EP3114355B1 - Dispositif à soupape - Google Patents

Dispositif à soupape Download PDF

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Publication number
EP3114355B1
EP3114355B1 EP15703877.9A EP15703877A EP3114355B1 EP 3114355 B1 EP3114355 B1 EP 3114355B1 EP 15703877 A EP15703877 A EP 15703877A EP 3114355 B1 EP3114355 B1 EP 3114355B1
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EP
European Patent Office
Prior art keywords
valve
pressure
control
valve slide
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.)
Active
Application number
EP15703877.9A
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German (de)
English (en)
Other versions
EP3114355A1 (fr
Inventor
Sascha Alexander Biwersi
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 Systems and Services GmbH
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Hydac Systems and Services GmbH
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Publication date
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Publication of EP3114355A1 publication Critical patent/EP3114355A1/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
    • 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
    • F15B13/025—Pressure reducing valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B13/026—Pressure compensating valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • F15B20/007—Overload
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve

Definitions

  • the invention relates to a valve device for influencing a media flow between a supply connection to which a pressure supply source can be connected and a pressure connection to which a hydraulic consumer can be connected, with the features in the preamble of claim 1.
  • valve devices are freely available on the market in the form of pressure compensators, flow control valves or pressure reducing valves. These valves have the task of regulating a constant pressure difference that is independent of an inlet pressure. If this pressure difference is also present via a metering orifice, the overall function is referred to as a volume flow controller.
  • a pressure compensator has a valve slide that can be displaced in a housing.
  • the pressure compensator regulates a volume flow between a supply connection and a pressure connection.
  • the valve slide has a control edge which interacts with the valve housing.
  • the pressure present at the supply connection is copied to one control side of the valve slide, while the opposite control side is acted upon by the fluid pressure present at the pressure connection and possibly an energy store.
  • a pressure compensator also possible without a compression spring; all that is required for this is a specifiable area ratio, as is the case, for example, with the use of a stepped piston.
  • the valve slide moves as long as there is a pressure difference between the control sides.
  • the DE 10 2012 014 359 A1 describes a generic valve device for influencing a media flow between a supply connection, to which a pressure supply source can be connected, and a pressure connection, to which a hydraulic consumer can be connected, with a valve device which has a valve slide which is guided in a valve housing so that it can move longitudinally between end positions, wherein, by means of a control device, the pressure regulated by the valve slide at the pressure connection is limited from a predetermined displacement of the valve slide in the direction of one of its end positions, wherein A control line opens into the valve housing, which is part of an LS signal line, a tank connection or another return connection which essentially has ambient pressure.
  • valve devices go from US 2013/0061955 A1 , the U.S. 5,778,929 , the US 2010/0084589 A1 and the WO 2013/090458 A1 emerged.
  • the invention is therefore based on the object of showing a valve device which no longer allows pressure fluctuations at the supply connection to pass unhindered and thus offers protection for a connected hydraulic consumer.
  • valve device with the features of claim 1.
  • Advantageous embodiments of this valve device emerge from the dependent claims 2 to 9.
  • the valve device according to the invention is characterized in that a fluid coming from the supply connection flows off via the control line after the predetermined displacement of the valve slide.
  • the draining of the fluid relieves the pressure, which causes the valve slide to move in the direction of its closed position until a new equilibrium of the pressures is established on its control sides. In this way, the movement of the valve slide is advantageously accelerated.
  • the pressure at the pressure connection regulated by the valve slide is actually limited from a predetermined displacement of the valve slide in the direction of one of its end positions.
  • the maximum pressure at the pressure connection is advantageously limited.
  • the hydraulic consumer can no longer be overloaded.
  • the fluid pressure at the pressure connection has a constant pressure difference to the supply connection until a permissible maximum pressure is reached. Any "ghost movements" of the valve slide are also avoided by this pressure-limited valve device.
  • a control line opens into the valve housing, which is part of an LS signal line, a tank connection or some other return connection which essentially has ambient pressure.
  • the control device can have a control channel within the valve slide, which runs out on a control side of the valve slide into a media chamber within the valve housing and which connects this media chamber with a further media chamber within the valve housing to which the control line is connected, from the predetermined displacement of the valve slide .
  • the media chambers can be pressure chambers that apply fluid pressure to the control sides of the valve slide. If the valve slide is displaced by a predetermined displacement from its one end position, the closed position, pressure equalization takes place between the media chambers. Due to this pressure equalization alone, there is already a return movement of the valve piston and thus a reduction or limitation of the fluid pressure at the pressure connection.
  • the control channel in the valve slide advantageously merges with the control line from a longitudinal channel, which runs parallel to the direction of travel of the valve slide, into a transverse channel, which remains covered by the valve housing until the fluid-carrying connection between one media chamber and the other media chamber is made.
  • a control edge which interacts with the transverse channel can be formed in the valve housing. Only when the transverse channel passes over the control edge does a fluid-carrying connection occur between the media chambers.
  • a simple, easy to manufacture and space-saving way is shown to establish a fluid-carrying connection between the media chambers as a function of the displacement of the valve slide.
  • a pressure signaling channel can open into the control channel, which forwards the pressure regulated by the valve slide between the supply connection and the pressure connection into the control channel.
  • the fluid pressure present at the supply connection can thus be copied to one control side of the valve slide in a simple manner without having to provide additional bores in the valve housing.
  • fluid can flow away from the supply connection in the direction of the control line via the pressure signaling channel.
  • the pressure signaling channel advantageously ends in a valve chamber of the valve housing which is laterally bounded by two control parts of the valve slide.
  • the fluid flow with the supply connection and the pressure connection is advantageously regulated by the control parts.
  • the control channel advantageously has a diaphragm or a throttle point, which is provided between the supply connection and the control side of the valve slide which is adjacent to the one media chamber.
  • the control behavior of the valve device can advantageously be influenced, in particular delayed, with the orifice or the throttle point. In this way, for example, pressure surges at the supply connection can no longer be mapped directly to one control side of the valve slide, so that a sudden opening of the valve device is prevented, which could lead to damage to the hydraulic consumer.
  • a device in a fluid-carrying line between the pressure connection and the hydraulic consumer, a device can be provided and the LS signal line can open into the fluid-carrying connection between the device and the hydraulic consumer.
  • This has the advantage that there is a low pressure in the further media chamber to which the control line is connected. In this way, the fluid can more easily flow out of the further control chamber via the control line when the valve slide is displaced beyond the predetermined displacement.
  • the valve device is preferably an individual pressure compensator and the device is a metering orifice. This combination advantageously creates a volume flow controller.
  • valve slide can separate the pressure connection from the supply connection in at least one of the end positions under the action of an energy store, preferably in the form of a compression spring.
  • a pressure compensator 10 in connection with a metering orifice 12 is shown in the form of a hydraulic symbol representation and in the form of a longitudinal section, which form a volume flow regulator 14 in the overall function.
  • This volume flow regulator 14 forms the starting point the description for the following based on the Figures 3 and 4 explained valve device 16 according to the invention.
  • valve housing 18 has a valve bore 20 in which a valve slide 22 which is guided so as to be longitudinally displaceable is arranged.
  • the valve bore 20 is closed at both ends 24, 26 by end screws 28, 30 which each engage in an assignable internal thread 32 of the valve bore 20.
  • Annular sealing elements 34 are provided between the end screws 28, 30 and the valve housing 18.
  • the valve slide 22 is provided for controlling a fluid-carrying connection 36 between at least two fluid connection points 38, 40 accommodated in the valve housing 18, a supply connection 38 and a pressure connection 40.
  • a pressure supply source P can be connected to the supply connection 38 and a hydraulic consumer U can be connected to the pressure connection 40.
  • the valve slide 22 has a total of two control parts 42, 44, of which the first control part 42 has at least one pocket-like recess 46 and the second control part 44 is arranged at a distance from the first control part 42 by a first fluid guide 48.
  • the first control part 42 has at least one pocket-like recess 46 and the second control part 44 is arranged at a distance from the first control part 42 by a first fluid guide 48.
  • the control part 42 In principle, there is also the possibility of implementing the solution according to the invention with just one control part, for example the control part 42. In the non-actuated state of the valve slide 22, i.e.
  • the second control part 44 is in contact with a housing inner wall 52 of the valve housing 18 by means of a cylindrical guide part 50.
  • a conical transition part 54 forms a flow guide for the fluid flowing through the fluid guide 48 and causes the fluid flow to be deflected in the direction of the pressure connection 40.
  • the transition part 54 also contributes to the flow force compensation on the valve slide.
  • valve slide 22 is guided in the area of the pressure connection 40 in the valve housing 18 through its inner wall 52.
  • a first fluid guide 48 keeping them at a distance.
  • a second fluid guide 58 between the second control part 44 and the further guide part 56 now improves the flow around the valve slide 22 in the region of the second control part 44, as a result of which the pressure losses within the pressure compensator 10 are reduced.
  • the sealing behavior of the second control part 44 with respect to the housing inner wall 52 is improved by the second fluid guide 58, since the sealing gap between the valve slide 22 and the housing inner wall 52 can be reduced by introducing the second fluid guide 58 into the valve slide 22.
  • the two fluid guides 48, 58 which form axial spacings between the first control part 42 and the second control part 44 and between the second control part 44 and the further guide part 56, are formed by diameter reductions 59 in the valve slide 22 that run like a groove. Such diameter reductions 59 are also referred to technically as grooves.
  • valve slide 22 On its one end face 60, on the left in the plane of the figure, the valve slide 22 adjoins a media chamber 62 of variable volume, into which a control channel 64 of the valve slide 22 opens at its one end 66, the other end 68 of which via two transverse pressure reporting channels 70 in one Valve space 72 between the two control parts 42, 44, directly adjoining the transition part 54, opens out.
  • the valve chamber 72 is delimited at the edge by the two control parts 42, 44 of the valve slide 22 and the valve housing 18.
  • the pressure regulated by the valve slide 22 between the supply connection 38 and the pressure connection 40 is transmitted via the pressure reporting channels 70 and the Control channel 64 forwarded into a media chamber 62.
  • the fluid pressure prevailing in one media chamber 62 then acts on valve slide 22 in the direction of an open position.
  • the hydraulic consumer U is connected to the pressure connection 40 via a fluid-carrying line 73.
  • the device 12 is provided, in particular in the form of a metering orifice.
  • a corresponding control line 76 in the form of an LS signal line 78 is provided, which is connected to the valve housing 18 and to another Media chamber 80 leads.
  • a fluid pressure prevailing in the further media chamber 80 acts on the other end face 74 of the valve slide 22 to the left in the direction of the closed position SS, in which the valve slide 22 separates the pressure connection 34 from the supply connection 40 at zero stroke.
  • the valve slide 22 is also acted upon on its other end face 74 by an energy store 82 in the form of a compression spring.
  • Guides 84, 86 for the compression spring 82 are formed on the valve slide 22 and on the opposite end screw 30.
  • valve device 16 of Figures 3 and 4 represents a further development and differs from the volume flow controller 14 of Figures 1 and 2 Essentially in that in a valve device 88 in the form of an individual pressure compensator by means of a control device 90 the pressure between the supply connection 38 and the pressure connection 40 is regulated by the valve slide 22 from a predetermined displacement V of the valve slide 22 in the direction of one of its end positions, in this case the right end position in the image plane can be limited.
  • control device 90 has an extended control channel 64 within the valve slide 22, which opens out on one control side 60 of the valve slide 22 into the one media chamber 62 within the valve housing 18.
  • the control channel 64 connects the one media chamber 62 with the further media chamber 80 within the valve housing 18, to which the control line 76 is connected, in a fluid-conducting manner from the predetermined displacement V of the valve slide 22.
  • the control channel 64 merges in the direction of the further media chamber 80 with the control line 76 from a longitudinal channel 94, which runs parallel to the direction of travel VR of the valve slide 22, into a transverse channel 96.
  • the transverse channel 96 remains covered by the valve housing 18 until the fluid-carrying connection 98 between the one media chamber 62 and the further media chamber 80 is established.
  • an inner circumferential groove 100 which has a control edge 102, is provided in the valve housing 18.
  • the fluid can flow around the end of the further guide part 56 through the inner circumferential groove 100.
  • the fluid can flow out of the further media chamber 80 via the control line 76 in the direction of the LS signal line 78, a tank connection 104 or another return connection having essentially ambient pressure.
  • the LS signal line 78 and the tank connection 104 have adjustable throttle points 106, 108.
  • the control channel 64 in the valve slide 22 has a further throttle point 110 which is provided between the supply connection 38 and the control side 60 of the valve slide 22 which is adjacent to the one media chamber 62.
  • This throttle point 110 is designed very simply in that the pressure reporting channels 70 have a correspondingly small inner diameter. Through this throttle point 110, pressure fluctuations at the supply connection 38 are forwarded to the first media chamber 62 with a delay.
  • valve device 16 The functioning of the valve device 16 is explained below.
  • a fluid pressure present at the supply connection 38 is passed on via the pressure signaling channels 70 and the control channel 64 into the one media chamber 62. There it acts on the adjacent control side 60 of the valve slide 22. On the opposite control side 74, the valve slide 22 is acted upon by the load pressure via the LS signal line 78 and the compression spring 82. When the fluid pressure at the supply connection 38 exceeds the counter pressure due to the load pressure and the compression spring 82, the valve slide 22 moves, starting from the closed position SS with zero lift, to the right in the plane of the drawing.
  • the second control part 44 is disengaged from the housing inner wall 52, so that a fluid-carrying connection 36 between the supply connection 38 and the pressure connection 40 is increasingly opened.
  • the fluid-carrying connection 48 is interrupted by closing the control part 42 on the control edge 51 and the fluid-carrying connection 36 is established between the media chambers 62, 80 because the transverse channel 96 of the control device 90 overflows the control edge 102 in the valve housing 18 Has.
  • This fluid-carrying connection 98 between the media chambers 62, 80 results in a pressure equalization between the media chambers 62, 80.
  • the valve slide 22 is therefore shifted again to the left in the direction of the closed position SS as long as the pressure equalization exists.
  • This effect is reinforced by the fact that fluid can flow out of the further media chamber 80 via the control line 76 in the direction of the LS signal line 78 and the tank connection 104. If the valve slide has moved sufficiently far in the direction of the closed position SS, at least a partial overlap occurs again Transverse channel 96 through the valve housing 18, whereby the fluid-carrying connection 98 between the media chambers 62, 80 is initially throttled and is completely separated as the valve slide 22 is displaced. In this way, an equilibrium position is established which advantageously limits the pressure at the pressure connection 40 to a maximum value. This means that the hydraulic consumer U can no longer be overloaded.
  • the fluid pressure at the pressure connection 40 advantageously has a constant pressure difference to the supply connection 38 until the maximum permissible pressure is reached.
  • valve device 16 which advantageously no longer allows pressure fluctuations at the supply connection 38 to pass unhindered and thus effectively prevents any damage to the hydraulic consumer U.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Safety Valves (AREA)

Claims (9)

  1. Système à soupape pour influencer un courant de fluide entre un raccord (38) d'alimentation, auquel une source (P) d'alimentation en pression peut être raccordée, et un raccord (40) de pression, auquel un consommateur (U) hydraulique peut être raccordé, comprenant un dispositif (88) à soupape, qui a un tiroir (22) de soupape, guidé avec possibilité de se déplacer longitudinalement entre deux positions (SS) d'extrémité dans un corps (18) de soupape, dans lequel, au moyen d'un dispositif (90) de commande, la pression réglée par le tiroir (22) de la soupape au raccord (40) de pression peut, à partir d'un coulissement (V) donné à l'avance du tiroir (22) de soupape, être limitée en direction de l'une de ses positions d'extrémité, dans lequel débouche, dans le corps (18) de la soupape, une ligne (76) de commande, qui est une partie constitutive d'une ligne (78) de signal LS, d'un raccord (104) de réservoir ou d'un autre raccord de retour, ayant sensiblement la pression ambiante, caractérisé en ce qu'un fluide, venant du raccord (38) d'alimentation, s'écoule par la ligne (76) de commande, à partir du coulissement (V) donné à l'avance du tiroir (22) de la soupape.
  2. Système à soupape suivant la revendication 1, caractérisé en ce que le dispositif (90) de commande a, dans le tiroir (22) de la soupape, un canal (64) de commande, qui débouche, d'un côté (60) de commande du tiroir de la soupape, dans une chambre (62) de fluide dans le corps (18) de la soupape et qui met en communication fluidique, à partir du coulissement (V) donné à l'avance du tiroir (22) de la soupape, cette chambre (62) de fluide avec une autre chambre (80) de fluide dans le corps (18) de la soupape, chambre (80) à laquelle est raccordé la ligne (76) de commande.
  3. Système à soupape suivant la revendication 2, caractérisé en ce que le canal (64) de commande se transforme, dans la direction de l'autre chambre (80) de fluide ayant la ligne (76) de commande, d'un canal (94) longitudinal, qui s'étend parallèlement à la direction (VR) de déplacement du tiroir (22) de la soupape, en un canal (96) transversal, qui reste recouvert par le corps (18) de la soupape, jusqu'à ce que la communication (98) fluidique, entre la une chambre (62) de fluide et l'autre chambre (80) de fluide, soit produite.
  4. Système à soupape suivant la revendication 2 ou 3, caractérisé en ce que, dans le canal (64) de commande, débouche un canal (70) d'annonce de pression, qui achemine, dans le canal (64) de commande, la pression du raccord (40) de pression réglée par le tiroir (22) de la soupape.
  5. Système à soupape suivant la revendication 4, caractérisé en ce que le canal (70) d'annonce de pression débouche dans un espace (72) de soupape du corps (18) de la soupape, qui est délimité, du côté du bord, par au moins une partie (42) de commande, de préférence par deux parties (42, 44) de commande du tiroir (22) de la soupape.
  6. Système à soupape suivant l'une des revendications 2 à 5, caractérisé en ce que le canal (64) de commande a un diaphragme ou un point (110) d'étranglement, qui est prévu entre le raccord (38) d'alimentation et le côté (60) de commande du tiroir (22) la soupape voisin de la une chambre (62) de fluide.
  7. Système à soupape suivant l'une des revendications 1 à 6, caractérisé en ce qu'il est prévu un dispositif (12) dans un conduit (73) fluidique entre le raccord (40) de pression et le consommateur (U) hydraulique, et en ce que la ligne (78) de signal LS débouche dans le conduit (71) fluidique entre le dispositif (12) et le consommateur (U) hydraulique.
  8. Système à soupape suivant la revendication (7), caractérisé en ce que le système (88) à soupape est une balance manométrique individuelle et le dispositif (12), un diaphragme de dosage.
  9. Système à soupape suivant l'une des revendications précédentes, caractérisé en ce que le tiroir (22) de la soupape sépare, sous l'action d'un accumulateur (82) d'énergie, de préférence sous la forme d'un ressort de compression, dans au moins l'une de ses positions d'extrémité, le raccord (40) de pression du raccord (38) d'alimentation.
EP15703877.9A 2014-03-01 2015-02-07 Dispositif à soupape Active EP3114355B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014003086.5A DE102014003086A1 (de) 2014-03-01 2014-03-01 Ventilvorrichtung
PCT/EP2015/000253 WO2015131973A1 (fr) 2014-03-01 2015-02-07 Dispositif à soupape

Publications (2)

Publication Number Publication Date
EP3114355A1 EP3114355A1 (fr) 2017-01-11
EP3114355B1 true EP3114355B1 (fr) 2021-01-06

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ID=52468967

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15703877.9A Active EP3114355B1 (fr) 2014-03-01 2015-02-07 Dispositif à soupape

Country Status (4)

Country Link
EP (1) EP3114355B1 (fr)
CN (1) CN206071985U (fr)
DE (1) DE102014003086A1 (fr)
WO (1) WO2015131973A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016007754A1 (de) 2016-06-24 2018-01-11 Hydac System Gmbh Ventilvorrichtung zum Beeinflussen eines Medienstromes
CN111255761B (zh) * 2020-01-19 2022-04-05 宁波宇洲液压设备有限公司 液控换向减压阀
CN112555214B (zh) * 2020-12-10 2021-07-23 山东泰丰智能控制股份有限公司 一种三端口二通定压差阀

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3531758B2 (ja) * 1994-06-27 2004-05-31 株式会社小松製作所 圧力補償弁を備えた方向制御弁装置
DE102008026926A1 (de) * 2008-06-05 2009-12-17 Hydac Electronic Gmbh Stromteilervorrichtung und Versorgungseinrichtung unter Einsatz einer dahingehenden Stromteilervorrichtung
DE102008042624A1 (de) * 2008-10-06 2010-04-08 Robert Bosch Gmbh Schieberventil zur hydraulischen Steuerung in einem Kraftfahrzeug-Automatikgetriebe
WO2011115647A1 (fr) * 2010-03-17 2011-09-22 Parker Hannifin Corporation Soupape à commande hydraulique comprenant un limiteur de pression
WO2013090458A1 (fr) * 2011-12-12 2013-06-20 Parker-Hannifin Corporation Soupape de réduction de pression comportant un relâchement de pression
DE102012014359A1 (de) * 2012-07-19 2014-01-23 Hydac Filtertechnik Gmbh Ventilvorrichtung und Ventilanordnung bestehend aus dahingehenden Ventilvorrichtungen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
WO2015131973A1 (fr) 2015-09-11
CN206071985U (zh) 2017-04-05
DE102014003086A1 (de) 2015-09-03
EP3114355A1 (fr) 2017-01-11

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