EP1364108A1 - Systeme de soupape d'echange gazeux pour moteur a combustion interne - Google Patents

Systeme de soupape d'echange gazeux pour moteur a combustion interne

Info

Publication number
EP1364108A1
EP1364108A1 EP02708247A EP02708247A EP1364108A1 EP 1364108 A1 EP1364108 A1 EP 1364108A1 EP 02708247 A EP02708247 A EP 02708247A EP 02708247 A EP02708247 A EP 02708247A EP 1364108 A1 EP1364108 A1 EP 1364108A1
Authority
EP
European Patent Office
Prior art keywords
gas exchange
valve
pressure accumulator
exchange valve
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
EP02708247A
Other languages
German (de)
English (en)
Other versions
EP1364108B1 (fr
Inventor
Hermann Gaessler
Udo Diehl
Karsten Mischker
Rainer Walter
Juergen Schiemann
Christian Grosse
Volker Beuche
Stefan Reimer
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 EP1364108A1 publication Critical patent/EP1364108A1/fr
Application granted granted Critical
Publication of EP1364108B1 publication Critical patent/EP1364108B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
    • F01L2013/0094—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing with switchable clamp for keeping valve open

Definitions

  • the present invention relates to a
  • Gas exchange valve device for an internal combustion engine, in particular a motor vehicle, with a hydraulic device which comprises a fluid circuit, at least one pressure accumulator connected to the fluid circuit with a piston biased by a device, and a controllable actuation device, and with a gas exchange valve, the valve element of which is actuated by the actuation device ,
  • Such a gas exchange valve device is known from DE 198 26 047 AI.
  • Gas exchange valve device is used when the internal combustion engine has no camshaft.
  • Such an internal combustion engine has the advantage that the control times of the intake and exhaust valves are independent of the position of the piston of the respective cylinder.
  • valve opening and closing times can be realized, which enable the internal combustion engine to be operated with particularly low emissions and consumption.
  • the known hydraulic device works with a hydraulic circuit, which consists of a hydraulic reservoir is fed by a high pressure hydraulic pump.
  • the actuating device comprises a piston which can be acted upon hydraulically in both directions of movement and which is connected to the valve stem of the valve element of a gas exchange valve.
  • One of the two chambers of the hydraulic cylinder can be pressurized with 2/2 switching valves, which leads to a corresponding movement of the piston and thereby the valve element on the engine block.
  • the hydraulic circuit is connected to a hydraulic pressure accumulator, which is designed as a spring-loaded piston accumulator and serves to dampen vibrations in the hydraulic system. Furthermore, a similarly constructed emergency pressure accumulator is connected to one of the two chambers in the hydraulic cylinder, which, when the pressure in the hydraulic line drops, still provides sufficient pressure and fluid volume that the valve can be moved into its closed rest position. Both pressure accumulators work with different pressure levels, which are set by different stiffnesses of their return springs.
  • an emergency closing spring is provided in the known gas exchange valve device, which presses the piston of the actuating device and thus also the valve element into the closed position when there is no hydraulic pressure. This ensures that when the internal combustion engine is restarted, the valve element does not protrude into the combustion chamber in such a way that it can collide, for example, with other valve elements or even with the piston of the internal combustion engine moving in the combustion chamber.
  • the present invention therefore has the task of developing a gas exchange valve device of the type mentioned at the outset in such a way that it can be manufactured more economically and more simply and can be operated with as little energy expenditure as possible.
  • the invention assumes that the pressure accumulator in is designed in such a way that, if the hydraulic pressure in the fluid circuit drops, it can still provide such a sufficient fluid volume that the actuating device can bring the valve element of the gas exchange valve into a substantially closed position.
  • the piston of the pressure accumulator moves towards its non-pressurized rest position due to its prestress. It achieves this when the fluid circuit and thus also the pressure accumulator are essentially depressurized.
  • valve element of the pressure accumulator is additionally used according to the invention for the blocking process of the valve element: the pressure accumulator is so arranged that its piston releases the valve element of the gas exchange valve when it is pressurized via the fluid circuit and pushed out of its rest position. In such an operating state, in which the fluid circuit and thus also the pressure accumulator are pressurized, the valve element can move freely and, as a result, the internal combustion engine can also be operated normally.
  • the pressure in the fluid circuit drops to a value below the normal operating pressure
  • the hydraulic fluid is pressed out of the pressure accumulator by the spring action of the piston and the valve element of the gas exchange valve is closed via the actuating device.
  • the pressure accumulator is arranged such that when the piston reaches its non-pressurized position of rest and thus no fluid volume can be provided by the pressure accumulator for closing or maintaining the closed state of the valve element, the valve element of the gas exchange valve is essentially closed in it Position blocked.
  • an emergency closing spring is therefore no longer necessary, since the locking of the valve element of the gas exchange valve in an essentially closed position is carried out by the piston of the pressure accumulator in the event of a pressure loss.
  • the gas exchange valve device according to the invention can thus be manufactured considerably more cheaply and easily.
  • a lower hydraulic pressure is required to move the valve element into an open position since, apart from the inertial forces of the valve element, no further forces have to be overcome.
  • the piston of the pressure accumulator acts at least indirectly on a valve stem of the valve element of the gas exchange valve when the pressure accumulator is approximately depressurized.
  • the valve stem of the valve element generally has a certain length, so that the positioning of the pressure accumulator such that its piston can act on the valve stem is relatively easy.
  • the piston of the pressure accumulator acts directly on the actuating device, for example, and there, for example, blocks the piston of a hydraulic cylinder in a specific position.
  • a contact surface which is at least indirectly connected to the piston of the pressure accumulator and a contact surface which is at least indirectly connected to the valve element of the gas exchange valve work together in the approximately pressureless state of the pressure accumulator in frictional engagement.
  • only very small forces are required to block the valve element of the gas exchange valve.
  • the valve element of the gas exchange valve can move from the closed position into the open position due to its weight. This is reliably possible through a simple frictional connection. Such is very inexpensive and easy to implement.
  • the contact surface at least indirectly connected to the piston of the pressure accumulator and / or the contact surface at least indirectly connected to the valve element of the gas exchange valve are / are designed as a friction surface (s). In this way, the frictional engagement and thus the possible holding force can be improved in a simple manner.
  • the contact surface at least indirectly connected to the piston of the pressure accumulator can cooperate with the contact surface at least indirectly connected to the valve element of the gas exchange valve in the approximately pressureless state of the pressure accumulator in a positive connection.
  • This training is alternatively or in addition to the above-mentioned friction.
  • a positive lock enables the valve element to be locked in the desired position even more securely.
  • a recess is provided in the valve stem of the valve element of the gas exchange valve, in which an engaging section which is at least indirectly connected to the piston of the pressure accumulator engages in the approximately depressurized state of the pressure accumulator.
  • an engaging section which is at least indirectly connected to the piston of the pressure accumulator engages in the approximately depressurized state of the pressure accumulator.
  • the recess can be arranged so that the gas exchange valve is blocked in the slightly depressurized state of the pressure accumulator in a slightly open position.
  • FIG. 1 shows a schematic representation of a first exemplary embodiment of a gas exchange valve device of an internal combustion engine
  • FIG. 2 shows a partial section through a region of the gas exchange valve device from FIG. 1 with a valve element and a pressure accumulator;
  • FIG. 3 shows a partial section through a Vencilelement and a pressure accumulator of a second embodiment of a gas exchange valve device of an internal combustion engine
  • a gas exchange valve device has the reference number 10 overall. It comprises a gas exchange valve, which in the present case is designed as an inlet valve 12 of an internal combustion engine 14.
  • the inlet valve 12 is actuated by a hydraulic cylinder 16.
  • a hydraulic cylinder 16 This comprises a housing 18, in which a piston 20 with a piston rod 22 is slidably guided.
  • the piston rod 22 is passed through the housing 18 and connected to a valve stem 24, which in turn is molded onto a plate-shaped valve element 26.
  • a region of the surface of the valve stem 24 is designed as a friction surface 25 (see FIG. 2) in the closed position
  • the valve element 26 lies tightly against a valve seat 28 in the upper region of a combustion chamber 30 of the internal combustion engine 14.
  • the gas exchange valve device 10 further comprises a reservoir 34, from which hydraulic fluid is conveyed by a high-pressure pump 36 into a high-pressure hydraulic line 38.
  • the high-pressure hydraulic line 38 branches into a branch 42, which opens directly into a lower working space 44 of the hydraulic cylinder 16 in FIG. 1 (the designations “above” and “below” in this description refer only to the illustrations in FIG the figures; it is understood that the parts of the gas exchange device 10 can be installed in any position).
  • Another branch 46 of the high-pressure hydraulic line 38 leads to a 2/2-way switching valve 48 which is pressed into its closed position by a spring 50 in the de-energized state.
  • the branch 46 of the high-pressure hydraulic line 38 leads after the 2/2 switching valve 48 to an upper working chamber 52 of the hydraulic cylinder 16 in FIG. 1. From there, a high-pressure hydraulic line 54 leads via a further 2/2 switching valve 56 and a check valve 58 back to the reservoir 34.
  • the 2/2-way valve 56 is open when de-energized.
  • a branch line 60 opens, which is connected to a pressure accumulator 62.
  • the pressure accumulator 62 comprises a housing 64 in which a piston 66 is slidably held. The piston 66 is acted upon by a spring 68 in the direction of the end of the pressure accumulator 62, which is connected to the spur line 60.
  • the rigidity and the spring travel of the spring 68 are selected so that the pressure accumulator 62 acts as a vibration damper for the Hydraulic lines 38, 42, 46 and 54 occurring pressure fluctuations can work.
  • a housing 70 of a further pressure accumulator 72 is molded onto the housing 18 of the hydraulic cylinder 16. Its design is shown in detail in Figure 2:
  • a cavity 74 is formed in the housing 70, in which a piston 76 is movably held.
  • the outer lateral surface of the piston 76 is sealed off from the inner wall of the cavity 74 by a sealing ring 78 which lies in an annular groove 80 in the outer lateral surface of the piston 76.
  • the cavity 74 is closed by a cover 82.
  • the cover 82 is provided with a ventilation opening which is not visible in the figure.
  • a spiral spring 84 is tensioned between cover 82 and piston 76 and acts on piston 76 to the left in FIG.
  • a blocking rod 86 is formed on the piston 76 and, in the pressure-free state of the pressure accumulator 72 shown in FIG. 2, extends through a passage 88 into a working space 90.
  • the valve stem 24 of the valve element 26 of the inlet valve 12 extends perpendicular to the longitudinal axis of the piston 76 and the blocking rod 86 likewise through the working space 90. It is sealed off from the working space 90 by sealing rings 92 and 94.
  • the axial end of the blocking rod 86 facing the Vencilschaft 24 is designed as a friction surface 87.
  • a branch line 96 leads from the working space 90 to the lower working space 44 of the hydraulic cylinder 16.
  • the spiral spring 84 of the pressure accumulator 72 has a lower rigidity and a longer spring travel than the spring 68 of the pressure accumulator 62 Pressure accumulator 62, therefore, pressure accumulator 72 does not work as a vibration damper, but rather as an emergency pressure accumulator, which, as will be explained in more detail below, provides a fluid volume which is sufficient to hold valve element 26 in the event of a pressure drop in hydraulic lines 38, 42, 46 and 54 To move intake valve 12 to its closed position.
  • the gas exchange valve device 10 shown in FIGS. 1 and 2 operates as follows:
  • the high pressure pump 36 pumps hydraulic fluid from the reservoir 34 into the hydraulic line 38 and from there via the branch line 42 into the lower working space 44 of the hydraulic cylinder 16.
  • the switching valve 48 is opened and the switching valve 56 is closed, the upper working space 52 of the hydraulic cylinder 60 also becomes pressurized by hydraulic fluid.
  • the engagement surface in the axial direction on the upper side of the piston 20 of the hydraulic cylinder 16 is larger than on its underside, the piston 20 is pressed down and the inlet valve 12 is opened.
  • valve element 26 can thus be freely moved by the piston 20 of the hydraulic cylinder 16 via the valve stem 74 and the piston rod 22. Since neither the piston 20 nor the valve element 26 are pressed into one position or the other by a spring, only a small hydraulic force is required for the movement of the valve element 26.
  • the pressure in the cavity 74 of the pressure accumulator also decreases as a result 72.
  • the spiral spring 84 can push the piston 76 of the pressure accumulator 72 to the left in FIG. 2.
  • the hydraulic fluid stored in the cavity 74 is therefore pressed through the passage 88, the working space 90 and the branch line 96 into the lower working space 44. There, the inflowing hydraulic fluid in turn pushes the piston 20 of the hydraulic cylinder 16 upward.
  • the switching valve 56 is open when the internal combustion engine 14 is switched off and therefore the upper working chamber 52 of the hydraulic cylinder 16 is depressurized. As a result, the valve element 26 is in turn moved or pressed upward against the valve seat 28 via the piston rod 22 and the valve stem 24, so the valve element 26 is ultimately brought into its closed position by the work of the piston 76 of the pressure accumulator 72.
  • the piston 76 When the pressure in the cavity 74 drops to ambient pressure, ie the pressure accumulator 72 is depressurized, the piston 76 reaches its extreme left position, which is defined by the fact that the friction surface 87 on the end of the blocking rod 86 facing away from the piston 76 against the friction surface 25 presses on the valve stem 24 of the valve element 26.
  • the spring travel of the spiral spring 84 is selected such that the spiral spring 84 is not completely relaxed, even in this position of the piston 76 of the pressure accumulator 72, so that it still exerts a force on the piston 76.
  • the length of the blocking rod 86 is in turn selected such that when its friction surface 87 abuts the friction surface 25 of the valve stem 24, the piston 76 does not yet come into contact with the boundary wall of the cavity 74 on the left in FIG. 2. Ultimately, the friction surface 87 of the blocking rod 86 is pressed by the spiral spring 84 against the friction surface 25 on the valve stem 24, and thereby a frictional connection between these two elements is established.
  • Gas exchange valve device 10 a comparatively low hydraulic force is required to move the piston 20 of the hydraulic cylinder 16.
  • FIG. 3 in which a region of a second exemplary embodiment of a gas exchange valve device 10 is shown.
  • Such parts whose function is equivalent to the elements shown in Figures 1 and 2, have the same reference numerals. It will not be discussed in detail again.
  • the axial position of the annular groove 25 in the valve stem 24 is selected such that when the tip 87 of the blocking rod 86 engages in the annular groove 25 in the valve stem 24, the inlet valve 12 is not completely closed, but is slightly opened. This means, that the valve element 26 is lifted off the valve seat 28.
  • the annular groove 25 is positioned in the valve stem 24 such that the opening stroke h of the valve element 26 is approximately 0.5 is up to 1.0 mm.
  • the gas exchange valve device does not include a separate pressure accumulator for vibration damping.
  • the vibration damping function is integrated in the pressure accumulator that blocks the valve element in the depressurized state. This is achieved by the fact that the pretensioning device present in this works in two stages: in a harder area of the pretensioning device it provides the vibration damping function, in a softer area the emergency pressure and blocking function. For example, two springs with different stiffness can be connected in series.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

La présente invention concerne un système de soupape d"échange gazeux (10) destiné à un moteur à combustion interne (14) appartenant notamment à une automobile, ledit système comprenant un dispositif hydraulique (15). Ledit dispositif hydraulique comprend un circuit hydraulique (38, 42, 46, 54), un accumulateur hydraulique (62, 72) relié au circuit hydraulique (38, 42, 46, 54) et comprenant un piston (66, 76) précontraint par un système (68, 84), ainsi qu"un système d"actionnement commandé (16). Le système de l"invention comprend également une soupape d"échange gazeux (12) dont l"élément de soupape (26) est soumis à l"action du système d"actionnement (16). Afin de simplifier la conception du système de soupape d"échange gazeux (10), l"accumulateur hydraulique (72) est disposé de sorte que son piston (76), dans un état sensiblement non pressurisé de l"accumulateur hydraulique (72), bloque au moins indirectement l"élément de soupape (26) de la soupape d"échange gazeux (12) dans une position sensiblement fermée.
EP02708247A 2001-02-19 2002-02-14 Systeme de soupape d'echange gazeux pour moteur a combustion interne Expired - Lifetime EP1364108B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10107698A DE10107698C1 (de) 2001-02-19 2001-02-19 Gaswechselventileinrichtung für eine Brennkraftmaschine
DE10107698 2001-02-19
PCT/DE2002/000522 WO2002066796A1 (fr) 2001-02-19 2002-02-14 Systeme de soupape d"echange gazeux pour moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1364108A1 true EP1364108A1 (fr) 2003-11-26
EP1364108B1 EP1364108B1 (fr) 2006-03-15

Family

ID=7674558

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02708247A Expired - Lifetime EP1364108B1 (fr) 2001-02-19 2002-02-14 Systeme de soupape d'echange gazeux pour moteur a combustion interne

Country Status (5)

Country Link
US (1) US6848400B2 (fr)
EP (1) EP1364108B1 (fr)
JP (1) JP2004518845A (fr)
DE (2) DE10107698C1 (fr)
WO (1) WO2002066796A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7004122B2 (en) * 2002-05-14 2006-02-28 Caterpillar Inc Engine valve actuation system
US6907851B2 (en) 2002-05-14 2005-06-21 Caterpillar Inc Engine valve actuation system
DE10306456B4 (de) * 2003-02-17 2006-11-30 Robert Bosch Gmbh Stellvorrichtung zur elektrohydraulischen Betätigung von Gaswechselventilen einer Brennkraftmaschine
DE10310300A1 (de) * 2003-03-10 2004-09-23 Robert Bosch Gmbh Verfahren zum Betreiben eines hydraulischen Aktors, insbesondere eines Gaswechselventils einer Brennkraftmaschine
EP1520962A1 (fr) * 2003-10-02 2005-04-06 Ford Global Technologies, LLC, A subsidary of Ford Motor Company Système de controle variable de soupape et procédé de controle variable de soupape de moteur à combustion interne
DE102006018588A1 (de) * 2006-04-21 2007-10-25 Schaeffler Kg Ventilbetätigungseinrichtung, insbesondere für Gaswechselventile von Hubkolbenbrennkraftmaschinen
WO2008156913A2 (fr) * 2007-05-11 2008-12-24 Lawrence Livermore National Security, Llc Moteur harmonique
EP2063075A1 (fr) 2007-11-23 2009-05-27 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Commande de soupape entraînée par fluide
JP4831839B2 (ja) * 2008-03-27 2011-12-07 三菱重工業株式会社 エンジンバルブアクチュエータ及び内燃機関
DE102008027650A1 (de) * 2008-06-10 2009-12-17 Man Diesel Se Ventilsteuerung für ein Gaswechselventil in einer Brennkraftmaschine
SE546024C2 (en) * 2022-07-11 2024-04-16 Freevalve Ab An apparatus comprising a plurality of tools, wherein each tool comprises at least one hydraulic chamber

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3739891A1 (de) * 1987-11-25 1989-06-08 Porsche Ag Vorrichtung zum betaetigen eines gaswechsel-tellerventils
US6308690B1 (en) * 1994-04-05 2001-10-30 Sturman Industries, Inc. Hydraulically controllable camless valve system adapted for an internal combustion engine
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
US6223846B1 (en) * 1998-06-15 2001-05-01 Michael M. Schechter Vehicle operating method and system
DE19935871C2 (de) * 1999-07-30 2003-02-13 Daimler Chrysler Ag Vorrichtung mit zumindest einem elektromagnetischen Aktuator zum Betätigen eines Gaswechselventils und ein Verfahren zu deren Betreibung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO02066796A1 *

Also Published As

Publication number Publication date
EP1364108B1 (fr) 2006-03-15
WO2002066796A1 (fr) 2002-08-29
JP2004518845A (ja) 2004-06-24
DE50206078D1 (de) 2006-05-11
DE10107698C1 (de) 2002-08-22
US20040035378A1 (en) 2004-02-26
US6848400B2 (en) 2005-02-01

Similar Documents

Publication Publication Date Title
DE112006002365B4 (de) Hydrauliksystem für die Steuerung zweier Aktuatoren und Getriebe mit einem solchen
DE10101584A1 (de) Druckspeicher zur Druckbeaufschlagung einer Hydraulikvorrichtung, mit der vorzugsweise ein Gaswechselventil einer Brennkraftmaschine betätigt wird
DE19744337A1 (de) Vorgesteuertes Druckbegrenzungsventil
DE10107698C1 (de) Gaswechselventileinrichtung für eine Brennkraftmaschine
AT519932B1 (de) Ablassventil für hohe Drücke
DE102012208307A1 (de) Dämpfungsvorrichtung
DE102006005621A1 (de) Anschlagfeder für ein Kolben-Zylinderaggregat
DE3330314C1 (de) Druckluftbetriebener Starter
DE102015108521B4 (de) Zylindereinheit
EP0976948B1 (fr) Dispositif d'amortissement de masses déplacées, en particulier pour systèmes moteurs électromagnétiques
DE2226610B2 (de) Speicherladeventil
DE102014208879A1 (de) Parksperrenaktuator für eine hydraulisch betätigbare Parksperre eines Kraftfahrzeug-Automatgetriebes
EP0502241B1 (fr) Poussoir à rattrapage de jeu hydraulique pour commande de soupape
DE102012004921A1 (de) Hydraulische Verstellvorrichtung mit Notschließfunktion und Zylinder dafür
DE102018110030B4 (de) Hydraulische Spannvorrichtung für einen Kettentrieb
DE3207995A1 (de) Hyraulischer zylinder und kolben mit automatischem kolbenventil
DE102015225858A1 (de) Schaltventil, insbesondere für ein Hydrauliksystem
EP3085921A1 (fr) Soupape d'inversion et bielle comprenant une soupape d'inversion
DE102015111273A1 (de) Hydraulikventil und Pleuel mit einem Hydraulikventil
DE4422879B4 (de) Vordruckventil
DE102019107710A1 (de) Schaltvorrichtung für ein Kraftübertragungselement eines Kraftfahrzeugs
AT521675B1 (de) Hydraulisches Steuerventil für eine längenverstellbare Pleuelstange mit zwei stirnseitigen Steuerkolben
DE102010038078B4 (de) Hydraulische Parksperre und Verfahren zum Schalten einer solchen
DE102015221515B4 (de) Ventilanordnung zur Begrenzung von Druckspitzen in einem Hydrauliksystem eines Automatikgetriebes
DE112004000191B4 (de) Antrieb für ein Turbinenventil

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: 20030919

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

RIN1 Information on inventor provided before grant (corrected)

Inventor name: REIMER, STEFAN

Inventor name: BEUCHE, VOLKER

Inventor name: GROSSE, CHRISTIAN

Inventor name: SCHIEMANN, JUERGEN

Inventor name: WALTER, RAINER

Inventor name: MISCHKER, KARSTEN

Inventor name: DIEHL, UDO

Inventor name: GAESSLER, HERMANN

17Q First examination report despatched

Effective date: 20050317

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 50206078

Country of ref document: DE

Date of ref document: 20060511

Kind code of ref document: P

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20060628

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20061218

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20070221

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20070418

Year of fee payment: 6

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20070216

Year of fee payment: 6

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20080214

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20081031

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080902

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080229

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080214