WO2007059898A1 - Soupape de commande hydraulique/pneumatique a fonction de securite integree - Google Patents

Soupape de commande hydraulique/pneumatique a fonction de securite integree Download PDF

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Publication number
WO2007059898A1
WO2007059898A1 PCT/EP2006/011046 EP2006011046W WO2007059898A1 WO 2007059898 A1 WO2007059898 A1 WO 2007059898A1 EP 2006011046 W EP2006011046 W EP 2006011046W WO 2007059898 A1 WO2007059898 A1 WO 2007059898A1
Authority
WO
WIPO (PCT)
Prior art keywords
control valve
connection point
connection
actuating element
spool
Prior art date
Application number
PCT/EP2006/011046
Other languages
German (de)
English (en)
Inventor
Harald Geis
Horst Rott
Original Assignee
Thomas Magnete 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 Thomas Magnete Gmbh filed Critical Thomas Magnete Gmbh
Priority to AT06818623T priority Critical patent/ATE523699T1/de
Priority to EP06818623A priority patent/EP1952032B1/fr
Publication of WO2007059898A1 publication Critical patent/WO2007059898A1/fr

Links

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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors

Definitions

  • the invention relates to a hydraulic / pneumatic control valve according to the features of the preamble of claim 1.
  • a generic control valve with fall-safe function is known from DE-A-103 08 910 and is used especially for control tasks in the field of mobile hydraulics.
  • the safety function is that in case of failure in any position in which the valve is moved by an actuator, a connected to the junction A hydraulic control element should be depressurized. This is realized in that a pressurized connection point P is connected to one or more further connection points T, which is connected to one or more containers, and thus relieves this connection.
  • the safety function is formed by a valve member into which a spool is integrated.
  • the slide has for this purpose a coaxial bore, which is designed as a relief channel, which is connected via a transverse channel and control recesses in the form of an annular groove on the circumference of the spool with the consumer connection point.
  • the end face of the spool formed by a plunger of an actuating element is open and opens into a control chamber.
  • the transverse bore is designed so that it is connected to the connection point for the consumer both in the first position in which the spool is not actuated, and in a second position, and in any intermediate position between the two positions in which it was actuated is.
  • DE 41 33 536 C2 shows another hydraulic solenoid valve with FaM-Safe function.
  • US 5,209,261 A shows a slide valve with fail-safe function with a through hole in the spool.
  • the seal between an actuating element and the through opening on the slide at this point is realized by a seat valve whose seat body closes the opening.
  • a back pressure spring By a back pressure spring, the opening of the slider is pressed against the closing body.
  • the present invention has for its object to achieve an improved sealing in a generic control valve, which prevents leakage losses and a pressure drop, in particular during normal operation.
  • the object is achieved in connection with the preamble by the characterizing part of claim 1.
  • the advantage of the invention is that no or only small leaks can occur at the point during a loading of a control slide by the actuating element by the positive and positive sealing at the head of the actuating element in normal operation, so that no pressure loss at the connection A occurs.
  • a pressure built up at the junction A is guided through the discharge channel in the spool to the head of the slide in the storage space and degraded by the line connection between the storage space and the connection point T to the tank connection.
  • valve spools with the same outer contour can be used for the valve as for valves that operate only in "normal" mode, and the only requirement for use with fail-safe valves is that they have a continuous coaxial bore as a relief channel exhibit.
  • the sealed head of the actuating element In the normal function of the sealed head of the actuating element is located directly on the control port of the spool.
  • the control opening of the slide is closed by the seal.
  • the normal function can be described by two positions. In a position of the slide designated as the first position, the pressurized connection P is connected directly to the working connection via the discharge channel. The drain to the tank connection is blocked. However, the storage space is permanently connected to the connection point T via a line connection. Due to the further sealed connection point of the control opening of the spool there is no pressure drop at the consumer A.
  • the pressure port P is locked.
  • the consumer A is now connected via the compensation channel in the spool valve via the tank connection T connected to the duct.
  • the sealing of the control port only has a sealing function which prevents excessive penetration of the fluid of the valve into the region of the actuating device.
  • the connection of the connection P with the tank connection is blocked by the axial slide position.
  • the control of the actuating element is terminated when, for example, the spool is blocked between the two position due to contamination or the like.
  • the spool is placed in a position where the head ends of spool and actuator are spaced apart. In this position, which is located between the first and the second position of the spool described above, the port T is blocked from the consumer port A of the valve, however, the connection from A to the pressure port P is still open, so that the port A is still is pressurized.
  • a relief of this pressurized connection point A is initially in conjunction with the designed as a coaxial bore in the spool discharge channel, the control port is now open and opens into a storage space.
  • This space has according to the invention a conductive connection to the connection point of the tank T, so that in this way always a pressure relief of the consumer point A is ensured.
  • the connection of the discharge channel via the storage space to the connection point T remains upright.
  • the seal can z. B. be realized by a mounted at the head end of the actuator plug or by a coating of the front page.
  • the shape of the seal can advantageously be done either as an elastomeric piston or cone.
  • the elastomeric material can occupy the entire radial surface.
  • the elastomer seal is enclosed in a mouth-like, axial recess of the head part of the actuating element and terminates flush with the head part in the radial direction.
  • the opening diameter of the mouth corresponds to the diameter of the control opening of the control slide, so that the seal is made by the embedded elastomer material.
  • the O - ring seal can be realized by a cylindrical pin arranged on the front side, on the outer circumference of which the O - rings are arranged.
  • the seal can also be designed as a flat surface of the front part of the actuating element.
  • the actuator is executed in this case at the junction as a full piston surface which seals the coaxial opening bore of the spool.
  • the head of the actuating element is designed in this embodiment as a brass cone, the tip of which penetrates into the open end face of the spool and seals this point.
  • the sealing ram can also be constructed in a further advantageous embodiment in the form of a sleeve whose outer sleeve bottom forms the sealing surface with respect to the bore of the spool.
  • a ball or other molded seat body is arranged loosely and is from the front side of the immersed in the sleeve opening head of the Betlochistselemen- held in your position.
  • the actuator abuts against the ball, which thus presses the outer sleeve bottom against the control hole.
  • Such a construction prevents tilting of the joint, so that a complete seal is always possible.
  • the line connection is arranged within the outer envelope of the valve and extends parallel to the discharge channel of the spool. If further connection points to the environment are provided, then of course this connection can also be routed to these locations. It is only crucial that a pressure relief of the storage space is guaranteed at open connection between spool and actuator.
  • the spool in the stowage on a restoring device which is suitably designed as a compression spring.
  • the head of the spool in the storage space has radial shoulders for this purpose.
  • One end of the compression spring is supported there while the other end presses against the bottom of the storage space facing away from the connection point.
  • a further advantageous embodiment of the invention comprises, in particular as an actuating device, an electromagnet whose armature with axially extended rod tappet forms the actuating element, at whose head the seal is arranged.
  • an electromagnet whose armature with axially extended rod tappet forms the actuating element, at whose head the seal is arranged.
  • a proportional solenoid is preferably used whose stroke / current characteristic corresponds to the axial displacement of the control spool.
  • the armature of the electromagnet is provided with an additional coaxial seal against its armature counterpart, at an axial distance to seal the connection point is arranged.
  • Fig. 1 shows in a longitudinal sectional view of a first embodiment of the inventive control valve in an overall view.
  • FIG. 2 shows a longitudinal section of a second embodiment of the inventive control valve in an overall view.
  • FIGS. 3 a to 3 c show longitudinal views of details of FIG. 1.
  • the hydraulic control valve shown in FIG. 1 is a 3/2-way proportional pressure reducing valve operating as a safety valve in fail-safe function, i. the pressure to be controlled is applied to the end face of a spool 3 of a valve member 17 of the control valve and counteracts a force generated by an actuator 2 of an actuator 1 and the counterforce generated by a restoring device 5.
  • the valve member 17, which occupies substantially the right side of Fig. 1, consists of a sleeve-like valve body 12 and has, at its left end face, a connection point marked A of a consumer, via a pressure line 4, which with a pressure connection P is connected, and with a working medium z. B hydraulic oil is supplied.
  • the consumer may be either the direct hydraulic control of a drive or work system or the control of pilot valves for such systems.
  • the valve body 12 has on its periphery a third connection point for a tank T.
  • the designed as a cylinder spool 3 has in its interior a coaxial discharge channel. 6 on, which extends axially over its entire length.
  • the fail-safe function of the valve shown in Fig. 1 is that in case of malfunction, the connection point A is to be relieved in any position of the spool, A must be connected to T, at the same time the connection should be interrupted from A to P.
  • valve member 17 shown in Fig. 1, it was a part of a cartridge-mounted cartridge in a designated location (Cavity).
  • On the outer circumference of the valve body 12 are each three O-ring seals can be seen.
  • Reference numeral 19 shows the O-ring seal between the actuator 2 and the atmospheric environment of the valve.
  • the two other O-ring seals 20, 21 are arranged. These separate the supply lines of the individual connections in the cavity from each other.
  • the entire axial length of the valve body 12 extending coaxial bore 30 of the spool 3 is mounted.
  • the bore 30 opens directly into the consumer connection point A.
  • the spool 3 has at its outer periphery in the axial region between the terminals P and T an axial recess 31, and connected to this recess radial Compound 32 which is connected to the coaxial discharge channel 6 in the interior of the spool 3.
  • This discharge channel 6 extends over the entire axial length of the spool 3 from the junction A to a junction 10 at the other end.
  • the valve body 17 has, at its end associated with the actuating device 2, a coaxial recess which forms a storage space 7, in which the restoring device acts against the force effect of the confirmation element 2.
  • the return device is arranged as a compression spring about the outer diameter of the spool 3 and presses with its axially left end against the bottom of the recess and with the other end against a shoulder of the head of the spool 3 in this area.
  • the discharge channel 6 of the spool 3 opens at this head end in a control opening 8. The opening is firmly closed in the illustrated position of the slider 3 at the junction 10 with the head of the actuating element 1.
  • the valve body 12 also has an axially arranged in the interior of the body line connection 34, through which a conductive connection of the storage space 7 with the tank connection T is made.
  • the connecting line 34 provides in the normal function for a venting or emptying of the fluid, which collects in the storage space or in the actuator 2 during operation. With the open position of the control opening 8 and open connection point P, the line 34 fulfills the function that the connection A receives a direct connection to the connection T and is thus relieved of load by this measure.
  • a discharge of the terminal A via the discharge channel 6, the radial connection 32 and the axial recess 31 to the tank port T is ensured in a functional failure of a consumer.
  • the connection P ie the pressure supply, is blocked.
  • FIG. 1 shows a cup-shaped electromagnet in the design as a proportional magnet.
  • the magnet parts 28 of the electromagnet are surrounded by a pot-like housing pot 29, on whose bottom of the pot a plug 22 is provided for the energization of a coil 25 arranged in a coil body 26.
  • the magnetic flux is closed via the winding 25, a non-magnetic material, designed as a hollow cylinder armature 14 and the characteristic influencing armature counterpart, which in the working stroke of the armature 14 as Cone 15 is designed, which tapers against the stroke direction.
  • the force generated by the magnetic field causes the armature 14 in the axial direction to the left stroke movement.
  • the armature 14 is guided via a bearing bush 24 in a sleeve 27 configured as a pot, which extends axially from the in the direction of the valve body 12 arranged end of the magnet member 28, along the outer circumference of the cone 15 and armature 14 extends and there fixedly connected to both the bobbin 26, and with the armature counterpart, and at its bottom of the pot the lifting direction opposite end face of the armature 14 comprises.
  • an additional O-ring seal 18 is additionally provided as a seal of the magnetic member 28 against ambient media.
  • the head of the tappet 13 has on its front side a seal 9 which closes the control opening 8 in the position of the control slide 3 shown in FIG.
  • the seal 9 comprises an elastomer material 11, which is arranged in a coaxial recess of the end face of the plunger 13. The elastomeric material 11 is pressed into the recess as a cone.
  • FIG. 2 differs only in the nature of the seal 9 from the embodiment in Fig. 1. Therefore, the same reference numerals are used in the following for the same functions as in Fig. 1.
  • the material pairing of plunger material (steel) and elastomeric material 11 (FIG. 1) is designed as an O-ring seal 33 in this embodiment.
  • the end face of the plunger head directed in the direction of the control opening 8 has a radial journal which is provided as a receptacle for the O-ring seal 33.
  • the sealing of the connection point 10 between the plunger and the control opening. 8 occurs outside circumference through the O - rings 33, while the power is transmitted to the spool 3 by the steel of the plunger 13.
  • FIG. 3a to FIG. 3c. 3a and 3b show the normal operation, both in a non-activated position of the actuator 2 - corresponding to the embodiments of Fig. 1 and Fig. 2 corresponds to this position of a de-energized electromagnet - as well as an activated by the actuator 2 position of the spool 3, ie the solenoid is energized and the spool 3 is moved axially in the direction of the lifting movement of the plunger 13 to the left.
  • the control opening 8 of the spool 3 is closed, the head of the actuating element 1 is applied to the opening.
  • the connection point 10 is positively and positively sealed.
  • connection point A for the consumer is relieved via the relief channel 6, the radial connection 32 and the axial recess 31 to the tank T.
  • the axial recess 31 of the spool 3 terminates at its right end in height of the tank port T and is connected thereto.
  • the radial connection 32 is axially away from the pressure line 4 of the pressure port P, so that it is closed.
  • About the radial connection 32 and the discharge channel 6 of the working port A is connected to the tank port T.
  • the connection for a working device or for a pilot valve of a drive is thus shut down.
  • the spool 3 is pressed by acting as restoring device 5 compression spring against the head of the actuating element 1.
  • the connection point 10 is closed.
  • the line connection 34 parallel to the spool 3 within the valve body 12 exerts no safety function in this slide position, but serves exclusively for the usual venting or draining for the fluid of the control valve, which has collected within the actuator 2 (solenoid).
  • Fig. 3b shows the spool 3 in an activated by the actuator 1 position (energized state of the electromagnet according to Fig. 1 or Fig. 2).
  • the slider 3 is moved to the stroke of the actuator 1 so far axially to the left until the radial connection 32 is above the connection point P, but at the same time the tank outlet T is closed.
  • the connection point 10 towards the actuating element 1 is still closed.
  • the connection point A is connected in line with the pressure line 4 and the port P.
  • line connection 34 again serves only the venting and / or emptying of the storage space 7 or the actuator 2 (solenoid).
  • the actuation (energization) of the actuating device 2 is interrupted.
  • the plunger 13 is moved axially to the left.
  • the spool 3 would follow by the return spring 5 of the rear stroke movement of the actuating element 1. If this subsequent movement of the slider 3 is disturbed, ie it is stuck in the position of Fig. 3b, for example by a chip, another object or generally by dirt particles, the working port - as shown in FIG. 3c - with the pressure port P still connected.
  • the pressurized medium accumulates in the storage space, but it can now flow through the conductive connection 34 of the storage space 7 to the tank outlet T. The working port A is thus relieved and the connected devices are shut down.
  • the invention has been explained using the example of a seal from an elastomeric membrane as a cone (FIG. 1) or as an O-ring seal 33 (FIG. 2). It also includes other forms of sealing, especially those in which the head of the plunger is made of the same material as that of the actuating element. This also includes sealing tappets with an associated seat body, which is confirmed directly or indirectly via an inner tappet.
  • the invention also relates to pneumatically operated valves.
  • the actuating device as an electromagnet, manually or electronically actuated or triggered switching devices as actuators to the disclosure of the invention.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Multiple-Way Valves (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne une soupape de commande hydraulique/pneumatique qui comprend un tiroir de commande (3) actionné par un élément d'actionnement (1) d'un dispositif d'actionnement (2), cet élément étant en équilibre dynamique avec la pression qui agit sur les surfaces frontales du tiroir (3). Dans une première position, une liaison est établie entre un point de raccordement P sollicité en pression et au moins un point de raccordement A pour un consommateur par l'intermédiaire d'un premier canal de décharge (6) ménagé dans le tiroir de commande (3). Dans une deuxième position, la liaison entre le point de raccordement A et le point de raccordement P est rompue et le consommateur A est déchargé au niveau d'un point de raccordement T dans un réservoir par l'intermédiaire du premier canal de décharge (6). Ledit canal de décharge (6) est relié au point de raccordement A et au point de raccordement T et il est guidé jusqu'à un point de liaison (10) du tiroir de commande (3) avec l'élément d'actionnement (1), ce point de liaison (10) se présentant sous la forme d'une ouverture de commande (8) dans une chambre d'accumulation (7) de la soupape de commande, et la liaison du canal de décharge (6) au point de raccordement T peut être commandée par le dispositif d'actionnement (2). Une liaison de force et de forme est établie entre le tiroir de commande (3) et l'élément d'actionnement du tiroir de commande sous la forme d'un joint coaxial. En cas de dysfonctionnement de la soupape de commande, une fonction de sécurité décharge sur le point de raccordement T le point de raccordement A du consommateur au repos indépendamment de la position du tiroir de commande (3). La décharge du point de raccordement A est effectuée vers le réservoir (point de raccordement T) par l'intermédiaire du joint (9) ouvert et de la chambre d'accumulation (7). L'invention est caractérisée en ce que le joint (9) coaxial est disposé sur le côté de l'élément d'actionnement (1) tourné vers le point de liaison (10).
PCT/EP2006/011046 2005-11-24 2006-11-17 Soupape de commande hydraulique/pneumatique a fonction de securite integree WO2007059898A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AT06818623T ATE523699T1 (de) 2005-11-24 2006-11-17 Hydraulisches/pneumatisches steuerventil mit fail-safe funktion
EP06818623A EP1952032B1 (fr) 2005-11-24 2006-11-17 Soupape de commande hydraulique/pneumatique a fonction de securite integree

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005056039A DE102005056039B4 (de) 2005-11-24 2005-11-24 Hydraulisches / pneumatisches Steuerventil mit Fail-Safe Funktion
DE102005056039.3 2005-11-24

Publications (1)

Publication Number Publication Date
WO2007059898A1 true WO2007059898A1 (fr) 2007-05-31

Family

ID=37685621

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/011046 WO2007059898A1 (fr) 2005-11-24 2006-11-17 Soupape de commande hydraulique/pneumatique a fonction de securite integree

Country Status (4)

Country Link
EP (1) EP1952032B1 (fr)
AT (1) ATE523699T1 (fr)
DE (1) DE102005056039B4 (fr)
WO (1) WO2007059898A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2025885A2 (fr) * 2007-08-09 2009-02-18 Delphi Technologies, Inc. Soupape de contrôle d'huile pour déphaseur à came variable
WO2018074952A1 (fr) * 2016-10-18 2018-04-26 Parker Hannifin Emea S.A.R.L. Système de commande électro-hydraulique avec vannes pilotes à sécurité intégrée

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013014452A1 (de) 2013-08-30 2015-03-05 Hydac Fluidtechnik Gmbh Ventilvorrichtung
WO2021007424A1 (fr) 2019-07-10 2021-01-14 Fema Corporation Of Michigan Système de direction à soupape de réaction de charge commutable
DE102020118902A1 (de) 2020-06-26 2021-12-30 Fema Corporation Of Michigan Proportionales hydraulisches Zweistufenventil
US11473693B2 (en) 2020-06-26 2022-10-18 Fema Corporation Of Michigan Proportional hydraulic two-stage valve

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3797526A (en) * 1972-08-21 1974-03-19 E Champeon Cage valve with pilot and mechanical operating means
US5085402A (en) * 1990-08-10 1992-02-04 The Lee Company High speed solenoid valve actuator
EP1103992A1 (fr) * 1999-11-24 2001-05-30 Parker Hannifin Rak S.A. Electrovanne miniature, procédés de son montage
DE10308910A1 (de) * 2003-02-28 2004-09-09 Linde Ag Hydraulisches Steuerventil
EP1589392A1 (fr) * 2004-04-24 2005-10-26 THOMAS MAGNETE GmbH Vanne de régulation de pression

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4123036C2 (de) * 1991-07-12 1994-08-11 Daimler Benz Ag Schieberventil
DE4133536C2 (de) * 1991-10-10 1995-11-30 Hydraulik Ring Gmbh Hydraulikmagnetventil

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3797526A (en) * 1972-08-21 1974-03-19 E Champeon Cage valve with pilot and mechanical operating means
US5085402A (en) * 1990-08-10 1992-02-04 The Lee Company High speed solenoid valve actuator
EP1103992A1 (fr) * 1999-11-24 2001-05-30 Parker Hannifin Rak S.A. Electrovanne miniature, procédés de son montage
DE10308910A1 (de) * 2003-02-28 2004-09-09 Linde Ag Hydraulisches Steuerventil
EP1589392A1 (fr) * 2004-04-24 2005-10-26 THOMAS MAGNETE GmbH Vanne de régulation de pression

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2025885A2 (fr) * 2007-08-09 2009-02-18 Delphi Technologies, Inc. Soupape de contrôle d'huile pour déphaseur à came variable
EP2025885A3 (fr) * 2007-08-09 2009-04-15 Delphi Technologies, Inc. Soupape de contrôle d'huile pour déphaseur à came variable
WO2018074952A1 (fr) * 2016-10-18 2018-04-26 Parker Hannifin Emea S.A.R.L. Système de commande électro-hydraulique avec vannes pilotes à sécurité intégrée
EP3529130A4 (fr) * 2016-10-18 2020-06-24 Parker Hannifin Emea S.A.R.L. Système de commande électro-hydraulique avec vannes pilotes à sécurité intégrée
US11125254B2 (en) 2016-10-18 2021-09-21 Parker Hannifin Emea S.À.R.L. Electro-hydraulic control system with fail-safe pilot valves

Also Published As

Publication number Publication date
DE102005056039A1 (de) 2007-06-06
DE102005056039B4 (de) 2009-01-29
ATE523699T1 (de) 2011-09-15
EP1952032B1 (fr) 2011-09-07
EP1952032A1 (fr) 2008-08-06

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