EP2220380B1 - Vanne hydraulique - Google Patents

Vanne hydraulique Download PDF

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Publication number
EP2220380B1
EP2220380B1 EP20080850047 EP08850047A EP2220380B1 EP 2220380 B1 EP2220380 B1 EP 2220380B1 EP 20080850047 EP20080850047 EP 20080850047 EP 08850047 A EP08850047 A EP 08850047A EP 2220380 B1 EP2220380 B1 EP 2220380B1
Authority
EP
European Patent Office
Prior art keywords
connector
control
valve device
load
fluid
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
EP20080850047
Other languages
German (de)
English (en)
Other versions
EP2220380A1 (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 EP2220380A1 publication Critical patent/EP2220380A1/fr
Application granted granted Critical
Publication of EP2220380B1 publication Critical patent/EP2220380B1/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
    • 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
    • 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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric
    • 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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86622—Motor-operated
    • Y10T137/8663—Fluid motor
    • 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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]

Definitions

  • a hydraulic valve assembly is known with 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 are connectable to a 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, wherein the compensation valve has a discharge outlet, which is connectable to the pressure outlet and a movable from an initial position in opposite directions valve element in the form of a slide on one side of the pressure in the load-sensing line and the force of a spring and acted on the opposite side of the pressure at the pressure outlet is, wherein the valve element when moving in one direction, a pressure regulating function and when moving in the opposite direction performs a pressure relief function, wherein the slide has a longitudinal channel, which is connected via a transverse bore to the pressure output and ends in a first pressure chamber, and wherein the longitudinal channel beyond
  • a similar directional valve is known as a hydraulic valve device, which is used to control the pressure and flow of hydraulic oil to or from working ports A, B at least one consumer, wherein the pressure and the flow by means of at least one actuator operable in a slide bore displaceable spool as a movable control device and thus operatively connected annular channels is controllable, wherein in the center of symmetry on a symmetry axis of the valve device a tank connection annular channel is arranged as so-called. Return connection and on both sides further existing ring channels are also arranged symmetrically to the axis of symmetry. Due to the aforementioned symmetrical structure this is in the known solution so far from a constructive point of view simple and allows a cost-effective production. Also, the known valve device should have an improved dynamic switching behavior and have a large range of functions.
  • the invention is based on the object to further improve this while maintaining its advantages that the reliability is further increased and that the solution according to the invention can be well designed with respect to changing applications in terms of a modular system ,
  • This object is achieved by a hydraulic valve device having the features in the entirety of claim 1.
  • the control device can be easily adapted to a variety of fluidic applications use cases in the sense of a modular building block concept that thereby larger conversion or adaptation work on the hydraulic valve device are necessary. Due to the asymmetric structure of the control device, which acts so far on the fluid connection arrangement, a safe control behavior is achieved and the controller can be so far with a very favorable dynamic travel behavior position accurately in the functional positions bring.
  • the solution according to the invention also constructs a short construction, so that all relevant switching and control positions for the hydraulic valve devices can be realized in a small installation space.
  • control device can also assume a so-called floating position, without there being any loss of resolution in the lowering and lifting region relative to the working or utility connections A, B.
  • the proportional range in lifting and lowering is fully maintained, the housing length is still kept short in length due to the special design of the control device, to which the asymmetric design of the hydraulic valve device contributes.
  • control device is preceded by a pressure compensator with which the so-called quantity cut-off is possible by means of a load-sensing pressure limitation in the spring chamber of the pressure compensator.
  • a pressure compensator with which the so-called quantity cut-off is possible by means of a load-sensing pressure limitation in the spring chamber of the pressure compensator.
  • this function of Mengenabschneidung is not possible or to obtain only over appropriate additional valve constructions in a complex manner.
  • control function of the pressure compensator is improved by a relatively large outflow cross-section opens into the return port. Also, the so-called. Floating position is improved.
  • the Fig.1 shows a designated as a whole with 10 fluid port arrangement.
  • the pertinent fluid port assembly 10 has a pressure supply port P, a return port R, a section load sensing port LS, two control ports P A 'and P B ' and two payload ports A, B on.
  • the aforementioned fluid ports LS, P A ', R, P and P B ', A and B are housed in a control housing 12, wherein in the direction of the Fig.1 seen the lower end of the control housing 12 is provided with a per se conventional pressure compensator 14, which is the terminals LS, P A ', R, P and P B ' upstream and this controls so far.
  • the function quantity cutoff is achieved by means of an LS pressure limitation in the spring chamber 16 of the pressure compensator, whereby a quantity cutoff makes sense, for example, if a steering cylinder connected to the useful connections A, B, is at the stop and you want to cut off the inflow to the extent to avoid overloads.
  • the control device 18 as such is controlled in a known and therefore not described in more detail manner of conventional pilot valves 20,22, which in the Figure 3 are reproduced with their hydraulic symbols and the sake of ease of representation in the Fig.1 are shown only insofar as their respective assignable pilot housing 24,26 are addressed.
  • the two pilot valves 20, 22 for the control device 18 supply two counteracting control pressures X A and X B, respectively.
  • a pump control pressure P ST acts on the respective pilot valve 20, 22 and a tank connection line T O is likewise connected to the respective pilot valve.
  • the aforementioned control device 18 has a viewing direction on the Fig.1 seen horizontally displaceable spool 28, in the Fig.1 is shown in its undeflected middle or neutral position.
  • the pertinent neutral position of the spool 28 is supported by two spring memory, which are designed as compression springs 30 and are integrated in a respective assignable spring chamber in the pilot housings 24,26.
  • the pertinent structure is known in the pertinent hydraulic valve devices, so that in this respect will not be discussed in more detail here at this point.
  • the control device 18 with control slide 28 is provided with anti-swirl connections 32, 34 as well as with load-sensing connections 36, 38, which are interconnected in pairs to carry fluid.
  • the first load-avoidance port 32 is fluidly connected to the second load-sensing port 38 and the second load-sensing port 34 is in fluid communication with the first load-sensing port 36.
  • Said reporting ports and sensing ports are inserted into the spool 18 in the form of radial cross-bores and depending on which axial Verfahr ein the spool 18 occupies the said connections 32, 34, 36 and 38 come into fluid-conducting or blocking connection with the respectively assignable connections of the fluid connection arrangement 10.
  • the center channel is in the direction of the Fig.1
  • this is provided as a further connecting channel 42 at least one annular longitudinal channel, which in turn in the neutral position of the control device 18 with its axial length covers at least the area between the control terminal P A 'and user port A.
  • the Lastmelde- and Lastcronlan whatever 32,36; 34,38 are each formed as radially extending Boh ments in the spool 28.
  • the middle channel 40 is limited to produce the channel guides insofar by an insert sleeve 44 which at least partially along its outer periphery in a predetermined center region arranged with the inner wall of the spool 28 in this area limits the longitudinal annular channel 42, which is so far from a plurality of concentric to the center channel 40 arranged individual channels (not shown) may be formed.
  • the axial length of the insert sleeve 44 extends as shown in the Fig.1 between the first load-signaling connection 32 and a narrowed offset point between the first load-sensing connection 36 and the second load-sensing connection 38 in the height of the return connection R.
  • the opposite other free end in the region of the first load signaling connection 32 is based on a compression spring, which extends in this respect between a closure plug 46 and the free end of the sleeve and insofar with a predeterminable Preload holding the insert sleeve 44 in position.
  • a compression spring which extends in this respect between a closure plug 46 and the free end of the sleeve and insofar with a predeterminable Preload holding the insert sleeve 44 in position.
  • About the pertinent arrangement can be optionally existing length tolerances in the system, insert sleeve 44 to spool 28, compensate.
  • the spool 28 along its outer periphery two longitudinal control channels 48,50, which open in the neutral position of the control device 18 respectively in the Nutzanschluß A and the Nutzanschluß B.
  • the load sensing bore 36 under the housing wall between the user port A and the return port R.
  • the hydraulic valve device forms a so-called. LS directional control valve with upstream pressure compensator 14.
  • at least one pressure relief valve 52 is provided for securing parts of the hydraulic circuit, and the load-sensing LS is compared with LS max by means of a shuttle valve 54 togl ichen.
  • the hydraulic valve device according to the invention is designed as a LS-way valve with upstream pressure compensator 14 and has a valve-length of the construction short design on with respect to known solutions less ring channels.
  • upstream pressure compensator 14 is the function already described quantity cut by LS-pressure limitation in the spring chamber of the pressure compensator 14 possible.
  • the spool 28 along its outer periphery between the two groove-like control channels 48,50 still separate pockets 56 which are separated from each other in awake Kunststofffichen angular arrangements along said spool 28 extend.
  • a segmenting partition wall 58 is retracted and in the in the Fig.2 shown floating position is the user port A in fluid-carrying connection with the individual pockets 56 of the spool 28th
  • valve arrangement shown in the Fig.2 using additional pockets 56 between the two control channels 48,50 can reach a floating position for the valve without loss of resolution in lowering and lifting area of the hydraulic arrangement.
  • valve device solution it is possible to solve the combination of a floating position and a rapid traverse in a mobile valve in slide construction, which is useful in particular for use in conventional machines (not shown), in which work equipment to move quickly and / or if these in a way Pivoting off or hang up, which is the case for example for a mower bar a slope mower od.
  • a floating position and a rapid traverse in a mobile valve in slide construction which is useful in particular for use in conventional machines (not shown), in which work equipment to move quickly and / or if these in a way Pivoting off or hang up, which is the case for example for a mower bar a slope mower od.
  • the pertinent Lastmeldebohrung ends so far on the lateral surface of the spool 28, wherein the lateral surface is guided around the outlet of the detection hole locally. Otherwise, the lateral surface is here opened and recessed to create a return flow from A to P.
  • the rotational position of the load detection bore and housing pocket is maintained, not shown, mechanical anti-rotation for the spool 28 is present.
  • the further load-sensing bore is then in the R-channel and the corresponding further load-sensing bore is under the housing wall between P A 'and the A-channel.
  • a rapid traverse position of the spool 28 is achieved in each case by an overstroke on the so-called. Lifting position and the floating position on the so-called. Lowering position of the connected hydraulic components of the machine. This corresponds to the desired working conditions at the mentioned machines, because the rapid traverse as switching position should not be switched on directly from "neutral", in order to avoid an excessive switching pressure.
  • the radial load sensing bore and the radial load sensing bore are each covered by the housing wall.
  • the concept of the short design requires that in the position "lifting" (working position of the working machine) drives the load detection hole of the terminal A in the P port and the load sensing bore in the R port.
  • a check valve 60 is installed in the corresponding connecting line 62. In the so-called. Lower position and in the neutral position, a spring holds the check valve 60 then open, so that both a pressure message is guaranteed as well as a dynamic flow, which is due to the control movements of the connected pressure compensator 14.
  • the pressure drop at the check valve at rapid control movements of the pressure compensator 14 and the spring force are coordinated so that at fast control movements, as they correspond to a high flow, the check valve 60 can not close.
  • the leakage flow from P to R immediately becomes so high that the Pressure drop across the open check valve 60 overcomes the spring force and the check valve closes safely.
  • the floating position is achieved by overtravel on the lowering position and the lifting position of each connected machine. In that regard, it is possible that only when the implement has been placed in the lowered position, for example, on the ground, then the floating position is turned on.
  • check valves 60 shown can also in the embodiment of the Fig.1 and 2 are used in the local control channels 48,50 (not shown), in which case the closing ball opens in each case in the direction of the load-sensing connection in order to achieve comparable results, as described above.
  • valve device can be standard way valves with the three basic positions for neutral, lifting and lowering extend in scope to a floating position and / or a rapid traverse, without this, as in the known slide valve solutions, comes to an extension of the slide stroke to to get into the additional position with the desired logical operations; Rather, with the solution according to the invention, a pusher slide extension can be completely avoided or the slide valve axis can even be shortened.

Claims (15)

  1. Dispositif de vanne hydraulique ayant un agencement (10) de raccordement pour un fluide comprenant au moins
    - un raccord (P) d'alimentation en pression,
    - un raccord (R) de retour,
    - un raccord (LS) de détection de charge de section,
    - deux raccords (PA') et (PB') de commande, ainsi que
    - deux raccords (A, B) utiles,
    et comprenant un dispositif (18) de commande déplaçable, pour commander au moins en partie des raccords de l'agencement (10) de raccordement pour un fluide, dans lequel le dispositif (18) de commande est pourvu de raccords (32, 34 ; 36, 38) d'indication de charge et de remplissage de charge, qui en étant branchés par paire l'un avec l'autre, associent un raccord d'indication de charge à un raccord de charge (32, 38 ; 34, 36) de remplissage et qui, en fonction de la position en déplacement du dispositif (18) de commande, mettent en communication fluidique au moins une partie des raccords de l'agencement (10) de raccordement pour un fluide, le dispositif (18) de commande comportant un tiroir (28) de commande ayant des canaux (40, 42) fluidiques de liaison, qui relient entre eux les raccords (32 36 ; 34 38) d'indication de charge et de remplissage de charge pouvant être associés l'un à l'autre par paire, et dans lequel au moins l'un des canaux (40) de liaison est formé en canal médian et au moins un autre des canaux (42) de liaison est formé en canal longitudinal annulaire qui, dans la position neutre du dispositif (18) de commande, recouvre par sa longueur axiale au moins la zone comprise entre le raccord (PA') de commande et le raccord (A) utile, caractérisé en ce que le canal (40) médian est délimité par une douille (44) rapportée, qui le long de son pourtour extérieur, délimite avec la paroi intérieur du dispositif (18) de commande le canal (42) longitudinal annulaire respectif.
  2. Dispositif de vanne suivant la revendication 1, caractérisé en ce que, dans la position neutre du dispositif (18) de commande, le canal (40) médian recouvre, par sa longueur axiale, la zone comprise entre le raccord (LS) de détection de charge de section et le raccord (B) utile.
  3. Dispositif de vanne suivant la revendication 1 ou 2, caractérisé en ce que le dispositif (18) de commande peut être commandé par deux vannes (20, 22) pilotes agissant en sens opposé et être maintenu, en étant centré par un ressort, dans sa position neutre.
  4. Système hydraulique suivant l'une des revendications 1 à 3, caractérisé en ce que le tiroir (28) de commande a, le long de son pourtour extérieur, au moins deux canaux (48, 50) de commande de type en rainure, orientés longitudinalement, qui, dans la position neutre du dispositif (18) de commande, débouchent respectivement dans le raccord (A) utile et dans le raccord (B) utile.
  5. Dispositif de vanne suivant la revendication 4, caractérisé en ce que, dans la position neutre du tiroir (28) de commande, respectivement un trou (36, 38) radial de remplissage de charge se termine, de manière décalée sur le pourtour par rapport au canal (48, 50) de commande qui peut lui être associé, sous la paroi respective de séparation du corps, qui se trouve respectivement entre les raccords (A, B) utiles et le raccord (R) de retour.
  6. Dispositif de vanne suivant la revendication 5, caractérisé en ce que les trous (36, 38) de remplissage de charge sont séparés fluidiquement les uns des autres.
  7. Dispositif de vanne suivant l'une des revendications 1 à 6, caractérisé en ce que, dans la position neutre du tiroir (28) de commande, les trous (32, 34) radiaux d'indication de charge débouchent respectivement des deux côtés à côté du raccord (LS) de détection de charge de section et sont recouverts par une paroi du corps.
  8. Dispositif de vanne suivant l'une des revendications 4 à 7, caractérisé en ce que, dans la position neutre du tiroir (28) de commande, un canal longitudinal du tiroir (28) de commande relie fluidiquement la borne (LS) de détection de charge de section à une chambre (XA) de commande du dispositif de vanne.
  9. Dispositif de vanne suivant l'une des revendications 1 à 8, caractérisé en ce qu'en amont du dispositif (18) de commande avec ses raccords pour du fluide est montée une bascule (14) manométrique qui commande au moins en partie l'agencement (10) de raccordement pour du fluide.
  10. Dispositif de vanne suivant l'une des revendications 5 à 9, caractérisé en ce que, dans une position flottante du tiroir (28) de commande, l'un de ses canaux (48) annulaires, qui débouche dans le raccord (A) utile, comporte une cloison (58) qui sépare le raccord (PA') de commande au raccord (A) utile.
  11. Dispositif de vanne suivant l'une des revendications 1 à 10, caractérisé en ce qu'au moins pour une partie des canaux (40, 42) de liaison, au moins un clapet (60) anti-retour est inséré entre les raccords d'indication de charge et de remplissage de charge pouvant être associés l'un à l'autre par paire.
  12. Dispositif de vanne suivant la revendication 11, caractérisé en ce que le clapet (60) anti-retour respectif à l'intérieur des canaux de liaison ferme dans la direction de remplissage de charge (A), ainsi que d'indication de charge (B) ou de remplissage de charge (B) ainsi que d'indication de charge (A).
  13. Dispositif de vanne suivant la revendication 11, caractérisé en ce que le tiroir (28) de commande peut être déplacé au-delà d'une position maximum de travail pour venir dans une position de déplacement rapide.
  14. Dispositif de vanne suivant la revendication 11, caractérisé en ce que le tiroir (28) de commande relie dans sa position de déplacement rapide, par une rainure (50) de commande, le raccord (PB') de commande au raccord (B) utile et, par ses canaux de liaison supplémentaires en forme de poche entre les trous (LSA) d'indication, relie le raccord (A) utile au raccord (PA) de commande.
  15. Dispositif de vanne suivant la revendication 11, caractérisé en ce que les trous (LSA) et (LSB) d'indication de charge du tiroir (28) de commande sont dirigés, dans leur position en rotation, sur des élargissements locaux du raccord (LS) de détection de charge de section.
EP20080850047 2007-11-14 2008-10-09 Vanne hydraulique Not-in-force EP2220380B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200710054137 DE102007054137A1 (de) 2007-11-14 2007-11-14 Hydraulische Ventilvorrichtung
PCT/EP2008/008519 WO2009062572A1 (fr) 2007-11-14 2008-10-09 Vanne hydraulique

Publications (2)

Publication Number Publication Date
EP2220380A1 EP2220380A1 (fr) 2010-08-25
EP2220380B1 true EP2220380B1 (fr) 2012-12-19

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Application Number Title Priority Date Filing Date
EP20080850047 Not-in-force EP2220380B1 (fr) 2007-11-14 2008-10-09 Vanne hydraulique

Country Status (6)

Country Link
US (1) US8464757B2 (fr)
EP (1) EP2220380B1 (fr)
JP (1) JP5462178B2 (fr)
DE (1) DE102007054137A1 (fr)
DK (1) DK2220380T3 (fr)
WO (1) WO2009062572A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8863115B2 (en) 2008-03-20 2014-10-14 Sap Ag Execution of program code having language-level integration of program models
DE102009021103A1 (de) * 2009-05-13 2010-11-18 Hydac Filtertechnik Gmbh Hydraulische Ventilvorrichtung
DE102009058371A1 (de) 2009-12-15 2011-06-16 Hydac Filtertechnik Gmbh Ventilanordnung zur Ansteuerung eines Verbrauchers
JP2014173616A (ja) * 2013-03-06 2014-09-22 Caterpillar Sarl 作業機械の圧損低減回路
JP2016156405A (ja) * 2015-02-23 2016-09-01 アネスト岩田株式会社 パイロットバルブ
ITUA20162417A1 (it) * 2016-04-08 2017-10-08 Atlantic Fluid Tech S R L Valvola di controllo direzionale
DK3775576T3 (da) 2018-05-18 2022-08-08 Hydac Systems & Services Gmbh Styreindretning
DE102018207929A1 (de) * 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Ventil
DE102018212312A1 (de) * 2018-07-24 2020-01-30 Robert Bosch Gmbh Ventilbaugruppe mit Lasthaltung, Druckwaage und Kopierventil
US10876552B2 (en) * 2018-09-21 2020-12-29 Eaton Intelligent Power Limited Hydraulic fluid pressure compensator unit with integrated load sense and reverse flow checks
DE102020208932A1 (de) 2020-07-16 2022-01-20 Robert Bosch Gesellschaft mit beschränkter Haftung Ventil mit selbsttätiger Rücklaufreduzierung bei ziehenden Lasten
CN115325214B (zh) * 2022-10-13 2023-01-24 南通埃东石化设备制造有限公司 一种出水量恒定的手动调节阀

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3565110A (en) * 1969-08-04 1971-02-23 Commercial Shearing Control valves
JPS549276B2 (fr) * 1972-02-29 1979-04-23
US3771564A (en) * 1972-03-23 1973-11-13 Caterpillar Tractor Co Pilot control valve
US4253482A (en) * 1979-03-05 1981-03-03 Gresen Manufacturing Company Hydraulic valve having pressure compensated demand flow
US4617798A (en) * 1983-04-13 1986-10-21 Linde Aktiengesellschaft Hydrostatic drive systems
SE458704B (sv) * 1987-05-18 1989-04-24 Atlas Copco Ab Anordning vid ett hydrauliskt drivsystem anslutet till en lastdrivande hydraulmotor
DE8801058U1 (fr) * 1988-01-29 1988-03-10 Danfoss A/S, Nordborg, Dk
JP3119722B2 (ja) * 1992-05-25 2000-12-25 株式会社小松製作所 圧力比例制御弁による４位置クローズドセンタの切換弁の油圧回路
JPH06280805A (ja) * 1993-03-25 1994-10-07 Komatsu Ltd 圧油供給装置
IT1281708B1 (it) * 1996-01-24 1998-02-26 Brevini Hydraulics Spa Dispositivo per l'azionamento di un'utenza idraulica con una velocita' di azionamento indipendente dal carico resistente gravante su tale
US5765594A (en) * 1996-04-02 1998-06-16 Danfoss A/S Hydraulic control valve
WO1998031940A1 (fr) * 1997-01-21 1998-07-23 Hitachi Construction Machinery Co., Ltd. Distributeur dote d'une vanne de distribution
JP4428856B2 (ja) * 2000-12-20 2010-03-10 カヤバ工業株式会社 切換弁
EP1370773B1 (fr) 2001-03-21 2005-06-22 Bucher Hydraulics GmbH Distributeur
DE10258517B3 (de) 2002-12-14 2004-06-03 Sauer-Danfoss (Nordborg) A/S Hydraulische Ventilanordnung
DE102005050169A1 (de) * 2005-06-21 2006-12-28 Bosch Rexroth Ag LS-Steueranordnung und LS-Wegeventil

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WO2009062572A1 (fr) 2009-05-22
JP2011503480A (ja) 2011-01-27
EP2220380A1 (fr) 2010-08-25
JP5462178B2 (ja) 2014-04-02
DK2220380T3 (da) 2013-02-04
DE102007054137A1 (de) 2009-05-28
US8464757B2 (en) 2013-06-18
US20100300552A1 (en) 2010-12-02

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