37 each have the same pressures, namely via the control line 33 from the input 17 ago and via the open first check valve 41 and the open control valve 49 also from the input 17 ago.
  • a pressure compensator is provided, which is in this steady-state pressure at the control terminals 47 and 35 in the closed state. In this closed state, the discharge valve 47 does not form a discharge path from the inlet connection 53 to an outlet connection 55 which leads via a discharge line 57 via the outlet 23 to the tank 25.
  • the Fig. 4 shows in contrast a state in which, also with locked suspension, the differential pressure in the hydraulic accumulator 9 is higher than the operational condition on the piston side 7 of the lifting cylinder 5 and thus via the input 17 in the valve assembly 11 effective system pressure.
  • the storage line 43 is shown in the Fig. Upper part with a thick solid line and in its lower part of the pipe with a thick dashed line. According to the prevailing in the hydraulic accumulator 9 higher effective pressure than in the lifting cylinder 5, the first check valve 41 is closed.
  • the higher effective pressure of the hydraulic accumulator 9 is thus applied to the first control connection 47 of the discharge valve 37 via the non-energized control valve 49 which is opened by the spring tension 52, while the second control connection 35 leads via the line branch 31 to the lower differential pressure of the input 17.
  • the discharge valve 37 has a pressure compensator, which in Fig. 7 in symbol representation and in Fig. 6 is shown in the form of a functional sketch.
  • Fig. 8 shows a longitudinal section of a practical embodiment. As can be seen, it is a slide valve with the valve housing 63 axially movable slide piston 65, shown in the closed position, which is effected by a force acting on the second control port 35 hydraulic closing pressure, reinforced by a mechanical biasing force, the Fig. 6 and 7 designated 67.
  • the discharge valve 37 opens by an opening hydraulic pressure acting on the first control port 47, provided that the opening pressure at the spool 65 causes a higher opening force than the closing pressure prevailing at the control port 35, amplified by the biasing force 67.
  • condition is that the discharge valve 37 opens to form a discharge path from the inlet port 53 to the outlet port 55 and thus to the tank 25, that applies to the forces acting on the spool 65 forces, the closing force resulting from the pressure at the second control terminal 35, plus the mechanical bias 67th results, is lower than the opening force, generated by the hydraulic pressure at the first control terminal 47th So: F Vorspa , + F print ⁇ 35 ⁇ F print ⁇ 47
  • a pressure level of about 8 bar is present as the opening pressure difference predetermined by the piston geometry and the prestressing force 67.
  • the Fig. 8 shows an embodiment in which engage on a two-part spool 65 for generating the biasing force 67, two coil springs 69 and 71 which bias the piston 65 in the figure to the right in the illustrated closed position, in which the input terminal 53, located in the in Fig. Right side axial end of the valve body 53 is located opposite the output port 55 is locked.
  • the hydraulic pressure of the second control port 35 acts on the left side of the piston 65 in FIG ,
  • the Fig. 5 refers to a further state in which at the input 19 of the valve assembly 11, the higher effective pressure prevails, compared with the Pressure at the input 17 or the pressure in the hydraulic accumulator 9.
  • Such an operating condition arises when running a device on an obstacle when operating a work machine with locked suspension. This may for example be the case when a mobile device, such as a wheel loader 1, runs with its blade 3 on an elevation forming an obstacle, whereby the standing on the blade 3 weight of the wheel loader 1, the piston of the respective lifting cylinder 5 in the rod side 15th shifts, creating an overpressure on the rod side 15.
  • this overpressure is effective, as well as via the open control valve 49 at the first control port 47 of the drain valve 37, so that in the fulfillment of the opening condition, ie a higher pressure at the port 53 relative to the Control terminal 35 which is connected via the first line branch 31 to the input 17, the discharge valve 37 opens, which in turn the discharge path to the tank 25 is opened, whereby the pressure relief of the storage line 43 is carried out.
  • the higher pressure in the control port 47 ensures that the valve 37 is not in the locked position.
  • the actual pressure compensator is formed by the coil spring 69 and by the effective pressure surfaces of the axially displaceable spool 65.
  • the locking piston is designed as a control slide is in turn formed by the coil spring 71 and the effective piston surface 81 of the said piston piston part.
  • the one with 65 in Fig. 6 designated piston can, as in Fig. 6 imaged to be made in several parts to form such a check valve, that is, the multi-part design prevents when the port 55, a higher pressure than the pressure is formed by the biasing forces of the coil springs 69 and 71 plus the effective pressure force through the Pressure at the second control port 35, it to open the valve seat 55 and so far to an unwanted backflow the fluid enters the system.
  • the indicated spool assembly can also be integrally formed (not shown).
  • the construction of the drain valve 37 is not mandatory. Any valve construction whose function corresponds to the above-mentioned opening and closing conditions can be used.
  • the in Fig. 8 shown construction of the two-part slide piston 65 is not mandatory, in which the piston part located on the right in this figure at the input port 53 forms a check valve, which is loaded by the designated spring 69 with low closing force.
  • the designated 71 closing spring forms the main part of in Fig. 6 and 7 with 67 designated bias, which increases the closing force of the valve.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Vehicle Body Suspensions (AREA)

Claims (11)

  1. Dispositif de compensation de pressions hydrauliques effectives dans un accumulateur (9) hydraulique et dans un actionneur hydraulique, comportant au moins un vérin (5) de levage, d'un système hydraulique, comprenant
    - un distributeur (27) pour fermer une liaison pour du fluide entre l'actionneur (5) hydraulique et l'accumulateur (9) hydraulique, le distributeur (27) ménageant dans.son état libéré une liaison directe pour du fluide entre l'actionneur (5) hydraulique et l'accumulateur (9) hydraulique et interrompant la liaison pour du fluide dans son état fermé, et
    - un dispositif (11) de vanne de commande, qui a un conduit (34) accumulateur menant du distributeur (27) à l'accumulateur (9) hydraulique, une première branche (31) de conduit menant d'un côté (7) du piston du vérin (5) hydraulique au distributeur (27) et une deuxième branche (39) de conduit menant d'un côté (15) de tige du vérin (5) de levage au distributeur (27), dispositif (11), qui peut être activé en fonction du passage du distributeur (27) à l'état fermé, qui, si une différence déterminée à l'avance des pressions effectives est dépassée, effectue une compensation de pression et qui comporte une vanne (37) d'évacuation, qui peut être fermée dans son état libéré par une différence des pressions effectives dépassant la valeur prescrite, état dans lequel un trajet (57) d'évacuation, diminuant la différence de pression, est formé vers le côté (25) de cuve du système hydraulique,
    - caractérisé en ce que, pour le contournement du distributeur (27) à l'état fermé de la première (31) et de la deuxième (39) branches de conduit, un trajet pour du fluide mène respectivement vers le conduit (43) de l'accumulateur ; et
    - en ce que, dans le trajet respectif pour du fluide, un clapet antiretour (41, 45), orienté vers le côté (7, 15) du piston ou de la tige, est monté de manière à ce que la pression effective plus haute respective puisse, à partir du côté (7, 15) de piston ou de tige du vérin (5) de levage, être envoyée à l'accumulateur (9) hydraulique par le conduit (43) d'accumulateur en passant par le trajet respectif pour du fluide, qui peut être libéré, par ouverture du clapet antiretour (41, 45) respectif, si la pression effective du côté (7, 15) du piston ou de la tige dépasse la pression dans l'accumulateur (9) hydraulique.
  2. Dispositif suivant la revendication 1, caractérisé en ce qu'il est prévu comme actionneur hydraulique au moins un vérin (5) de levage d'une machine (1) fournissant du travail, dont un côté (7) de piston produisant une force de levage et dont un côté (17) de tige sont reliés à un bloc (13) de commande de la machine (1) fournissant du travail.
  3. Dispositif suivant l'une des revendications précédentes, caractérisé en ce qu'une vanne d'évacuation est prévue sous la forme d'une balance (37) manométrique, qui, à l'état libéré, libère le trajet (57) d'évacuation menant au côté (25) de cuve du conduit (23) d'accumulateur à l'accumulateur (9) hydraulique et menant du trajet pour du fluide respectivement libéré au vérin (5) de levage.
  4. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que la balance (37) manométrique a un raccord (53) d'entrée communiquant avec l'accumulateur (9) hydraulique, un raccord (55) de sortie communiquant avec la cuve (25), un premier raccord (47) de commande pour l'amenée d'une pression de déblocage et un deuxième raccord (35) de commande pour l'amenée d'une pression de fermeture.
  5. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que le deuxième raccord (35) de commande communique avec le côté (7) de piston du vérin (5) de levage.
  6. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que, sur la balance (37) manométrique, est effective une précontrainte (67) renforçant l'effet de la pression de fermeture sur le deuxième raccord (35) de commande.
  7. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que la balance (37) manométrique a un piston (65) de tiroir, qui, pour coulisser dans la position de fermeture, peut être chargé sur sa surface (81) de piston, tant par la pression de fermeture s'appliquant au deuxième raccord (35) de commande qu'également par la force d'un ressort (69, 71) de précontrainte, et en ce que l'autre surface (79a) de piston peut être chargée par la pression de déblocage s'appliquant sur le premier raccord (47) de commande.
  8. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que la surface (81) effective de piston, voisine du deuxième raccord (35) de commande du piston (65) de tiroir, est plus grande que la surface (79) effective de piston, qui est voisine du premier raccord (47) de commande.
  9. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que le raccord (53) d'entrée de la balance (37) manométrique est formé à l'extrémité du piston (65) de tiroir opposée au ressort (69, 71) de précontrainte, par l'ouverture axiale du côté de l'extrémité du corps (63) de tiroir, et en ce que respectivement un bord (77, 75) de commande est prévu à la partie d'extrémité associée du piston (65) de tiroir et au corps (63) de tiroir entre son ouverture du côté de l'extrémité et le premier raccord (47) de commande décalé axialement vers l'intérieur dans le corps (63).
  10. Dispositif suivant l'une des revendications précédentes, caractérisé en ce que le distributeur (27) est précontraint mécaniquement dans l'état libéré et peut être mis hydrauliquement dans l'état fermé.
  11. Dispositif suivant l'une des revendications précédentes, caractérisé en ce qu'une vanne (49) de commande met à l'état ouvert en communication le trajet pour du fluide donnant la pression effective plus haute du dispositif (11) de vanne de commande avec le premier raccord (47) de commande de la balance (37) manométrique et fournit au distributeur (27) la pression hydraulique le fermant.
EP09737365A 2008-11-07 2009-10-16 Dispositif de compensation des pressions différentielles hydrauliques Not-in-force EP2344700B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008057723A DE102008057723A1 (de) 2008-11-07 2008-11-07 Vorrichtung zum Ausgleich hydraulischer Wirkdrücke
PCT/EP2009/007422 WO2010051907A1 (fr) 2008-11-07 2009-10-16 Dispositif de compensation des pressions différentielles hydrauliques

Publications (2)

Publication Number Publication Date
EP2344700A1 EP2344700A1 (fr) 2011-07-20
EP2344700B1 true EP2344700B1 (fr) 2012-11-14

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EP09737365A Not-in-force EP2344700B1 (fr) 2008-11-07 2009-10-16 Dispositif de compensation des pressions différentielles hydrauliques

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Country Link
US (1) US9016054B2 (fr)
EP (1) EP2344700B1 (fr)
KR (1) KR101650692B1 (fr)
CN (1) CN102209814B (fr)
DE (1) DE102008057723A1 (fr)
WO (1) WO2010051907A1 (fr)

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US6966329B2 (en) * 2003-01-27 2005-11-22 Hydraforce, Inc. Proportional pilot-operated flow control valve
DE10305790A1 (de) * 2003-02-07 2004-08-26 Hydac System Gmbh Federungsvorrichtung
KR100518767B1 (ko) * 2003-05-28 2005-10-06 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 건설중장비용 액츄에이터 유량 가변제어장치
KR100518768B1 (ko) * 2003-05-28 2005-10-06 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 부하홀딩용 유압밸브의 제어장치
DE102004010053A1 (de) * 2004-03-02 2005-09-29 Hydac System Gmbh Federungsvorrichtung
US7343934B2 (en) * 2005-04-15 2008-03-18 Fema Corporation Of Michigan Proportional pressure control valve with control port pressure stabilization
DE112008000200B4 (de) * 2007-01-18 2021-08-26 Hitachi Construction Machinery Co., Ltd. Schwingungsunterdrückungsvorrichtung für hydraulische Arbeitsmaschine und hydraulische Arbeitsmaschine

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US9016054B2 (en) 2015-04-28
DE102008057723A1 (de) 2010-05-12
KR20110097795A (ko) 2011-08-31
WO2010051907A1 (fr) 2010-05-14
EP2344700A1 (fr) 2011-07-20
KR101650692B1 (ko) 2016-08-24
CN102209814A (zh) 2011-10-05
US20110197573A1 (en) 2011-08-18
CN102209814B (zh) 2014-08-27

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