EP2430319B1 - Dispositif de soupape hydraulique - Google Patents

Dispositif de soupape hydraulique Download PDF

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Publication number
EP2430319B1
EP2430319B1 EP20100717055 EP10717055A EP2430319B1 EP 2430319 B1 EP2430319 B1 EP 2430319B1 EP 20100717055 EP20100717055 EP 20100717055 EP 10717055 A EP10717055 A EP 10717055A EP 2430319 B1 EP2430319 B1 EP 2430319B1
Authority
EP
European Patent Office
Prior art keywords
connection
load
consumer
pressure
hydraulic valve
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.)
Not-in-force
Application number
EP20100717055
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German (de)
English (en)
Other versions
EP2430319A1 (fr
Inventor
Winfried RÜB
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 Filtertechnik GmbH
Original Assignee
Hydac Filtertechnik GmbH
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 Hydac Filtertechnik GmbH filed Critical Hydac Filtertechnik GmbH
Publication of EP2430319A1 publication Critical patent/EP2430319A1/fr
Application granted granted Critical
Publication of EP2430319B1 publication Critical patent/EP2430319B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F15B13/0418—Load sensing elements sliding within a hollow main valve spool
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7761—Electrically actuated valve

Definitions

  • the DE 10 2005 033 222 A1 discloses a LUDV valve assembly in which a directional control valve forms a Zulaufmeßblende, which is followed by an individual pressure compensator.
  • a LUDV control is considered a special case of a load sensing control in which the highest load pressure of the hydraulic load is reported to a variable displacement pump and this is controlled so that there is a pump pressure related to the pump performance by a certain pressure difference above the load pressure.
  • a hydraulic consumer is driven in the form of a hydraulic working or consumer cylinder, which is connected to two load terminals of the control arrangement. To adjust a rapid traverse, the two pressure chambers of the consumer can be connected to each other and to a pressure medium source.
  • this connection of the two consumer connections via a pressure fluid flow path, in which a check valve is arranged.
  • the connection of the other consumer connection to the pressure medium source and / or the first-mentioned consumer connection is possible only at rapid traverse via the pressure fluid flow path and the check valve.
  • this design measure means that a flow of pressure medium from a piston rod-side annular space to a bottom-side cylinder space is only permitted in principle, as long as the pressure in the latter is less than or approximately equal to the pressure on the piston rod side.
  • a comparable solution to the DE 10 2005 033 222 A1 is also through the EP 1 647 719 A2 shown, which relates to a regeneration valve means with independent, separate regeneration valve, which responds to the extension of the consumer cylinder, so as to establish a fluid connection from the bottom side to the ring side of the consumer cylinder, both said pressure chambers of the consumer cylinder are then connected to the return port R to To counteract any acceleration pressure or to avoid that the cylinder is not slowed down or even stopped by high loads in rapid traverse.
  • said regeneration valve corresponding space is created in the valve housing. Also, the known regeneration valve builds complicated, which should lead to increased manufacturing costs.
  • the EP 1 184 576 B1 describes a valve device for controlling a consumer, in particular in the form of a so-called. Mäh head for a also usable in forestry full mower, wherein a pressure limit of the load applied to the respective consumer of the mowing head load pressure is made possible by a control piston or a movable control device of a hydraulic valve assembly when a limit load pressure is exceeded in a pressure limiting position can be brought in the the load pressure leading consumer terminal is connected to a tank port and the load pressure continues to act on this consumer port in the flow direction on the control piston.
  • a pressure limit of the load applied to the respective consumer of the mowing head load pressure is made possible by a control piston or a movable control device of a hydraulic valve assembly when a limit load pressure is exceeded in a pressure limiting position can be brought in the the load pressure leading consumer terminal is connected to a tank port and the load pressure continues to act on this consumer port in the flow direction on the control piston.
  • the DE 603 04 663 T2 in turn describes a hydraulic valve assembly having a supply port assembly having a high pressure port P and a low pressure port T, a working port arrangement comprising two working or Nutzan getting A, B, which in turn are connectable to a hydraulic consumer, a directional valve and between the directional valve and the supply port arrangement P, T arranged compensation valve whose pressure output is connected to a pressure input of the directional valve.
  • the compensation valve has a discharge port which is connectable to a pressure outlet and has a valve element movable in the opposite direction from a starting position in the form of a slide, which is on one side of the pressure in the load-sensing conduit and the force of a spring and on the opposite side Pressure is applied to the pressure outlet.
  • the valve member As the valve member moves in one direction, it will perform a pressure control function and, when moving in the opposite direction, will perform a pressure relief function.
  • the spool has a longitudinal channel which is connected via a transverse bore to the pressure outlet and terminates in a first pressure chamber.
  • the longitudinal channel in turn goes beyond the transverse bore and leads via a closable opening to a second pressure chamber, in which a relief pressure prevails.
  • the invention has for its object to provide a cost-effective and space-saving manner a functionally reliable hydraulic valve assembly that avoids an acceleration pressure when switching from power stroke in a rapid traverse and allows monitoring of the load pressure.
  • the control device can be adjusted by a means for measuring the load pressure with the measurement simultaneously in position, it is possible that returned in a rapid traverse position of the control device when a maximum pressure is exceeded, the control device in a power stroke position becomes. This is done smoothly, since it is provided according to the invention that a valve opening cross-section between a feed line and a working connection is not changed during the transition from power stroke to rapid traverse position. It is also provided, when switching the reflux of a ring side of the consumer no longer to switch to a tank connection, but to connect to a feed channel (PA) through the user port (A). If in turn the load pressure falls during the power stroke, then the force on the means for measuring the load pressure also decreases and the movable control device assumes a proportional intermediate position between the power stroke and the rapid traverse.
  • PA feed channel
  • the means for measuring the load pressure is a measuring cylinder with volumetric flask whose first working space is fluidly connected to the Se Erasmussloadsensing connection and pressurized in rapid traverse and in the power stroke and the piston rod in a Anberichtraum the control housing of the movable control device protrudes.
  • the measuring piston is arranged to be axially movable relative to the control slide and a longitudinal channel in the control slide connects the load-sensing connection to the first working space of the measuring cylinder.
  • the measuring cylinder is an integral part of the spool, which can be moved in a particularly preferred embodiment of a maximum working position also in the rapid traverse position.
  • a control connection of the control slide with a control groove is fluid-conducting connected to one of the useful connections, in particular in the form of a working space of the hydraulic consumer.
  • pocket-like connection channels extend in the control device between a load-signaling connection and a further user connection for the consumer.
  • the movable control device is provided with further Lastmelde- and Lasttextlan whiln that interconnect paired with each other connect a load-sensing connection to a load-sensing connection and connect in dependence on the Verfahr ein the control device at least a portion of the terminals of the fluid connection arrangement fluid leading together.
  • the consumer of a consumer or working cylinder is formed with an annular space and a piston chamber as a fluid-carrying Workrooms. It is further provided that in a change from power stroke to rapid traverse then the annular space of the consumer cylinder is connected to the Nutzanschluß A as a feed line.
  • the hydraulic valve device can also be used in other hydraulic drives, such as traction motors of electro-hydraulic vehicles and more.
  • the pertinent paired hydraulic motor assembly then has fluid-carrying working spaces and a the annular space of the working cylinder corresponding working space of the respective hydraulic motor is then to connect to the supply line via the Nutzanschluß A with this and the other fluid-carrying spaces of the respective hydraulic motor are comparable to the piston chamber of said consumer cylinder as working space head for.
  • FIGURE shows a partial longitudinal section through the valve device according to the invention.
  • valve assembly 1 with a designated as a whole with 10 fluid port assembly, which includes a pressure supply port P, a return port R, a section load sensing LS, two control terminals P ' A and P' B and two payload A, B has.
  • the fluid ports LS, P ' A , R, P and P' B , A and B are housed in a common control housing 12, which is seen in the figure at the end of the control housing 12 is provided with a known pressure compensator 14, the Terminals LS, P ' A , R, P and P' B is connected upstream and these controls.
  • the pressure compensator 14 enables a so-called pressure medium quantity cut by a pressure limitation (not shown) (LS) in a spring chamber 16 of the pressure compensator 14 in order to cut off the amount of inflow, for example in the case of a fluidic load connected to the service connections A, B in the form of a hydraulic consumer cylinder 4, in order to avoid overloading the load.
  • LS pressure limitation
  • a movable control device 18 of the valve assembly 1 is driven by two pilot valves 20,22, the sake of simplicity in the figure are shown only insofar as their respective assignable housing connections are shown in the control housing 12.
  • the pertinent control via pilot valves is common, so that will not be discussed in more detail here at this point.
  • the respective pilot valve 20,22 accommodated in a assignable housing 24,26, which are flanged on both sides of the center part of the control housing 12 and in addition to the usual connections T 0 and P ST on the bottom side ports for the purpose of applying two counteracting control pressures X A and X B.
  • About the port P ST is the pump control pressure to the respective pilot valve 20,22 and further the pertinent pilot valves are connected to said tank connection line T 0 .
  • Said control device 18 has a horizontally displaceable control slide 28, viewed in the direction of the figure, which is shown in the figure in its floating position deflected to the left.
  • the neutral position is effected by two counter-acting spring accumulator in the form of compression springs 30, which are integrated in a respective spring chamber through which pressure medium X A , X B spring chamber in the pilot housings 24,26.
  • the control device 18 with spool 28 is provided with load-sensing terminals 32,34 and load-sensing terminals 36,38, which are interconnected in pairs carrying fluid.
  • the first load-sensing terminal 32 is fluidly connected to the second load-sensing terminal 38 and the second load-indicating connection 34 is in fluid-conducting connection with the first load-sensing connection 36.
  • the connections mentioned are introduced as radial transverse bores into the control slide 18 and come into respectively open or blocking connection with the connections of the fluid connection arrangement which can be assigned in this respect, depending on the displacement position of the control slide 28 10 as shown in the figure.
  • the spool 28 has along its outer periphery at least two longitudinally oriented, pocket-like control channels 48,50, which open in the neutral position of the spool 28 respectively in the Nutzanschluß A and the Nutzanschluß B. Further, in the control channel 48, a dividing partition 58 is retracted, at least in the area of the utility connection A, wherein in the figure shown floating position of the spool 28 of the Nutzanschluß A in fluid industrialder connection with even further in the outer periphery of the spool 28 introduced fluid carrying pockets 56 which in the position shown in a the spool 28 encompassing annular channel, which in turn is connected to the return port R.
  • the designated control channel 50 forms with its opening cross-section in the direction of the user port B, the so-called orifice of the valve device and seen in the direction of the figure is left of the partition 58 of the other part of the pocket-like control channel 48 for the backflow into the feed channel P ' A Responsible in rapid traverse.
  • connecting channels 40, 42 arranged within the control slide 28 are used.
  • the one connecting channel 40 is formed as a so-called.
  • Central channel which covers in the neutral position of the control device 18 shown in the figure with its axial length between the section load sensing connection LS and the Nutzanschluß B.
  • the pertinent Center channel 40 begins in the direction of the figure seen on the left side of the spool 28 and extends along the center axis to the bore of the measuring cylinder 5.
  • the connecting channel 42 is provided in parallel as a ring longitudinal channel, in the neutral position of the control device 18 with its axial length at least covers the area between control terminal P ' A and user port A.
  • the center channel 40 is limited to the limit of the possible channel guides so far edge of an insert sleeve 44, which at least partially along its outer periphery in a predetermined central region arranged with the inner wall of the spool 28 in this area limits the longitudinal annular channel 42.
  • the annular longitudinal channel 42 may also be formed from a plurality of concentric with the central channel 40 individual channels (not shown in detail).
  • the axial position of the insert sleeve 44 extends according to the figure between the first load-sensing connection 32 and a narrowed offset point between the first load-sensing connection 36 and the second load-sensing connection 38 at the height of the return connection R.
  • the opposite other free end in the region of the first load-indicating connection 32 is based on a compression spring extending between a closure plug 46 and the free end of the sleeve and extent with a predetermined bias the insert sleeve 44 holds in their position.
  • any existing length tolerances in the system insert sleeve 44 can be compensated to the inside of the spool 28.
  • a rapid traverse position for the connected hydraulic consumer 4 is achieved in that the spool 28 is moved beyond the so-called.
  • Lifting position also seen in the direction of the figure to the right and the so-called.
  • Floating position for the consumer can be by a kind Overlift of the spool 28 on the so-called.
  • Lower position in the direction seen on the figure reach to the left. Starting from the neutral position shown in the figure, therefore, the spool 28 is moved to the right first in the lifting and then in the rapid traverse position for the consumer or moved in the opposite direction, starting from the neutral position to the left over the lowering position in the floating position.
  • the control channel 50 comes with increasing traversing movement of the spool 28 in the direction of lifting position in overlap with the control terminal P ' B , which leads to an enlargement of the relevant Meßblendenquerites.
  • a means 2 designed as a measuring cylinder 5 for measuring the load pressure in the useful connection B is present.
  • the measuring cylinder 5 has a measuring piston 6 and a piston rod 8, which is reduced in diameter relative to the measuring piston 6. Further, the piston rod 8 extends through on its right free end a bottom 9 of the spool 28 and the free right end of the piston rod 8 opens into the spring chamber, which is connected to the pilot control port X B.
  • the load-sensing connection 38 which opens into the return connection R in the center or neutral position of the control spool 28, is transferred on the opposite connection side into a longitudinal channel 15, which is in fluid-conducting connection with the center channel 40.
  • the longitudinal channel 15 terminates in a first working space 7 of the measuring cylinder 5, which is filled in the illustration shown by the measuring piston 6, which also closes the right channel end free cross section of the longitudinal channel 15.
  • the spool 28 moves the spool 28 as seen in the direction of the figure to the right, the spool takes the measuring cylinder 5 also to the right with the result that the load sensing port 38 in register with the Ring channel comes to which the user terminal B is connected, so that in the pertinent right position of the load sensing terminal 38 as load sensing terminal LS B for the pending in Nutzan gleich B load pressure is used, the pertinent Loadsensing réelle LS B in turn via the longitudinal channel 15 to the measuring cylinder 5 is passed. Consequently, the load-sensing connection 38 continues via the longitudinal channel 15 as a section load-sensing connection LS B and opens into the first working space 7 of said measuring cylinder 5.
  • the measuring cylinder 5 is moved to the right, at least until the piston rod 8 abuts with its right free end 11 against the end wall 13 of the spring chamber of the pilot housing 26.
  • a throttle or non-return valve arrangement is preferably provided.
  • the free cross section of the valve opening 50 between feed line P and working connection B is not changed during the transition from the power stroke to rapid traverse.
  • a monitoring of the load pressure with said measuring means 2 and a load-dependent switching from rapid traverse to power stroke is performed. If the cylinder piston unit of the consumer 4 is driven in rapid traverse and the load pressure rises to the maximum permitted pressure, the measuring cylinder arrangement 5 in the control spool 28 switches it back into the power stroke. Then again the maximum lifting power is available and due to the connection of the return flow from the ring side 3 in the feed channel, it does not unintentionally to a shift shock.
  • the force on the measuring cylinder 5 also decreases and the control spool 28 assumes a proportional intermediate position between power stroke and rapid traverse, with a throttled connection of the cylinder ring side 3 to the T return.
  • the throttled pressure on the cylinder ring side 3 must be set lower than the feed pressure in the pump inlet P, because only then can the lifting force be increased. As a result, no volume flow can now flow back into the feed channel from the cylinder ring side 3 (no regeneration). Conversely, no flow from the feed channel A flows to the ring side 3 of the consumer, either the throttle point must separate the pressure chambers from each other or a check valve, as stated, prevent the flow.
  • the consumer or working cylinder 4 may also be another hydraulic consumer, for example in the form of a hydraulic motor for a traction drive, be it in a vehicle, be it in a lifting device, such as an elevator, and the like.
  • a fluid-carrying working space of the consumer in correspondence to the annular space 3 of the consumer cylinder 4 when switching the control device 18 in the sense of a change from power stroke to rapid traverse to the user port A or B to connect as an effective feed line.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (10)

  1. Dispositif hydraulique à vanne, comprenant un agencement (10) de raccordement de fluide comportant au moins
    - un raccord (P) d'alimentation sous pression,
    - un raccord (R) de retour,
    - un raccord (LS) loadsensing de section,
    - deux raccords (P'A) et (P'B) de commande, ainsi que
    - deux raccords (A, B) utiles
    auquel au moins un consommateur (4) est raccordé par ses chambres de travail fluidiques,
    et comprenant un dispositif (18) déplaçable de commande, pour la commande au moins partielle de raccords de l'agencement (10) de raccordement de fluide, caractérisé en ce que le dispositif (18) de commande peut être mis dans une position de levage par force et inversement par un moyen (2) de mesure de la pression de charge dans une position de déplacement rapide lors du dépassement d'une pression de charge maximum et en ce que, dans une commutation du dispositif (18) de commande au sens d'un passage du levage par force au déplacement rapide, le reflux d'un côté (3) annulaire du consommateur (4) ne peut plus être branché sur un raccord (T) de cuve, mais communique avec un canal (PA) d'alimentation par le raccord (A) utile.
  2. Dispositif hydraulique à vanne suivant la revendication 1, caractérisé en ce que le moyen (2) de mesure de la pression de charge est un cylindre (5) de mesure, qui a un piston (6) de mesure, dont la première chambre (7) de travail communique fluidiquement avec un raccord (LSB) loadsensing de section et est alimentée en pression en déplacement rapide et en levage par force.
  3. Dispositif hydraulique à vanne suivant la revendication 2, caractérisé en ce que le piston (6) de mesure est pourvu d'une tige (8) de piston, qui, dans chaque état de déplacement du piston (6) de mesure, pénètre par son extrémité libre dans une chambre (XB) de commande d'une boîte (26) pilote, à laquelle est raccordée une soupape (22) pilote.
  4. Dispositif hydraulique à vanne suivant la revendication 2 ou 3, caractérisé en ce que le piston (6) de mesure est monté coulissant axialement dans le tiroir (28) de commande et un canal (15) longitudinal du tiroir (28) de commande met le raccord (LSB) loadsensing de section en communication fluidique avec la première chambre (7) de travail du cylindre (5) de mesure.
  5. Dispositif hydraulique à vanne suivant l'une des revendications 2 à 4, caractérisé en ce que le cylindre (5) de mesure est disposé à l'intérieur du dispositif (8) de commande, qui peut être déplacé.
  6. Dispositif hydraulique à vanne suivant l'une des revendications 1 à 5, caractérisé en ce que le dispositif (8) de commande, qui peut être déplacé, peut coulisser au-delà d'une position de travail maximum pour le consommateur (4) dans une position de déplacement rapide en direction de la soupape (22) pilote.
  7. Dispositif hydraulique à vanne suivant l'une des revendications 1 à 6, caractérisé en ce que le dispositif (8) de commande est pourvu de raccords (32, 34 ; 36, 38) d'indication de charge et de détection de charge, qui, branchés entre eux par paires, associent un raccord d'indication de charge à un raccord (32, 38 ; 34, 36) de détection de charge et qui, en fonction de la position en déplacement du dispositif (18) de commande, font communiquer fluidiquement entre eux au moins une partie des raccords de l'agencement (10) de raccordement de fluide.
  8. Dispositif hydraulique à vanne suivant la revendication 7, caractérisé en ce que le raccord (38) de détection de charge constitue un trou transversal radial dans le dispositif (18) de commande, qui débouche dans le canal (15) longitudinal du dispositif (18) de commande et qui prélève la pression au raccord (LSB) de loadsensing, dès que le raccord (36) de détection de charge débouche dans le raccord (B) utile auquel.est raccordé la chambre de travail pouvant être associée du consommateur (4).
  9. Dispositif hydraulique à vanne suivant l'une des revendications 1 à 8, caractérisé en ce que le consommateur est formé d'un cylindre de consommateur ayant une chambre (3) annulaire et une chambre de piston en tant que chambre de travail fluidique et en ce que, lors du passage du levage par force au déplacement rapide, la chambre (3) annulaire communique avec le raccord (A) utile comme conduit d'alimentation.
  10. Dispositif hydraulique à vanne suivant l'une des revendications précédentes, caractérisé en ce qu'une section transversale d'ouverture de vanne entre un conduit d'alimentation et un raccord de travail ne peut pas être modifiée lors du passage du levage par force à la position de déplacement rapide.
EP20100717055 2009-05-13 2010-04-23 Dispositif de soupape hydraulique Not-in-force EP2430319B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910021103 DE102009021103A1 (de) 2009-05-13 2009-05-13 Hydraulische Ventilvorrichtung
PCT/EP2010/002501 WO2010130334A1 (fr) 2009-05-13 2010-04-23 Dispositif de soupape hydraulique

Publications (2)

Publication Number Publication Date
EP2430319A1 EP2430319A1 (fr) 2012-03-21
EP2430319B1 true EP2430319B1 (fr) 2013-05-29

Family

ID=42342004

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20100717055 Not-in-force EP2430319B1 (fr) 2009-05-13 2010-04-23 Dispositif de soupape hydraulique

Country Status (6)

Country Link
US (1) US20110308642A1 (fr)
EP (1) EP2430319B1 (fr)
JP (1) JP2012526952A (fr)
DE (1) DE102009021103A1 (fr)
DK (1) DK2430319T3 (fr)
WO (1) WO2010130334A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013010390A1 (de) * 2013-06-20 2014-12-24 Hydac Accessories Gmbh Steuervorrichtung für hydraulisch betätigbare Arbeitseinheiten

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2593265B1 (fr) * 1986-01-17 1988-04-22 Rexroth Sigma Distributeur de fluide hydraulique sous pression
DE4234037C2 (de) * 1992-10-09 2001-03-22 Mannesmann Rexroth Ag Ventilanordnung, insbesondere für mobile Arbeitsgeräte
DE19631803B4 (de) * 1996-08-07 2007-08-02 Bosch Rexroth Aktiengesellschaft Hydraulische Steuervorrichtung
DE10041168A1 (de) 2000-08-21 2002-03-07 Mannesmann Rexroth Ag Ventileinrichtung
DE10258517B3 (de) 2002-12-14 2004-06-03 Sauer-Danfoss (Nordborg) A/S Hydraulische Ventilanordnung
KR100611713B1 (ko) 2004-10-14 2006-08-11 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 재생기능을 구비한 유압제어밸브
DE102005033222B4 (de) 2005-07-15 2012-05-16 Bosch Rexroth Aktiengesellschaft LUDV-Ventilanordnung
DE102006007935A1 (de) * 2006-02-21 2007-10-25 Liebherr France Sas Steuervorrichtung und hydraulische Vorsteuerung
DE102007054134A1 (de) * 2007-11-14 2009-05-20 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102007054137A1 (de) * 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102007054138A1 (de) * 2007-11-14 2009-05-28 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102008006879A1 (de) * 2008-01-31 2009-08-06 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung

Also Published As

Publication number Publication date
WO2010130334A1 (fr) 2010-11-18
EP2430319A1 (fr) 2012-03-21
JP2012526952A (ja) 2012-11-01
DE102009021103A1 (de) 2010-11-18
DK2430319T3 (da) 2013-07-22
US20110308642A1 (en) 2011-12-22

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