EP2414713A2 - Vanne de régulation de la pression, en particulier pour une transmission automatique d'un véhicule automobile - Google Patents

Vanne de régulation de la pression, en particulier pour une transmission automatique d'un véhicule automobile

Info

Publication number
EP2414713A2
EP2414713A2 EP10711612A EP10711612A EP2414713A2 EP 2414713 A2 EP2414713 A2 EP 2414713A2 EP 10711612 A EP10711612 A EP 10711612A EP 10711612 A EP10711612 A EP 10711612A EP 2414713 A2 EP2414713 A2 EP 2414713A2
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
control valve
section
channel
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.)
Withdrawn
Application number
EP10711612A
Other languages
German (de)
English (en)
Inventor
Walter Fleischer
Tilo Hofmann
Andrzej Pilawski
Klaus Schudt
Christof Ott
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2414713A2 publication Critical patent/EP2414713A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0251—Elements specially adapted for electric control units, e.g. valves for converting electrical signals to fluid signals
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F16K31/0613—Sliding valves with cylindrical slides
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0251—Elements specially adapted for electric control units, e.g. valves for converting electrical signals to fluid signals
    • F16H2061/0253—Details of electro hydraulic valves, e.g. lands, ports, spools or springs

Definitions

  • Pressure control valve in particular for an automatic transmission in a motor vehicle
  • the invention relates to a pressure regulating valve, in particular for an automatic transmission in a motor vehicle, according to the preamble of claim 1.
  • a pressure regulating valve of the type mentioned is known from US 2007/0023722 A1.
  • the pressure regulating valve described therein has a valve slide, which is guided in a bore with a constant diameter. Via an actuating piston of the valve spool is coupled to an electromagnetic actuator.
  • the valve spool is in the known
  • Pressure control valve acted upon by an acting as a helical spring biasing against the effective direction of the electromagnetic actuator.
  • control behavior in the known pressure control valve is unsatisfactory, and the production of the individual components is expensive.
  • Object of the present invention is to provide a pressure control valve, which provides a high control quality and can be produced inexpensively at the same time.
  • the force acting counter to the first direction of action on the valve spool depends on the pressure currently prevailing at the regulating pressure opening. If the pressure at the control pressure opening, the force acting on the valve spool against the first direction of action also decreases, whereby the valve spool is moved in the direction of action. If, on the other hand, the pressure prevailing at the control pressure opening increases, the force acting on the valve spool counter to the first direction of action also increases, as a result of which it is moved counter to the first effective direction.
  • This self-regulating function of the valve spool is achieved in that in the two pressure chambers, which are bounded by the opposite end faces of the valve spool, the prevailing at the control pressure port
  • a pressure control valve which provides a precise self-regulation function, at the same time simple design and correspondingly low production costs.
  • this comprises at least one outside of the valve spool Channel connecting at least one of the pressure chambers to the control pressure port.
  • valve slide at least one channel is present, which connects at least one of the pressure chambers with the control pressure opening.
  • the advantage of this development is that a redesign, for example, the automatic transmission is not required because the outer dimensions and connections of the pressure control valve remain unchanged. Even the housing of the pressure control valve may remain essentially unchanged, because it is sufficient to replace the valve spool against such with a channel and seal the two pressure chambers to the outside, for example, by appropriate plugs.
  • the channel can be arranged eccentrically to the longitudinal axis of the valve spool.
  • the piston of the electromagnetic actuator can engage the center of the face, which prevents tilting moments and unilateral wear without blocking the channel.
  • a simple variant for connecting the channel with the control pressure opening is the realization of a corresponding transverse opening in the valve slide.
  • the first end face is at least partially formed on a pressure piece, which is connected to a base body of the valve spool and in which the channel opens.
  • a pressure piece which is designed as a stamped and bent part, particularly inexpensive.
  • the first end face may be formed as at least partially as integral with the valve spool bottom into which the channel opens. Since usually the piston acts as centrally as possible on the valve spool in order to avoid tilting moments and consequently uneven wear and undefined leakage, the mouth of the channel should be eccentric.
  • the passage can be easily made by an off-center through-bore that is fluidly connected to the control pressure port by a corresponding transverse bore.
  • the piston may also be formed at least partially integral with the valve spool. Although this increases the production cost somewhat, since the demands on the manufacturing accuracy of the leadership of the valve spool in the housing and the leadership of the piston in the housing, if one is present, are increased; in return, however, additional guidance is provided and the number of parts to be handled separately is reduced.
  • Figure 1 is a schematic representation of an automatic transmission and an associated hydraulic circuit with a pressure control valve
  • Figure 2 is a partial section through the pressure regulating valve of Figure 1;
  • Figure 3 is a view similar to Figure 2 of a first alternative embodiment
  • Figure 4 is a view similar to Figure 2 of a second alternative embodiment.
  • FIG. 1 An automatic transmission of a motor vehicle is shown in FIG. 1 by a dash-dotted box, it bears the reference number 10 overall.
  • a hydraulic circuit 12 to which a pressureless hydraulic reservoir 14 and a hydraulic pump 16 belong, serves to control the automatic transmission 10.
  • An outlet of the hydraulic pump 16 forms a supply port 18, to which a pressure regulating valve 20 is connected.
  • the pressure control valve 20 From the pressure control valve 20 leads a return to a return port 22, which returns to the hydraulic reservoir 14. Further, the pressure regulating valve 20 is connected to a working port 24 to which the pressure to be controlled by the pressure regulating valve 20 is applied. In addition, the pressure regulating valve 20 has an electromagnetic actuator 26.
  • the pressure control valve 20 is constructed as follows: It comprises a sleeve-like housing 28 in which a guide bore 30 for a likewise sleeve-like hollow valve spool 32 is present.
  • the valve spool 32 has three adjacent sections 34, 36 and 38 in the axial direction.
  • the leftmost and first section 34 in FIG. 2 has a first diameter D1, which corresponds approximately to the inner diameter of the guide bore 30.
  • the approximately central second portion 36, which adjoins the first portion 34 has a second diameter D2, which is smaller than the first diameter D1.
  • the adjoining the second portion 36 third section 38 in turn has the first diameter D1. Since the guide bore 30 has the same inner width everywhere, an annular space 40 is formed between the guide bore of the housing 28 and the second portion 36 of the valve spool 32.
  • the second section 36 facing edge of the first portion 34 forms a
  • Control edge 42 whose function will be discussed in more detail later.
  • the second section 36 facing edge of the third portion forms a control edge 43rd
  • valve spool 32 is hollow in its interior. While it is completely open at its left end in FIG. 2, a disc-shaped pressure piece 44 is provided in its right-hand end in FIG. 2, which is designed as a stamped and bent part.
  • the pressure piece 44 is pressed into a corresponding receptacle (without reference numeral) of a base body 46 of the valve slide 32, there held captive.
  • the pressure piece 44 has a
  • the cavity in the interior of the valve spool 32 forms a channel 54, the function of which will also be discussed in greater detail below.
  • the channel 54 is connected in the region of the second portion 36 by transverse bores 56 with the annular space 40.
  • the first section 34 of the valve spool 32 in the housing 28 is associated with an inlet pressure port 58, the second section 36 a control pressure port 60 and the third section 38 a return port 62.
  • the inlet pressure port 58 is connected to the supply port 18, the control pressure port 60 to the working port 24, and the return port 62 with the return port 22.
  • the electromagnetic actuator 26 is disposed on the right side of the pressure regulating valve 20 in FIG. It includes, inter alia, an annular coil 64 and a centrally disposed armature 66.
  • a space 68, in which the armature 66 is received, is connected through a vent opening 70 with a non-pressurized outer space (no reference numeral).
  • a pin-shaped piston 72 is arranged, whose end faces 73 and 75 are formed spherical in the present embodiment, in order to create a centric, so lying on the longitudinal axis of the valve spool force application point.
  • the pressure piece 44 facing end face 73 of the piston 72 is located on the pressure piece 44, the armature 66 facing end face 75 of the piston 72 on the armature 66.
  • the piston 72 is in a through hole 74 in a guide bore 30 from
  • Anchor space 68 separating housing wall 76 guided fluid-tight.
  • valve spool 32 In operation, the valve spool 32 is acted upon by the piston 72 by means of the electromagnetic actuator 26 in a first effective direction, which is indicated in Figure 2 by an arrow 78.
  • the helical compression spring 53 urges the valve spool 32 counter to this first direction of action 78.
  • the pressure control valve 20 operates as follows: If the valve spool 32 is in a leftmost position in FIG. 2, hydraulic oil flows under high pressure from the supply port 18 and the inlet pressure port 58 into the annular space 40 and from there via the regulating pressure port 60 to the working port 24.
  • the return port 62 is substantially covered by the control edge 43, the return opening 62 is thus separated from the annular space 40 substantially.
  • the valve slide 32 is in a rather right-hand position, the inlet pressure opening 58 in the housing 28 is covered by the control edge 42, ie the annular space 40 is essentially separated from the inlet pressure opening 58. Instead, the control edge 43 now releases the return opening 62, so that the control pressure opening 60 communicates with the return opening 62. In this way, the control pressure opening
  • valve spool 32 results from the equilibrium of forces between the one hand on the valve spool 32 and the
  • Piston 72 engaging hydraulic forces and on the other hand, the force exerted by the electromagnetic actuator 26 via the piston 72 on the valve spool 32 and the force applied by the coil spring 53 on the valve spool 32 force.
  • the valve spool 32 is pressure-balanced in the embodiment shown in Figure 2, ie the sum of the hydraulic forces acting on it in about zero: A in Figure 2 left of the valve spool 32 existing pressure chamber 80 in which the helical compression spring 53 is arranged, namely communicates over the channel 54 and the transverse bores 56 as well with the control pressure port 60 as a right in Figure 2 from the pressure piece 44 existing pressure chamber 82, the latter on the
  • FIG. An alternative embodiment is shown in FIG.
  • elements and regions which have equivalent functions to elements and regions which have already been described in connection with a preceding figure bear the same reference numerals and are not explained again in detail.
  • valve spool 32 is not designed as a hollow part, but as a solid material piston.
  • the connection of the two pressure chambers 80 and 82 with the control pressure port 60 is therefore provided by an external channel 84. This can for example in a
  • valve spool 32 is hollow, according to the embodiment shown in Figure 2.
  • piston 72 is not designed as a separate part, but in one piece with the
  • Pressure piece 44 executed.
  • the control function corresponding to the pressure prevailing at the control pressure opening 60 is provided by a region of the pressure element 44 which corresponds to the cross section of the piston 72 being "shadowed", ie the control pressure prevailing in the pressure chamber 82 can not act on it.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Transmission Device (AREA)
  • Magnetically Actuated Valves (AREA)
  • Safety Valves (AREA)
  • Control Of Fluid Pressure (AREA)

Abstract

L'invention concerne une vanne de régulation de la pression (20) d'une transmission automatique d'un véhicule automobile, comprenant un boîtier (28), un coulisseau de vanne (32) guidé dans le boîtier (28) et comprenant plusieurs sections adjacentes (34, 36, 38). Une première section (34) possède un premier diamètre (D1), une deuxième section (36) poursuivant celle-ci possède un deuxième diamètre (D2) qui est inférieur au premier diamètre (D1) et une troisième section (38) poursuivant celle-ci possède le premier diamètre (D1). La première section (34) est associée à une ouverture d'alimentation en pression (58), la deuxième section (36), à une ouverture (60) de régulation de la pression, et la troisième section (38), à une ouverture de retour (62). Un dispositif d'actionnement électromagnétique (26) actionne le coulisseau de vanne (32) dans une première direction d'action (78), à l'aide d'un piston (72) guidé dans le boîtier (28) de façon étanche à la pression et s'engageant contre une première face frontale (50). Un dispositif d'admission (53) actionne le coulisseau de vanne (32) à l'opposé de la première direction d'action (78). Il est proposé que la première face frontale (50) du coulisseau de vanne (32) délimite une première chambre de pression (82) et qu'une deuxième face frontale (52), opposée, délimite une deuxième chambre de pression (80), chacune des chambres étant reliée fluidiquement avec l'ouverture de régulation de la pression (60).
EP10711612A 2009-03-31 2010-02-18 Vanne de régulation de la pression, en particulier pour une transmission automatique d'un véhicule automobile Withdrawn EP2414713A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009002003A DE102009002003A1 (de) 2009-03-31 2009-03-31 Druckregelventil, insbesondere für ein Automatikgetriebe in einem Kraftfahrzeug
PCT/EP2010/052035 WO2010112263A2 (fr) 2009-03-31 2010-02-18 Vanne de régulation de la pression, en particulier pour une transmission automatique d'un véhicule automobile

Publications (1)

Publication Number Publication Date
EP2414713A2 true EP2414713A2 (fr) 2012-02-08

Family

ID=42543222

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10711612A Withdrawn EP2414713A2 (fr) 2009-03-31 2010-02-18 Vanne de régulation de la pression, en particulier pour une transmission automatique d'un véhicule automobile

Country Status (5)

Country Link
US (1) US20120104293A1 (fr)
EP (1) EP2414713A2 (fr)
JP (1) JP2012522297A (fr)
DE (1) DE102009002003A1 (fr)
WO (1) WO2010112263A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010043697A1 (de) * 2010-11-10 2012-05-10 Robert Bosch Gmbh Druckregelventil, insbesondere zur Ansteuerung einer Kupplung in einem Kraftfahrzeug-Automatikgetriebe
DE102010064153A1 (de) 2010-12-27 2012-06-28 Robert Bosch Gmbh Verfahren zur Erfassung eines elektrischen Signals zur Ansteuerung eines Aktuators und Vorrichtung zur Steuerung eines Aktuators
DE102014214920A1 (de) 2014-07-30 2016-02-04 Robert Bosch Gmbh Schieberventil, mit einem Gehäuse und mit einem in einer Führungsausnehmung des Gehäuses angeordneten axial bewegbaren Ventilschieber
JP6656831B2 (ja) * 2015-07-08 2020-03-04 ナブテスコ株式会社 電磁比例弁
DE102017201518A1 (de) 2017-01-31 2018-08-02 Zf Friedrichshafen Ag Ventilvorrichtung mit einem verstellbaren Druckventil
DE102018222614A1 (de) * 2018-12-20 2020-06-25 Robert Bosch Gmbh Elektromagnetische Betätigungseinrichtung
US12072020B2 (en) 2021-12-15 2024-08-27 Ford Global Technologies, Llc Unitized valve body having annulus

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US904839A (en) * 1907-10-31 1908-11-24 Matthias Christian Piston-valve.
US2540467A (en) * 1947-05-23 1951-02-06 Hagan Corp Pilot valve
GB804449A (en) * 1956-05-22 1958-11-19 John Eldridge Collins Solenoid-operated control valve for fluids
SE312704B (fr) * 1964-07-22 1969-07-21 Sperry Rand Ltd
JPS5421912B2 (fr) * 1971-12-02 1979-08-02
US4009730A (en) * 1975-10-03 1977-03-01 Caterpillar Tractor Co. Combination pressure control selector valve
DE3309065A1 (de) * 1983-03-14 1984-09-20 Mannesmann Rexroth GmbH, 8770 Lohr Kolbenschieber fuer ein mehrwegeventil
JP2553341B2 (ja) * 1987-02-26 1996-11-13 株式会社ユニシアジェックス 圧力制御弁
JP2553345B2 (ja) * 1987-03-24 1996-11-13 株式会社ユニシアジェックス 圧力制御弁
DE4221757C2 (de) * 1992-07-02 1997-05-15 Rexroth Mannesmann Gmbh Magnetbetätigtes Proportional-Wegeventil
US6435213B2 (en) * 1999-04-23 2002-08-20 Visteon Global Technologies, Inc. Solenoid operated hydraulic control valve
US6269827B1 (en) * 1999-10-07 2001-08-07 Eaton Corporation Electrically operated pressure control valve
US6615869B2 (en) * 2001-03-26 2003-09-09 Denso Corporation Solenoid valve
JP2003028335A (ja) * 2001-07-11 2003-01-29 Aisin Seiki Co Ltd リニアソレノイドバルブ
US6907901B2 (en) 2002-06-03 2005-06-21 Borgwarner Inc. Solenoid control valve
JP2006118682A (ja) * 2004-10-25 2006-05-11 Denso Corp 油圧電磁制御弁
JP2007032689A (ja) 2005-07-26 2007-02-08 Denso Corp スプール弁装置
CN101668973B (zh) * 2007-03-31 2013-03-13 盾安美斯泰克公司(美国) 先导式滑阀
DE112008001516A5 (de) * 2007-07-18 2010-06-10 Schaeffler Kg Ventilteil eines hydraulischen Steuerventils

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010112263A2 *

Also Published As

Publication number Publication date
WO2010112263A3 (fr) 2011-02-24
WO2010112263A2 (fr) 2010-10-07
JP2012522297A (ja) 2012-09-20
US20120104293A1 (en) 2012-05-03
DE102009002003A1 (de) 2010-10-07

Similar Documents

Publication Publication Date Title
EP0325958B1 (fr) Clapet à commande hydraulique
EP2414713A2 (fr) Vanne de régulation de la pression, en particulier pour une transmission automatique d'un véhicule automobile
DE4212550C2 (de) Ventilanordnung mit einem Wegeventil
DE102004061800A1 (de) Injektor eines Kraftstoffeinspritzsystems einer Brennkraftmaschine
DE2813618C2 (de) Elektromagnetisch betätigtes Druckregelventil
DE102014017801B4 (de) Druckbegrenzungsventil
DE2608791C2 (fr)
EP2585745B1 (fr) Vanne de commutation par pression des fluides
EP3584475B1 (fr) Soupape à voies intégrée hydraulique pilotée
DE102016107986A1 (de) Hydraulikventil und Pleuel mit einem Hydraulikventil
EP0667459A1 (fr) Unité de soupape à électro-aimant proportionnel
EP0626303B1 (fr) Aménagement de soupape
EP3370130A1 (fr) Soupape de réglage de pression à tige de transmission de pression
EP0222858B1 (fr) Sectionneur de tuyau
DE102007008621A1 (de) Ventilbaugruppe
EP1319127A1 (fr) Configuration de soupapes de distribution
DE3011196C2 (fr)
EP3865746A1 (fr) Soupape de commande électrohydraulique
DE2255191C3 (de) Druckabhängiges Steuerventil
DE112019001633T5 (de) Ventilvorrichtung
DE19717807B4 (de) Von mindestens einem Elektromagneten betätigbares Wegeventil
DE19544591C2 (de) Zwei-Wege-Einbauventil
DE2905178C2 (de) Bremsventil zur gesteuerten Entlastung eines Hochdruckraums
DE19545021B4 (de) Elektromagnetisch betätigtes Wegeventil
DE19847997B4 (de) Hydraulisches Rückschlagventil, insbesondere Füllventil

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20111031

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20140902