EP0565982A1 - Agencement de soupape - Google Patents

Agencement de soupape Download PDF

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Publication number
EP0565982A1
EP0565982A1 EP19930105594 EP93105594A EP0565982A1 EP 0565982 A1 EP0565982 A1 EP 0565982A1 EP 19930105594 EP19930105594 EP 19930105594 EP 93105594 A EP93105594 A EP 93105594A EP 0565982 A1 EP0565982 A1 EP 0565982A1
Authority
EP
European Patent Office
Prior art keywords
valve
valve arrangement
bore
arrangement according
piston
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.)
Granted
Application number
EP19930105594
Other languages
German (de)
English (en)
Other versions
EP0565982B1 (fr
Inventor
Dieter Tischer
Bernd Niethammer
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.)
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hilite Germany GmbH
Original Assignee
HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Hydraulik Ring 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 HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH, Hydraulik Ring GmbH filed Critical HYDRAULIK-RING ANTRIEBS- und STEUERUNGSTECHNIK GmbH
Publication of EP0565982A1 publication Critical patent/EP0565982A1/fr
Application granted granted Critical
Publication of EP0565982B1 publication Critical patent/EP0565982B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • F15B13/0442—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 with proportional solenoid allowing stable intermediate positions
    • 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
    • Y10T137/86702—With internal flow passage
    • 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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—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
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87233—Biased exhaust valve
    • Y10T137/87241—Biased closed

Definitions

  • the invention relates to a valve arrangement according to the preamble of claim 1.
  • Such a valve arrangement is known, for example, to actuate cylinders operating in push-pull mode.
  • the cylinder selection with fluid supply or fluid discharge is made via the solenoid-operated directional valve.
  • the infeed movement is carried out by applying the fluid flow to the full cylinder surface.
  • the return movement of the switching piston is carried out by the load or a return spring.
  • the cylinders can generate a force that corresponds to the product of the full cylinder surface and system pressure.
  • a pressure relief valve is provided on the pump side, with which the pressure of one cylinder can be adjusted. Should the other cylinder be with another one, can.
  • the invention has for its object to design the generic valve assembly so that a pressure limitation can be achieved inexpensively with minimal parts and without additional volume.
  • the pressure valve is accommodated within the construction volume of the directional valve. Due to a slight modification of the switching piston of the directional control valve and installation of the valve member as the only additional component, the additional pressure valve and its system connection required in the known valve arrangement are eliminated.
  • the valve arrangement according to the invention fulfills the requirements that are placed on such a mass product, namely a small construction volume, a small number of components, low susceptibility to malfunction and extremely inexpensive production.
  • the directional control valve 1 has a directional control valve 1 which is attached to a connecting plate 2.
  • the directional control valve 1 has a switching piston 3, which is mounted axially displaceably in a bore 4.
  • the switching piston 3 has control edges 5 to 10.
  • connection plate 2 is provided with a working connection A, a working connection B, a pressure connection P and a return T to the tank in a known manner.
  • a cylinder 12 and 13 is connected to the working ports A and B, respectively.
  • these two cylinders 12, 13 work in push-pull. They each have a piston 14, 15, each of which is acted upon by hydraulic medium.
  • the piston rod 16, 17 carrying the piston 14, 15 is under the force of a compression spring 18, 19 which loads the piston rod 16, 17 in the direction of its retracted position. With the hydraulic medium, the corresponding piston 14, 15 is thus counter to the force of this return spring 18, 19 postponed.
  • a magnet 20 is connected to the directional control valve 1, the magnet plunger 21 of which cooperates with the adjacent end of the switching piston 3. If the magnet 20 is switched on, then the magnetic plunger 21 is extended in a known manner, so that it axially moves the switching piston 3 against the force of a return spring 22 into the desired switching position.
  • the return spring 22 is provided at the other end of the switching piston 3 and is supported at one end on a cover 23 which is screwed onto the housing of the directional control valve 1 and covers the bore 4 to the outside. With its other end, the return spring 22 is supported on a spring plate 24 which is seated on an additional piston 25 which projects axially displaceably into an axial bore 26 of the switching piston 3.
  • the bore 26 is guided to approximately half the length of the switching piston 3 and opens into a diametral bore 27 which passes through the switching piston 3 in the area between the control edges 8 and 9.
  • the bore 26 is crossed by a further diametral bore 28 which passes through the switching piston 3 in the area between the edge 11 and the adjacent switching piston end.
  • the directional control valve 1 has a relief bore 29 lying parallel to the switching piston 3, into which the tank connection T opens.
  • the relief bore 29 extends between two spaces 30 and 31. In the space 31, which is delimited at one end by the cover 23, there is the spring plate 24.
  • connection plate 2 has bores 32 to 35 which are connected to the corresponding connections A, B, P and T and to which corresponding bores 36 to 39 of the directional control valve 1 are connected.
  • the holes 36 and 38 of the directional control valve 1 assigned to the working connections A and B each open into an annular space 40 and 41 of the bore 4.
  • annular space 42 In the area between the two annular spaces 40 and 41 there is an annular space 42 with a smaller diameter in which the pressure connection P associated hole 37 opens.
  • the bore 39 assigned to the tank connection T finally opens into an annular space 43 in the bore 4, which has the same diameter as the annular space 42.
  • the cylinder 13 In the position shown in Fig. 1, the cylinder 13 is relieved, that is, its compression spring 19 has pushed the piston rod 17 into its initial position.
  • the other cylinder 12 is under the pressure of the hydraulic medium, so that its piston 14 is pushed back against the force of the spring 18.
  • the magnet 20 If the other cylinder 13 is now to be pressurized, the magnet 20 is actuated so that the magnet plunger 21 is axially displaced against the switching piston 3 in a known manner.
  • the magnetic plunger or armature 20 has performed its preliminary stroke VH, it comes to rest on the free end of the switching piston 3 and moves it during the subsequent working stroke into a switching position in which the hydraulic medium can flow to the cylinder 13.
  • the hydraulic medium flows via the pressure connection P and the bores 33 and 37 into the annular space 42.
  • the switching piston 3 is then displaced to the right in FIG. 1, that the control edge 7 closes the access of the hydraulic medium to the annular space 40, while the control edge 8 clears the way for the hydraulic medium to the annular space 41.
  • the hydraulic medium can pass from the annular space 42 into the annular space 41 and from there via the bores 38 and 34 to the working connection B.
  • the piston 15 is then moved by the hydraulic medium against the force of the spring 19.
  • the other cylinder 12 is now relieved, so that the spring 18 can move the piston 14 in FIG. 1 to the right into its end position.
  • the hydraulic medium When the cylinder 13 is pressurized, the hydraulic medium also enters the diametral bore 27 of the switching piston 3. This diametral bore 27 is arranged such that it is still in the region of the annular space 41. The hydraulic medium thus flows via this diametral bore 27 also into the axial bore 26 of the switching piston 3.
  • the additional piston 25 mounted in it is thus under the pressure of the hydraulic medium and the force exerted by the magnetic tappet 21, which counteracts the force of the return spring 22.
  • the magnetic plunger 21 moves against an end stop (not shown). Then the magnetic force has its greatest value.
  • the pressure acting on the additional piston 25 becomes greater than the restoring force, so that it is displaced against the force of the restoring spring 22 (stroke 47).
  • the additional piston 25 thus releases the diametral bore 28 of the switching piston 3, so that the hydraulic medium can now flow through the bore 26 and the diametral bore 28 into the space 31 and from there via the relief bore 29 to the bore 39, which connects to the tank connection T of the connecting plate 2 is connected.
  • the additional piston 25 thus forms in connection with the diametral bore 28 a pressure relief valve 67 which limits an impermissibly high pressure build-up.
  • This pressure relief valve 67 is housed within the switching piston 3, so that it has no additional space requirement.
  • an additional intermediate plate device is not required, as is provided in the known valve arrangement.
  • the magnet 20 is switched off, so that the magnetic plunger 21 is moved back into its starting position under the force of a return spring (not shown) or the return spring 22.
  • the return spring 22 pushes the additional piston 25 back into the in via the spring plate 24 Figure 1 shown locking position back, in which the additional piston closes the diametral bore 28.
  • the spring plate 24 comes into contact with the switching piston 3, it is moved again into the other switching position shown in FIG. 1 under the force of the return spring 22. Now the connection from the pressure port P to the working port B of the cylinder 13 is closed, while the annular space 40 is in communication with the annular space 42.
  • the hydraulic medium can therefore pass from the pressure connection P via these annular spaces into the bores 36 and 32 and thus to the working connection A of the cylinder 12. Its piston 14 is then moved by the hydraulic medium against the force of the return spring 18 into the pressure position shown in FIG. 1. The return spring 19 of the other cylinder 13 now pushes the piston 15 into the relief position shown in FIG. 1. The hydraulic medium which is no longer under pressure is then displaced from the annular space 41 into the annular space 43 via the working connection B and the bores 34, 38 and from there via the bores 39, 35 to the tank connection T.
  • the working stroke 46 of the switching piston 3 is between the stop points 44 and 45 of the magnetic plunger 21.
  • the opening stroke 47 of the additional piston 25 connects to the working stroke 46.
  • This opening stroke ensures that the hydraulic pressure acting on the piston 15 of the cylinder 13 does not assume impermissibly high values, but is limited to a predetermined value.
  • the level of this pressure can be adjusted by the restoring force of the spring 22.
  • the cover 23 can be provided with a threaded part (not shown) on which the Return spring 22 is supported. By screwing this threaded part into the cover 23 to a greater or lesser extent, the force of the return spring 22 can then be adjusted sensitively.
  • the valve arrangement can be easily and precisely adapted to the most varied of applications. This makes it possible to set the maximum allowable pressure exactly.
  • the additional piston 25a is also mounted in the bore of the switching piston 3a, the end of which is adjacent to the cover 23a of the directional control valve 1a is formed by an adapter piece 48.
  • the adapter piece 48 has the advantage that the diameter of the additional piston 25a is not dependent on the dimensions of the switching piston 3a.
  • the switching piston 3a has an annular groove 49 adjacent to the adapter piece 48, into which the adapter piece 48 engages with a flanged edge 50.
  • the adapter piece 48 has a socket part 51 with which it sits on the end of a base body 68 of the switching piston 3a and the free end face of which is flanged.
  • the bottom 52 of the socket part 51 lies flat against the end face 53 of the base body 68.
  • the socket part 51 is followed by an extension 54, which is advantageously formed in one piece with the socket part 51 and whose outer diameter is smaller than the outer diameter of the socket part 51 and preferably also smaller than the outer diameter of the base body 68.
  • the extension 54 serves as a bearing and guide for the additional piston 25a and thus for the spring plate 24a, on which one end of the return spring 22a is supported for the switching piston 3a. With its other end, the return spring 22a in turn rests on the cover 23a.
  • the approach 54 is centrally penetrated by a longitudinal bore 55, which also penetrates the bottom 52 of the socket part 51.
  • the axial longitudinal bore 55 is aligned with the bore 26a of the base body 68, thus forming a continuation of this bore 26a.
  • the additional piston 25a is mounted axially displaceably in the longitudinal bore 55.
  • the longitudinal bore 55 penetrates a diametral bore 56 which penetrates the shoulder 54 of the adapter piece 48.
  • the bore 26a of the base body 68 is thus connected to the space 31a via the longitudinal bore 55 and the diametral bore 56 of the adapter piece 48.
  • the spring plate 24a is designed as a sleeve which has a bottom 57. It is penetrated by a central bore 58, in which the additional piston 25a is held axially.
  • the end of the spring plate 24a facing away from the bottom 57 is provided with a conical surface 59 opening towards the bottom 52 of the socket part 51, which together with the opposite underside of the bottom 52 of the socket part 51 has an obliquely outwardly tapering flow area 60 for the hydraulic medium forms.
  • the spring plate 24a surrounds the shoulder 54 of the adapter piece 48 with a slight radial play 61.
  • a space 62 is formed between the bottom 57 of the spring plate 24a and the end face of the shoulder 54, the volume of which is in Dependence on the stroke of the additional piston 25a changes.
  • This space 62 is connected to the tank connection T via the annular gap 61.
  • the hydraulic medium can only flow through with a pressure gradient. This ensures excellent damping of the additional piston 25a, which, as a result, cannot oscillate during operation of the valve arrangement.
  • This valve arrangement is therefore characterized by a very high level of noise damping. Also, no pressure pulsations occur due to the damping of the additional piston 25a.
  • the valve arrangement according to FIG. 3 is otherwise of the same design as the exemplary embodiment according to FIG. 1.
  • the mode of operation of this valve arrangement is basically the same as in the previous exemplary embodiment. If the magnet plunger 21 of the magnet 20 comes into the stop position at the stop of the magnet, the additional piston 25a is then displaced by the hydraulic medium against the force of the return spring 22a in the bore 55 of the adapter piece 48, whereby the diametral bore 56 is released.
  • the hydraulic medium can then flow in the manner described via the diametral bore 27 (FIG. 1) of the switching piston 3a, the bores 26a and 55 into the diametral bore 56. There, the hydraulic medium enters the space 31a, in which the relief bore 29a opens.
  • the embodiment according to FIG. 3 is again characterized by its simple construction.
  • the additional piston 25a in connection with the diametral bore 56 in turn forms a pressure relief valve 67a, which is accommodated within the installation space of the directional control valve 1a.
  • this valve arrangement like the embodiment according to FIG. 1 - takes up very little space and can now also be used where space is tight or the construction volume cannot be exceeded.
  • this valve arrangement is characterized by the described high damping of the additional piston 25a and the associated high noise damping, the reduction of the pressure pulsations and the extremely low additional costs for the pressure limiting valve.
  • annular channel can also be provided instead of the diametrical bores 28 and 56.
  • annular channel can also be provided instead of the diametrical bores 28 and 56.
  • the flow gain can be substantially greater than with radial bores.
  • the additional piston 25, 25a can be a simple and inexpensive bearing needle in the embodiments according to FIGS. 1 and 3.
  • Fig. 4 shows two embodiments of valve members that can be used instead of the additional piston for the pressure relief valve.
  • the valve member 25b is designed as a ball, on which the spring plate 24b for the return spring 22b is supported.
  • the ball 25b closes the bore 26b of the switching piston 3b.
  • valve member is designed as a cone 25c. It is advantageously formed in one piece with the spring plate 24c for the return spring.
  • valve members 25b, 25c release the bore 26b of the switching piston 3b when the force generated by the return spring is exceeded, so that the hydraulic medium can flow out via the space 31a and the relief bore 29a to the tank connection T in the manner described.

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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)
  • Safety Valves (AREA)
EP19930105594 1992-04-15 1993-04-05 Agencement de soupape Expired - Lifetime EP0565982B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19924212550 DE4212550C2 (de) 1992-04-15 1992-04-15 Ventilanordnung mit einem Wegeventil
DE4212550 1992-04-15

Publications (2)

Publication Number Publication Date
EP0565982A1 true EP0565982A1 (fr) 1993-10-20
EP0565982B1 EP0565982B1 (fr) 1997-07-09

Family

ID=6456843

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930105594 Expired - Lifetime EP0565982B1 (fr) 1992-04-15 1993-04-05 Agencement de soupape

Country Status (3)

Country Link
US (1) US5417241A (fr)
EP (1) EP0565982B1 (fr)
DE (2) DE4212550C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4420164A1 (de) * 1994-06-09 1995-12-14 Rexroth Mannesmann Gmbh Kombiniertes Druck- und Schaltventil
WO1998044266A1 (fr) * 1997-04-02 1998-10-08 Voith Turbo Gmbh & Co. Kg Dispositif a soupape, en particulier dispositif combine valve proportionnelle-distributeur

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DE19834765A1 (de) * 1998-08-01 2000-02-03 Hydraulik Ring Gmbh Hydrauliksystem zum Betätigen von wenigstens zwei Funktionsbereichen in einem Fahrzeug
GB9820620D0 (en) 1998-09-23 1998-11-18 Lucas Ind Plc Improved solenoid controlled valve
WO2000018382A2 (fr) * 1998-09-28 2000-04-06 Tiefenbach Bergbautechnik Gmbh Distributeur hydraulique
DE10041168A1 (de) * 2000-08-21 2002-03-07 Mannesmann Rexroth Ag Ventileinrichtung
ITTO20010700A1 (it) * 2001-07-17 2003-01-17 Bottero Spa Gruppo valvolare proporzionale, particolarmente per l'alimentazione di aria in pressione in una macchina per la formatura di articoli di vet
US7000580B1 (en) 2004-09-28 2006-02-21 Borgwarner Inc. Control valves with integrated check valves
CN100441886C (zh) * 2004-11-12 2008-12-10 宁波华液机器制造有限公司 三通比例减压控制阀
US6971354B1 (en) 2004-12-20 2005-12-06 Borgwarner Inc. Variable camshaft timing system with remotely located control system
JP5188982B2 (ja) * 2005-12-13 2013-04-24 ボーグワーナー インコーポレーテッド バンド式チェックバルブを有する液圧テンショナ
US8387644B2 (en) * 2007-02-09 2013-03-05 Saturn Electronics & Engineering, Inc. Solenoid operated fluid control valve
EP2522820B1 (fr) * 2007-07-02 2017-08-09 BorgWarner Inc. Came concentrique avec clapets anti-retour dans la bobine pour un déphaseur
DE102007053877B3 (de) * 2007-11-09 2009-04-16 Voith Patent Gmbh Wegeschieber zur Steuerung von Arbeitszylindern oder Servomotoren
US8984853B2 (en) 2010-05-21 2015-03-24 United Technologies Corporation Accessing a valve assembly of a turbomachine
FI20115108A7 (fi) 2011-02-03 2012-08-04 Parker Hannifin Mfg Finland Oy Painesäädöllä varustettu suuntaventtiili
CN103148034A (zh) * 2013-02-02 2013-06-12 无锡市晟瑞机械电子有限公司 液压比例阀
DE102013113716B4 (de) * 2013-12-09 2020-12-24 Kendrion (Villingen) Gmbh Elektromagnetisches Plattenschieberventil mit Druckregelung
DE102014007129A1 (de) * 2014-05-16 2015-11-19 Audi Ag Elektromagnet für ein Hydrauliksystem
DE102014007130B3 (de) * 2014-05-16 2015-10-15 Audi Ag Elektromagnetventil für ein Hydrauliksystem
DE102014109097A1 (de) * 2014-06-27 2015-12-31 Hilite Germany Gmbh Hydraulikventil
DE102021202897A1 (de) 2021-03-24 2022-09-29 Zf Friedrichshafen Ag Aktuator zum Betätigen einer Parksperre

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Publication number Priority date Publication date Assignee Title
DE1290778B (de) * 1966-06-04 1969-03-13 Voith Getriebe Kg Elektromagnetisch betaetigtes Hydraulikventil
EP0128002A2 (fr) * 1983-06-01 1984-12-12 Vickers Incorporated Servovalve pour dispositifs hydrauliques à deux étages
DE3917418A1 (de) * 1989-05-29 1990-12-06 Vickers Systems Gmbh Elektro-hydraulisch bewegbares steuerventil

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US2946347A (en) * 1959-04-22 1960-07-26 New York Air Brake Co Control valve having a movable member containing combination check and relief valve unit
US3200841A (en) * 1963-06-20 1965-08-17 New York Air Brake Co Valve
DE3435950A1 (de) * 1984-09-29 1986-04-03 Alfred Teves Gmbh, 6000 Frankfurt Mehrwegeventil, insbesondere druckgesteuertes einstroemventil
DE3508340C2 (de) * 1985-03-08 1987-04-30 Mannesmann Rexroth GmbH, 8770 Lohr Mehrwegeventil
DE3938417C1 (fr) * 1989-11-18 1991-03-21 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
JP2651873B2 (ja) * 1989-11-20 1997-09-10 株式会社ゼクセル 変速機用油圧クラッチの切換弁
JP2784836B2 (ja) * 1990-05-11 1998-08-06 株式会社ゼクセル 電磁切換弁
DE4123036C2 (de) * 1991-07-12 1994-08-11 Daimler Benz Ag Schieberventil

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1290778B (de) * 1966-06-04 1969-03-13 Voith Getriebe Kg Elektromagnetisch betaetigtes Hydraulikventil
EP0128002A2 (fr) * 1983-06-01 1984-12-12 Vickers Incorporated Servovalve pour dispositifs hydrauliques à deux étages
DE3917418A1 (de) * 1989-05-29 1990-12-06 Vickers Systems Gmbh Elektro-hydraulisch bewegbares steuerventil

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4420164A1 (de) * 1994-06-09 1995-12-14 Rexroth Mannesmann Gmbh Kombiniertes Druck- und Schaltventil
WO1998044266A1 (fr) * 1997-04-02 1998-10-08 Voith Turbo Gmbh & Co. Kg Dispositif a soupape, en particulier dispositif combine valve proportionnelle-distributeur

Also Published As

Publication number Publication date
EP0565982B1 (fr) 1997-07-09
US5417241A (en) 1995-05-23
DE4212550C2 (de) 1998-12-10
DE59306854D1 (de) 1997-08-14
DE4212550A1 (de) 1993-10-21

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