EP2375014B1 - Dispositif de réglage d'un arbre à cames avec une soupape hydraulique - Google Patents

Dispositif de réglage d'un arbre à cames avec une soupape hydraulique Download PDF

Info

Publication number
EP2375014B1
EP2375014B1 EP11157216.0A EP11157216A EP2375014B1 EP 2375014 B1 EP2375014 B1 EP 2375014B1 EP 11157216 A EP11157216 A EP 11157216A EP 2375014 B1 EP2375014 B1 EP 2375014B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic valve
port
switching position
opening
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11157216.0A
Other languages
German (de)
English (en)
Other versions
EP2375014A1 (fr
Inventor
Andreas Knecht
Dirk Pohl
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.)
Hilite Germany GmbH
Original Assignee
Hilite Germany 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 Hilite Germany GmbH filed Critical Hilite Germany GmbH
Publication of EP2375014A1 publication Critical patent/EP2375014A1/fr
Application granted granted Critical
Publication of EP2375014B1 publication Critical patent/EP2375014B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven oil control valves
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values

Definitions

  • the invention relates to a Schwenkmotornockenwellenversteller with a hydraulic valve according to the preamble of claim 1.
  • the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 already relate to a Schwenkmotornockenwellenversteller with a hydraulic valve, which has two working ports. These two working ports each have axially adjacent to each other a standard opening and an opening for utilizing pressure peaks due to camshaft alternating torques.
  • a hydraulic pressure can be conducted from a supply connection to the work connection to be loaded, while the work connection to be relieved is guided to a tank connection.
  • the hydraulic valve is designed as a 4/3-way valve in cartridge design.
  • In the sleeve check valves are used on the inside, which are designed as band-shaped rings. By means of these check valves camshaft alternating torques are used to adjust the camshaft adjuster particularly fast or with a relatively low oil pressure can.
  • the check valves cover the openings for the use of pressure peaks due to camshaft alternating torques.
  • the object of the invention is to provide a simple to be controlled with little effort Schwenkmotornockenwellenversteller.
  • the camshaft alternating torques for fast phasing of the camshaft can be used in the invention Schwenkmotornockenwellenversteller. Moreover, due to the use of camshaft alternating torques, it is advantageously possible to enable adjustment with a relatively low oil pressure. A thus possible small dimensions of the oil pump improves the efficiency of the internal combustion engine. The saved volume flow of hydraulic fluid is different Consumers, such as a hydraulic valve lift adjustment available.
  • Pivot camshaft phasors have also recently been applied to the combustion engines with fewer cylinders to reduce fuel consumption, increase performance, and reduce exhaust emissions.
  • the smaller the number of cylinders the greater the fluctuations of the Nockwellen dockmomente.
  • the hydraulic valve is proportional to a first switching position adjustable in which the effect of check valves for the use of camshaft alternating torques is bypassed. Due to the proportional controllability of the control process between use of the camshaft alternating torques and circumvention of this use is continuously controlled.
  • the hydraulic valve is additionally adjustable in favor of a higher control quality in a switching position to bypass the use of camshaft alternating torque.
  • Fig. 1 shows in a circuit diagram a by means of an electromagnet 17 against a spring force of a spring 21 operable hydraulic valve 3, which is controlled proportionally.
  • a Schwenkmotornockenwellenversteller 4 is pivotable.
  • the angular position between the crankshaft and the camshaft is changed during operation of an internal combustion engine.
  • the opening and closing times of the gas exchange valves are shifted so that the internal combustion engine brings its optimal performance at the respective speed.
  • the Schwenkmotornockenwellenversteller 4 allows a continuous adjustment of the camshaft relative to the crankshaft.
  • a first consumer port A and a second consumer port B go to the Schwenkmotornockenwellenversteller 4 from.
  • the hydraulic valve 3 has four ports and five shift positions and can thus also be referred to as a 4/5-way valve with a locking middle position 7.
  • the hydraulic valve 3 is in one of the two switching positions 16, 19, which are represented by the two switch box behind the locking center position 7.
  • the hydraulic valve is in the switch position 19 of the switch box at the very rear.
  • pressure chambers 6 associated with this direction of rotation 1 are acted upon by the first consumer port A by a pressure which comes from a supply port P.
  • the pressure chambers 5 assigned to the second - ie opposite - direction of rotation 2 are relieved to the second consumer connection B.
  • the second consumer port B is guided to a tank 20 via a tank connection T.
  • the adjustment of the camshaft takes place with use of the camshaft alternating torques.
  • an outermost switching position 18 similar to the immediately adjacent switching position 15 is executed.
  • a volume flow from the hydraulic fluid coming from a check valve RSV-A assigned to the first supply connection A is made available to the supply connection P.
  • the other outermost switching position 19 is similar to the immediately adjacent switching position 16 executed.
  • a volume flow of hydraulic fluid coming from a check valve RSV-B assigned to the second supply connection B is made available to the supply connection P.
  • This additional volume flow from the load connection A or B to be relieved is fed into the volume flow coming from an oil pump 12 at the supply connection P.
  • the supply port P leads via a pump check valve RSV-P to the oil pump 12, which applies the pressure for adjusting the Schwenkmotornockenwellenverstellers 4.
  • This pump check valve RSV-P blocks the pressures in the hydraulic valve 3 so that peak pressures coming from the load connection A or B to be relieved can be made available to a larger proportion of the adjustment assistance than is the case with an open oil pump line 14a, 14b would.
  • Fig. 2 to Fig. 6 show a constructive embodiment of the hydraulic valve 3 in the five switching positions 18, 15, 7, 16, 19 according to Fig. 1 ,
  • Fig. 2 shows the hydraulic valve 3 in the first switching position 18, in which the electromagnet 17 according to Fig. 1 a hollow piston 22 of the hydraulic valve 3 does not move.
  • the stroke of the piston 22 is thus at zero.
  • the piston 22 is displaceable within a bushing 27 against the force of the spring designed as a helical compression spring 21.
  • the electromagnet 17 facing the front end is closed to produce a contact surface for an actuating plunger of the electromagnet 17, whereas the other end face for the realization of the tank port T is open.
  • the piston 22 has at its two ends outer webs 23, 24, which are guided relative to the bushing 27.
  • the two outer webs 23, 24 are pierced by transverse bores 29, 30, so that from these transverse bores 29, 30 via the interior of the hollow piston 22 access to the tank port T is present.
  • two narrow ribs 31, 32 are provided, which rotate around the piston 22.
  • These circumferential ribs 31, 32 correspond to two annular webs 33, 34 extending radially inwardly from the bush 27.
  • two axially outer annular webs 35, 36 are provided.
  • These four ring lands 33 to 26 are formed, since five inner ring grooves 37 to 41 are turned out of the socket. In this five réelleringnuten 37 to 41 five connection holes, which are drilled through the wall of the socket 27 open.
  • the axially inner openings A2, B2 for provided a camshaft alternating torque use.
  • the axially inner openings A2, B2 have the band-shaped check valves RSV-A, RSB-B.
  • one of the band-shaped check valves RSV-A and RSB-B is inserted into an inner annular groove 25 and 26 radially inside the axially inner openings A2 and B2 of the bush 27.
  • band-shaped pump check valve RSV-P is still provided in an inner annular groove 28.
  • This pump check valve RSV-P has basically the same structure as the two check valves RSV-A, RSV-B. However, this pump check valve RSV-P may have a different response force.
  • the other two check valves RSV-A and RSV-B block the openings A2 and B2 against pressures from the supply port P and from the the second working port B associated standard opening B1.
  • short-term peak pressures due to the camshaft alternating torques from the first working port A associated opening A2 through its check valve RSV-A.
  • the first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
  • the hydraulic valve 3 is in the switching position 15.
  • the rear rib 32 covers the corresponding annular land 34 so far that a flow through the very narrow gap is possible only with increased flow resistance.
  • the very slightly biased check valve RSV-A has a flow resistance, it is the short-term peak pressures due to camshaft alternating torques not possible to get from the first working port A to the second working port B.
  • the first working port A is guided or relieved via its standard opening A1 and the transverse bore 30 to the tank port T.
  • the hydraulic valve 3 is in the locking center position 7.
  • the supply port P is closed by the two ribs 31, 32.
  • the ribs 31, 31 cover the corresponding annular webs 33, 34 in a correspondingly large extent.
  • the two working connections A, B are blocked against the tank drain T.
  • both transverse bores 29, 30 are located axially outside the axially outer inner annular grooves 37, 41.
  • the hydraulic valve 3 is in the switching position 16.
  • coming from the supply port P hydraulic fluid through the gap between the rear rib 32 and the corresponding ring land 34 to the standard opening A1 of the first working port A pass.
  • the front rib 31 covers the corresponding annular web 33 so far that a flow through the very narrow Gap is only possible with increased flow resistance.
  • the very slightly biased check valve RSV-B has a flow resistance, it is the short-term peak pressures due to camshaft alternating torques not possible to get from the second working port B to the first working port A.
  • the second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
  • the two middle ribs 31, 32 axially spaced from the two annular ridges 33, 34, so that hydraulic fluid can pass through the gaps between them.
  • hydraulic fluid can pass through the gap between the rearmost outer web 24 and the corresponding annular web 36.
  • the other outer web 23 blocks the foremost inner annular groove 37 and the standard opening B1 of the second working port B for this purpose.
  • the outer web 23 and the foremost annular web 35 overlap over a large sealing length. In this way, in this switching position 19 hydraulic fluid can reach from the supply connection P via the pump check valve RSV-P to the standard opening A1 of the first working connection A.
  • the other two check valves RSV-A and RSV-B block the openings A2 and B2 against pressures from the supply port P and from the standard opening B1 of the second working port B.
  • short-term peak pressures due to the camshaft alternating torques from the opening B2 of the second working port B by the Check valve RSV-B let through.
  • the second working port B is guided or relieved via its standard opening B1 and the transverse bore 29 to the tank port T.
  • the standard opening A1 or B1 and the opening A2 or B2 are summarized for use of camshaft alternating moments only outside the bushing 27 to the working port A and B respectively.
  • an annular groove can be incorporated radially outside into the socket.
  • ball check valves may be used instead of band check valves.
  • the ball check valves need not necessarily be installed in the socket of a cartridge valve. It is also possible, for example, to use the ball check valves in a rotor and run the piston as a central valve which is arranged coaxially and centrally within the rotor hub slidably.
  • screens may also be provided in the direction of flow in front of one or more or even all ports, which protect the running surfaces between the piston and the bushing.
  • the hydraulic valve can also find application in a so-called central valve.
  • the socket is not directly connected to the magnetic part. Instead, the hydraulic valve is centrally located in the rotor of the Schwenkmotornockenwellenverstellers so that the sleeve rotates together with the piston.
  • the magnet is rotationally fixed relative to the cylinder head arranged, so that a relative movement between the plunger of the magnetic member and the piston takes place.
  • camshaft alternating torques does not have to be provided for both directions of rotation. It is also possible to dispense with one of the two axially outermost switching position 18 or 19. As a result, the camshaft alternating torques can then be used directly for faster adjustment only for the one direction of rotation.
  • a use of the camshaft alternating torques can be provided for both directions, but then to one of the two check valves RSV-A, RSV-B bypassing switch positions 15, 16 is omitted.
  • a further switching position in which both working ports A, B are relieved against the tank port T, so that a so-called center locking is made possible.
  • a locking bolt is provided in the Schwenkmotornockenwellenversteller, which fixes the rotor in an angular position against the stator, which is not an end position.
  • Such a central locking is for example in the DE 10 2004 039 800 B4 and the not pre-published DE 10 2009 022 869.1-13 shown.

Landscapes

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

Claims (6)

  1. Dispositif de réglage d'arbre à cames de moteur oscillant (4) avec une soupape hydraulique (3) comportant deux raccords de travail (A, B) comportant respectivement dans le plan axial, à proximité l'une de l'autre, une ouverture standard (A1 et/ou B1) et une ouverture (A2 et/ou B2) permettant d'exploiter les crêtes de pression dues aux moments alternés d'arbre à cames, une pression hydraulique d'un raccord d'alimentation (P) pouvant être amenée au raccord de travail (A et/ou B) à charger, tandis que le raccord de travail (B et/ou A) à décharger est conduit à un raccord de réservoir (T), caractérisé en ce qu'une position de connexion (16 et/ou 15) de la soupape hydraulique (3) peut être excitée de façon proportionnelle, les crêtes de pression du raccord de travail (B et/ou A) à décharger étant bloquées par rapport au raccord de travail (A et/ou B) à charger dans ladite position.
  2. Dispositif de réglage d'arbre à cames de moteur oscillant avec une soupape hydraulique selon la revendication 1, caractérisé en ce qu'en partant d'une position moyenne de blocage (7) de la soupape hydraulique (3), la première position de connexion (16 et/ou 15) peut être excitée d'abord, suivie d'une autre position de connexion (19 et/ou 18) permettant d'exploiter les moments alternés d'arbre à cames.
  3. Dispositif de réglage d'arbre à cames de moteur oscillant avec une soupape hydraulique selon la revendication 2, caractérisé en ce que la soupape hydraulique (3) comporte un piston (22) guidé à l'intérieur d'une douille (27) et deux étais extérieurs (23, 24) servant à bloquer les deux ouvertures standard (A1, B1), deux nervures (31, 32) étant prévues dans le plan axial entre ces étais extérieurs (23, 24), à l'aide desquelles, d'une part, le raccord d'alimentation (P) peut être bloqué contre les deux raccords de travail (A, B) dans la position moyenne de blocage (7) et, d'autre part, la première ouverture (B2 et/ou A2) permettant d'exploiter les crêtes de pression dues aux moments alternés d'arbre à cames peut être bloquée contre le raccord d'alimentation (P) dans la première position de connexion (16 et/ou 15), d'où la pression hydraulique est amenée à l'autre ouverture (A2 et/ou B2) conduisant à l'ouverture standard (A1 et/ou B1) bloquée par une soupape de retenue (RSV-A et/ou RSV-B).
  4. Dispositif de réglage d'arbre à cames de moteur oscillant avec une soupape hydraulique selon la revendication 3, caractérisé en ce que l'ouverture standard (B1) du raccord de travail (B) à décharger est bloquée dans la première position de connexion (16 et/ou 15) contre l'ouverture (B2) du même raccord de travail (B) à l'aide de l'étai extérieur (23 et/ou 24).
  5. Dispositif de réglage d'arbre à cames de moteur oscillant avec une soupape hydraulique selon la revendication 4, caractérisé en ce que l'étai extérieur (23 et/ou 24) comporte un alésage transversal (29 et/ou 30) guidant le fluide hydraulique de l'ouverture standard (B1) du raccord de travail (B) à décharger dans la première position de connexion (16 et/ou 15) jusqu'au raccord de réservoir (T), par le biais du piston (22) prenant une forme creuse.
  6. Dispositif de réglage d'arbre à cames de moteur oscillant avec une soupape hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que dans ladite position de connexion (16 et/ou 15) pouvant être excitée de façon proportionnelle, les crêtes de pression du raccord de travail (B et/ou A) à décharger sont bloquées par rapport au raccord de travail (A et/ou B) à charger et au raccord d'alimentation (P).
EP11157216.0A 2010-04-10 2011-03-07 Dispositif de réglage d'un arbre à cames avec une soupape hydraulique Active EP2375014B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010014500 2010-04-10
DE102010045358A DE102010045358A1 (de) 2010-04-10 2010-09-14 Schwenkmotornockenwellenversteller mit einem Hydraulikventil

Publications (2)

Publication Number Publication Date
EP2375014A1 EP2375014A1 (fr) 2011-10-12
EP2375014B1 true EP2375014B1 (fr) 2013-07-10

Family

ID=44504309

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11157216.0A Active EP2375014B1 (fr) 2010-04-10 2011-03-07 Dispositif de réglage d'un arbre à cames avec une soupape hydraulique

Country Status (5)

Country Link
US (1) US8662040B2 (fr)
EP (1) EP2375014B1 (fr)
JP (1) JP6025134B2 (fr)
CN (1) CN102213120B (fr)
DE (1) DE102010045358A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017106938A1 (de) 2017-03-31 2018-10-04 ECO Holding 1 GmbH Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009050779B4 (de) 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller mit einer Reibscheibe und Montageverfahren
DE102009054055A1 (de) * 2009-11-20 2011-05-26 Schaeffler Technologies Gmbh & Co. Kg Schaltbare Vorrichtung zur Druckversorgung
US9080473B2 (en) 2010-11-02 2015-07-14 Borgwarner, Inc. Cam torque actuated—torsional assist phaser
DE102010061337B4 (de) * 2010-12-20 2015-07-09 Hilite Germany Gmbh Hydraulikventil für einen Schwenkmotorversteller
JP5447543B2 (ja) * 2012-01-26 2014-03-19 株式会社デンソー バルブタイミング調整装置、およびその組付方法
DE102012201566B4 (de) * 2012-02-02 2017-05-18 Schaeffler Technologies AG & Co. KG Anordnung eines Volumenspeichers im Nockenwellenversteller
US10156164B2 (en) 2012-02-02 2018-12-18 Schaeffler Technologies AG & Co. KG Arrangement of a volume accumulator in a camshaft adjuster
CN102705029B (zh) * 2012-05-30 2014-12-10 绵阳富临精工机械股份有限公司 一种凸轮相位器
EP2796673B1 (fr) 2013-04-22 2018-03-07 Hilite Germany GmbH Soupape centrale pour un moteur pivotant à l'ajustage
DE102013104051B4 (de) 2013-04-22 2016-09-22 Hilite Germany Gmbh Zentralventil für einen Schwenkmotorversteller
DE102013104031B4 (de) 2013-04-22 2017-10-05 Hilite Germany Gmbh Zentralventil für einen Schwenkmotorversteller
DE102013107127A1 (de) 2013-07-05 2015-01-08 Hilite Germany Gmbh Pleuel für eine zweistufige variable Verdichtung
US9341090B2 (en) * 2014-02-06 2016-05-17 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US20160097605A1 (en) * 2014-10-07 2016-04-07 Spx Corporation Hydraulic Closure Unit and Retrofit System for a Plate Heat Exchanger
DE102016210177B4 (de) 2015-07-08 2022-03-31 Ford Global Technologies, Llc Variable Nockenwellensteuervorrichtung
DE102016107986A1 (de) * 2015-11-04 2017-05-04 Hilite Germany Gmbh Hydraulikventil und Pleuel mit einem Hydraulikventil
DE102016118962A1 (de) * 2016-10-06 2018-04-12 Denso Corporation Nockenwellensteller und zugehöriger Schaltkörper
JP6690633B2 (ja) 2017-01-19 2020-04-28 株式会社デンソー バルブタイミング調整装置およびチェック弁
WO2018135584A1 (fr) * 2017-01-19 2018-07-26 株式会社デンソー Dispositif d'ajustage du réglage de distribution et clapet de non-retour
US10113451B2 (en) 2017-03-28 2018-10-30 ECO Holding 1 GmbH Hydraulic valve for a cam phaser
JP6780573B2 (ja) * 2017-04-21 2020-11-04 株式会社デンソー バルブタイミング調整装置
EP3399168B1 (fr) * 2017-05-04 2020-09-16 ECO Holding 1 GmbH Bielle pour un moteur à combustion interne à compression variable avec module hydraulique pourvu d'une soupape d'inversion permettant de commander un flux de fluide hydraulique
DE102017121236A1 (de) * 2017-05-04 2018-11-08 ECO Holding 1 GmbH Hydraulikmodul mit einem Umschaltventil zum Steuern eines Hydraulikflüssigkeitsstroms eines Pleuels für eine Brennkraftmaschine mit variabler Verdichtung sowie Pleuel
EP3530891B1 (fr) 2018-02-21 2021-03-03 ECO Holding 1 GmbH Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
DE102019101159A1 (de) 2018-02-21 2019-08-22 ECO Holding 1 GmbH Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle
EP3530892B1 (fr) 2018-02-21 2021-05-19 ECO Holding 1 GmbH Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
US10883616B2 (en) * 2019-02-06 2021-01-05 ECO Holding 1 GmbH Control valve for cam phaser and method for mounting the control valve
CN112302752A (zh) * 2019-07-25 2021-02-02 句容嘉晟汽车配件有限公司 一种vvt系统

Family Cites Families (141)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2649105A (en) 1953-08-18 Self-draining pipe joint
DE135322C (fr) 1900-01-01
US894286A (en) 1908-04-10 1908-07-28 Frederick C Reineking Air-intake regulator for carbureters.
FR525481A (fr) 1920-10-01 1921-09-22 Alphonse Papin Soupape à ruban
US1746855A (en) 1926-03-17 1930-02-11 Louis O French Valve
US1860163A (en) 1930-04-21 1932-05-24 Binks Mfg Co Valve assembly for air-compressing cylinders
FR966121A (fr) 1948-05-10 1950-10-02 Dirupteur-distributeur d'allumage
FR996121A (fr) 1949-08-09 1951-12-13 Paul Duclos Ets Soupape à lames
US2781059A (en) 1954-01-08 1957-02-12 Gen Motors Corp Flow control device
US2918941A (en) 1957-12-02 1959-12-29 Orenda Engines Ltd Pressure relief blow-out device
GB1212327A (en) 1969-06-25 1970-11-11 Freital Plastmaschinen Improvements in or relating to hydraulic circuits for drives of processing machines
DE2025168A1 (de) 1970-05-23 1971-12-02 Bosch Gmbh Robert Rückschlagventil für flüssige oder gasförmige Medien
US3783590A (en) 1970-07-09 1974-01-08 A Allen Filter-silencer for pneumatic devices
DE2043002A1 (de) 1970-08-29 1972-03-02 Ishkewich M Druck und Saugventil
US3779669A (en) 1972-05-22 1973-12-18 Wooster Brush Co Pump spray unit
US3882891A (en) 1974-06-19 1975-05-13 Abex Corp Check valve
US4051864A (en) 1975-10-21 1977-10-04 Gould Inc. Flow regulator
DE2757490C3 (de) 1977-12-22 1980-09-11 1000 Berlin Druckventil
JPS5578150A (en) 1978-12-06 1980-06-12 Nissan Motor Co Ltd Exhaust gas return control device for internal conbustion engine
JPS582490A (ja) 1981-06-29 1983-01-08 Sanden Corp スクロ−ル型圧縮機
GB2161583B (en) 1984-07-10 1988-01-27 Prestcold Ltd Reed valve
DE3601643A1 (de) 1986-01-21 1987-07-23 Schrupp Gmbh Hydraulische steuervorrichtung fuer den schnellgang von verbrauchern
DE3616234A1 (de) 1986-05-14 1987-11-19 Bayerische Motoren Werke Ag Vorrichtung zur relativen drehlagenaenderung zweier in antriebsverbindung stehender wellen, insbesondere zwischen in einem maschinengehaeuse einer brennkraftmaschine gelagerten kurbelwelle und nockenwelle
DE3800761A1 (de) 1987-01-14 1988-07-28 Nippon Abs Ltd Blockierschutzvorrichtung fuer fahrzeugbremsanlagen
DE3829698A1 (de) 1987-09-05 1989-03-16 Zahnradfabrik Friedrichshafen Kolbenpumpe, insbesondere radialkolbenpumpe
FR2641832B1 (fr) 1989-01-13 1991-04-12 Melchior Jean Accouplement pour la transmission de couples alternes
DE4024057C1 (fr) 1990-07-28 1991-09-19 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
US5323806A (en) 1992-03-26 1994-06-28 Matsushita Electric Works, Ltd. Constant-speed exhaust valve device for hemadynamometer
DE4210580C2 (de) 1992-03-31 2001-06-28 Bosch Gmbh Robert Vorrichtung zur Winkelverstellung der Nockenwelle einer Brennkraftmaschine
DE4235929C2 (de) 1992-10-23 2000-08-24 Mannesmann Rexroth Ag Zylinderverstellung
DE4422742C2 (de) 1994-06-29 1997-02-06 Rexroth Mannesmann Gmbh Hydraulisches Wegeventil, das insbesondere von einem Proportionalmagneten betätigbar ist
US5657725A (en) 1994-09-15 1997-08-19 Borg-Warner Automotive, Inc. VCT system utilizing engine oil pressure for actuation
DE19525837A1 (de) 1995-07-15 1997-01-16 Schaeffler Waelzlager Kg Vorrichtung zum Verändern der Steuerzeiten einer Brennkraftmaschine
US5797361A (en) 1996-04-03 1998-08-25 Toyota Jidosha Kabushiki Kaisha Variable valve timing mechanism for internal combustion engine
KR100242589B1 (ko) 1996-04-04 2000-03-02 와다 아끼히로 내연기관의 가변밸브 타이밍기구
US5979380A (en) 1996-07-23 1999-11-09 Aisin Seiki Kabushiki Kaisha Valve timing control device
JPH10110691A (ja) 1996-10-07 1998-04-28 Zexel Corp 吐出弁構造
JP3620684B2 (ja) 1997-01-31 2005-02-16 株式会社デンソー 内燃機関用バルブタイミング調整装置
JP3164007B2 (ja) 1997-02-14 2001-05-08 トヨタ自動車株式会社 内燃機関のバルブタイミング調整装置
JPH1150820A (ja) 1997-08-05 1999-02-23 Toyota Motor Corp 内燃機関のバルブタイミング制御装置
DE19756015A1 (de) * 1997-12-17 1999-06-24 Porsche Ag Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad
DE19756016A1 (de) 1997-12-17 1999-06-24 Porsche Ag Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad
JP4147435B2 (ja) 1998-01-30 2008-09-10 アイシン精機株式会社 弁開閉時期制御装置
US6234125B1 (en) 1998-03-30 2001-05-22 Aft Atlas Fahrzeugtechnik Gmbh Apparatus for angular adjustment of camshafts relative to crankshafts in combustion engines
JPH11280427A (ja) 1998-03-31 1999-10-12 Aisin Seiki Co Ltd 弁開閉時期制御装置
JP3918971B2 (ja) 1998-04-27 2007-05-23 アイシン精機株式会社 弁開閉時期制御装置
DE19823619A1 (de) 1998-05-27 1999-12-02 Porsche Ag Einrichtung zur relativen Drehlagenänderung einer Welle zum Antriebsrad
DE19844669B4 (de) 1998-09-29 2014-06-05 Linde Hydraulics Gmbh & Co. Kg Hydrostatisches Antriebssystem mit einer Regenerationseinrichtung
DE19847705A1 (de) 1998-10-16 2000-04-20 Schaeffler Waelzlager Ohg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
JP4013364B2 (ja) 1998-10-30 2007-11-28 アイシン精機株式会社 弁開閉時期制御装置
DE19853670C5 (de) 1998-11-20 2019-01-10 Hilite Germany Gmbh Einrichtung zur Nockenwellenverstellung
JP2000230511A (ja) 1998-12-07 2000-08-22 Mitsubishi Electric Corp ベーン式油圧アクチュエータ
US6267041B1 (en) 1999-12-15 2001-07-31 Caterpillar Inc. Fluid regeneration circuit for hydraulic cylinders
JP4207141B2 (ja) * 2000-06-09 2009-01-14 株式会社デンソー バルブタイミング調整装置
JP4802394B2 (ja) 2000-08-03 2011-10-26 アイシン精機株式会社 弁開閉時期制御装置
DE10050225A1 (de) 2000-10-11 2002-04-25 Hydraulik Ring Gmbh Betätigungseinrichtung zum Festlegen einer Nockenwelle eines Antriebsmotors eines Fahrzeuges, vorzugsweise eines Kraftfahrzeuges, in einer Startposition
JP4159241B2 (ja) 2000-11-30 2008-10-01 株式会社デンソー 内燃機関用バルブタイミング調整装置
US6453859B1 (en) 2001-01-08 2002-09-24 Borgwarner Inc. Multi-mode control system for variable camshaft timing devices
US20030033998A1 (en) 2001-08-14 2003-02-20 Marty Gardner Hybrid multi-position cam indexer having controls located in rotor
US6763791B2 (en) 2001-08-14 2004-07-20 Borgwarner Inc. Cam phaser for engines having two check valves in rotor between chambers and spool valve
DE10143433B4 (de) 2001-09-05 2013-09-26 Hilite Germany Gmbh Proportionalventil
DE10161701A1 (de) 2001-12-15 2003-06-18 Ina Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Einrichtung zur hydraulischen Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
DE10161698A1 (de) 2001-12-15 2003-06-26 Ina Schaeffler Kg Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine, insbesondere Einrichtung zur hydraulischen Drehwinkelverstellung einer Nockenwelle gegenüber einer Kurbelwelle
DE10205415A1 (de) 2002-02-09 2003-08-28 Porsche Ag Vorrichtung zur relativen Drehwinkelverstellung einer Nockenwelle einer Brennkraftmaschine zu einem Antriebsrad
DE10211468A1 (de) 2002-03-15 2003-09-25 Daimler Chrysler Ag Nockenwellenversteller für eine Brennkraftmaschine
DE10211467A1 (de) 2002-03-15 2003-09-25 Daimler Chrysler Ag Nockenwellerversteller
DE10213081A1 (de) 2002-03-20 2003-10-02 Hydraulik Ring Gmbh Ventilsteuerung zur Einstellung des Hubes von Ventilen in Kraftfahrzeugen
US6782856B2 (en) 2002-04-09 2004-08-31 Ford Global Technologies, Llc Camshaft accumulator
DE10216352A1 (de) 2002-04-13 2003-10-23 Hydraulik Ring Gmbh Ansteuereinrichtung für mindestens einen Verbraucher, wie Nockenwellenversteller, automatisches Getriebe und dergleichen, von Fahrzeugen, vorzugsweise Kraftfahrzeugen
DE10228354B4 (de) 2002-06-25 2017-06-22 Daimler Ag Vorrichtung zur Druckversorgung einer Nockenwellen-Verstelleinrichtung
JP4126600B2 (ja) 2002-09-26 2008-07-30 アイシン精機株式会社 弁開閉時期制御装置の制御機構
US6899199B2 (en) 2002-10-24 2005-05-31 Barnes Group Inc. Flapper finger valve assembly
GB0303571D0 (en) 2003-02-17 2003-03-19 Delphi Tech Inc Oil flow control valve for a cam phaser
WO2004088094A2 (fr) 2003-03-29 2004-10-14 Hydraulik-Ring Gmbh Dispositif de poussoir a soupape variable utilise pour ajuster les soupapes d'echange de gaz dans un moteur a combustion interne
DE10314683B4 (de) 2003-03-29 2009-05-07 Entec Consulting Gmbh Variable Ventilhubsteuerung für einen Verbrennungsmotor mit untenliegender Nockenwelle
EP1464793B1 (fr) 2003-04-02 2007-12-05 Renault s.a.s. Arbre à cames pour moteurs
DE10319831A1 (de) 2003-05-03 2004-11-18 Hydraulik-Ring Gmbh Buchse für ein Hydraulikventil
US6871621B2 (en) 2003-05-12 2005-03-29 Hydraulik-Ring Gmbh Camshaft adjuster for internal combustion engines of motor vehicles
DE10322394A1 (de) 2003-05-12 2004-12-02 Hydraulik-Ring Gmbh Nockenwellenversteller für Verbrennungskraftmaschinen von Kraftfahrzeugen
ITBO20030390A1 (it) 2003-06-23 2004-12-24 Magneti Marelli Powertrain Spa Metodo e dispositivo di controllo della velocita' delle valvole
DE10330449B3 (de) 2003-07-05 2005-02-24 Daimlerchrysler Ag Nockenwellenversteller
DE10334690B4 (de) 2003-07-30 2008-08-21 Böckmann-Hannibal, Angela, Dipl.-Ing. (FH) Einrichtung zur Nockenwellenverstellung für Verbrennungskraftmaschinen
DE10344916A1 (de) 2003-09-17 2005-04-21 Teamtechnik Maschinen Und Anla Bearbeitungsstation
DE10346443A1 (de) 2003-10-07 2005-05-04 Daimler Chrysler Ag Hydraulischer Nockenwellenversteller für eine Brennkraftmaschine
DE10346448B4 (de) 2003-10-07 2017-03-30 Daimler Ag Nockenwellenversteller für eine Brennkraftmaschine
DE10352255B4 (de) 2003-11-08 2017-03-09 Schaeffler Technologies AG & Co. KG Verstellvorrichtung zum Verstellen der relativen Drehwinkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine
DE102004038252A1 (de) 2004-05-14 2005-12-15 Ina-Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
JP4202297B2 (ja) 2004-05-20 2008-12-24 株式会社日立製作所 内燃機関のバルブタイミング制御装置
DE102004033522A1 (de) * 2004-07-10 2006-02-09 Ina-Schaeffler Kg Nockenwellenversteller mit elektrischem Antrieb
DE102004035077A1 (de) 2004-07-20 2006-02-16 Hydraulik-Ring Gmbh Verfahren zum Einstellen einer Nockenwellenverstelleinrichtung für Brennkraftmaschinen von Kraftfahrzeugen sowie Vorrichtung zur Durchführung des Verfahrens
DE102004039800B4 (de) 2004-08-17 2006-07-27 Hydraulik-Ring Gmbh Nockenwellenverstellsystem
DE102004049123A1 (de) * 2004-10-07 2006-04-13 Ina-Schaeffler Kg Vorrichtung zur Veränderung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
US7387097B2 (en) 2004-10-08 2008-06-17 Ina-Schaeffler Jg INA-schaeffler KG, industriestrasse 1-3, 91074 herzogenaurach ANR 12 88 48 20
US7124722B2 (en) 2004-12-20 2006-10-24 Borgwarner Inc. Remote variable camshaft timing control valve with lock pin control
GB2421557B (en) 2004-12-23 2009-10-28 Mechadyne Plc Vane-type phaser
DE102005004281B3 (de) 2005-01-28 2006-01-05 Hydraulik-Ring Gmbh Nockenwellenversteller mit spielfreier Verriegelung
DE102005013085B3 (de) 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
DE102005034276A1 (de) 2005-07-22 2007-01-25 Daimlerchrysler Ag Nockenwellenstellvorrichtung
DE102005034275B4 (de) 2005-07-22 2018-02-15 Daimler Ag Nockenwellenstellventilvorrichtung
DE102005060111A1 (de) 2005-12-16 2007-07-05 Schaeffler Kg Nockenwellenverstellerzuleitung
DE602005007369D1 (de) 2005-12-23 2008-07-17 Delphi Tech Inc Verfahren und Vorrichtung zum Betrieb eines Öldurchflussregelventils
DE102006008532A1 (de) 2006-02-22 2007-08-30 Thyssenkrupp Automotive Ag Verfahren und Vorrichtung zur Fertigbearbeitung von gebauten Nocken- und Exzenterwellen
WO2007107426A1 (fr) * 2006-03-17 2007-09-27 Hydraulik-Ring Gmbh Circuit hydraulique, en particulier pour dispositif d'ajustement d'arbre a cames, et element de commande correspondant
DE102006012733B4 (de) 2006-03-17 2008-03-27 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
EP1996819B1 (fr) * 2006-03-17 2012-04-11 Hilite Germany GmbH Circuit hydraulique, destine en particulier a des dispositifs de reglage d'arbre a cames, et element de commande correspondant
DE102006012775B4 (de) 2006-03-17 2008-01-31 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
JP4484843B2 (ja) * 2006-04-28 2010-06-16 日立オートモティブシステムズ株式会社 内燃機関のバルブタイミング制御装置
DE102006022402A1 (de) 2006-05-13 2007-12-06 Schaeffler Kg Steuerventil für einen Nockenwellenversteller
GB2440157B (en) 2006-07-20 2011-01-19 Mechadyne Plc Variable phase mechanism
DE102006036052B4 (de) 2006-08-02 2018-03-08 Schaeffler Technologies AG & Co. KG Dichtblech für einen Nockenwellenversteller und Nockenwellenversteller mit einem Dichtblech
DE112007002915B4 (de) 2006-12-04 2020-10-29 Daimler Ag Verstelleinrichtung zur Phaseneinstellung einer Nockenwelle
GB2445570B (en) 2007-01-09 2011-04-06 Mechadyne Plc Rotary hydraulic coupling
DE102007007072A1 (de) * 2007-02-13 2008-08-14 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102007012967B4 (de) 2007-03-14 2009-01-08 Hydraulik-Ring Gmbh Ventil, insbesondere Cartridgeventil, mit integriertem Rückschlagsventil
WO2008140897A1 (fr) 2007-05-14 2008-11-20 Borgwarner Inc. Accumulateur monté sur came
DE102007026824A1 (de) 2007-06-06 2008-12-11 Muhr Und Bender Kg Verfahren zur Herstellung von Nocken für gebaute Nockenwellen
JP4858340B2 (ja) * 2007-07-18 2012-01-18 トヨタ自動車株式会社 可変動弁装置の制御装置
WO2009010332A1 (fr) 2007-07-18 2009-01-22 Schaeffler Kg Élément d'une soupape de commande hydraulique
DE102007040017B4 (de) 2007-08-24 2020-09-17 Schaeffler Technologies AG & Co. KG Steuerzeitenstellvorrichtung für eine Brennkraftmaschine mit Fertigungsverfahren
US8104511B2 (en) 2007-08-27 2012-01-31 Parker Hannifin Corporation Sequential stepped directional control valve
DE102007041552A1 (de) 2007-08-31 2009-03-05 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
JP5011039B2 (ja) * 2007-09-07 2012-08-29 株式会社ケーヒン 電磁装置
DE102007053688A1 (de) 2007-11-10 2009-05-14 Schaeffler Kg Steuerventilanordnung für Nockenwellenversteller und mit dieser ausgerüsteter Nockenwellenversteller
JP4544294B2 (ja) 2007-11-28 2010-09-15 株式会社デンソー バルブタイミング調整装置
DE102007058491A1 (de) 2007-12-05 2009-06-10 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
JP4518149B2 (ja) * 2008-01-10 2010-08-04 株式会社デンソー バルブタイミング調整装置
DE102008005277A1 (de) 2008-01-19 2009-07-23 Schaeffler Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
EP2093388B1 (fr) 2008-02-19 2014-10-08 hofer mechatronik GmbH Déphaseur d'arbre à cames de moteur à combustion interne
JP2009236045A (ja) 2008-03-27 2009-10-15 Denso Corp バルブタイミング調整装置
DE102008036877B4 (de) * 2008-08-07 2019-08-22 Schaeffler Technologies AG & Co. KG Nockenwellenverstellvorrichtung für eine Brennkraftmaschine
DE102009034011B4 (de) 2008-10-07 2018-04-05 Schaeffler Technologies AG & Co. KG Druckspeicher zur Unterstützung der Druckmittelversorgung eines Nockenwellenverstellers einer Brennkraftmaschine
JP5126157B2 (ja) 2009-04-23 2013-01-23 株式会社デンソー 内燃機関の可変バルブタイミング制御装置
JP5240674B2 (ja) 2009-05-12 2013-07-17 株式会社デンソー 内燃機関の可変バルブタイミング制御装置
DE102009022869A1 (de) 2009-05-27 2010-12-09 Hydraulik-Ring Gmbh Flügelzellennockenwellenverstellersystem
DE102009030201A1 (de) * 2009-06-24 2010-12-30 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102009035233B3 (de) 2009-07-29 2011-03-31 Hydraulik-Ring Gmbh Flügelzellennockenwellenversteller mit einer Spiralfeder
DE102009050779B4 (de) 2009-10-27 2016-05-04 Hilite Germany Gmbh Schwenkmotornockenwellenversteller mit einer Reibscheibe und Montageverfahren
DE102010008001B4 (de) 2010-02-15 2022-03-10 Schaeffler Technologies AG & Co. KG Vorrichtung zur variablen Einstellung von Ventilerhebungskurven von Gaswechselventilen einer Brennkraftmaschine
JP2011196245A (ja) * 2010-03-19 2011-10-06 Denso Corp バルブタイミング調整装置
DE102010053685B4 (de) 2010-12-08 2014-10-30 Schwäbische Hüttenwerke Automotive GmbH Vorrichtung zur Verstellung der Drehwinkelposition einer Nockenwelle
US8225818B1 (en) 2011-03-22 2012-07-24 Incova Technologies, Inc. Hydraulic valve arrangement with an annular check valve element

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017106938A1 (de) 2017-03-31 2018-10-04 ECO Holding 1 GmbH Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle

Also Published As

Publication number Publication date
US8662040B2 (en) 2014-03-04
JP2011226474A (ja) 2011-11-10
DE102010045358A1 (de) 2011-10-13
CN102213120B (zh) 2013-06-05
JP6025134B2 (ja) 2016-11-16
US20110247576A1 (en) 2011-10-13
EP2375014A1 (fr) 2011-10-12
CN102213120A (zh) 2011-10-12

Similar Documents

Publication Publication Date Title
EP2375014B1 (fr) Dispositif de réglage d'un arbre à cames avec une soupape hydraulique
EP1025343B1 (fr) Dispositif de modification relative de la position en rotation d'un arbre par rapport au pignon d'entree
EP2466081B1 (fr) Soupape hydraulique d'un actionneur d'un déphaseur d'arbre à cames
DE60201949T2 (de) Nockenwellenverstellanordnung für eine Vierzylinderbrennkraftmaschine
EP2796674B1 (fr) Soupape central pour un moteur pivotant à l'ajustage
DE102010019004B4 (de) Schwenkmotorversteller mit einem Hydraulikventil
DE102010019005B4 (de) Schwenkmotorversteller
DE102004036096B4 (de) Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102013104051B4 (de) Zentralventil für einen Schwenkmotorversteller
DE102009022869A1 (de) Flügelzellennockenwellenverstellersystem
EP3219941A1 (fr) Vanne à tiroir pour un déphaseur d'arbre à cames à cellules en ailettes
EP2905434B1 (fr) Déphaseur oscillant doté d'une soupape hydraulique pour arbreà cames
DE102012210178B4 (de) Steuerventil eines Nockenwellenverstellers
DE102013104031B4 (de) Zentralventil für einen Schwenkmotorversteller
DE102010032133A1 (de) Zentralventil
WO2013087620A1 (fr) Soupape hydraulique
EP3015662B1 (fr) Soupape hydraulique et moteur oscillant
DE102012206562A1 (de) Nockenwellenversteller
EP2920436B1 (fr) Dephaseur à palettes radiales comprenant une vanne de commande electromagnétique
DE102012208808A1 (de) Steuerventil zur Steuerung von Druckmittelströmen eines Nockenwellenverstellers
EP3267012B1 (fr) Clapet anti-retour pour une bielle de moteur à combustion interne à compression variable
DE102011013046A1 (de) Nockenwellenversteller
DE102010038198A1 (de) Schwenkmotorversteller mit einem Rotor
DE29824966U1 (de) Verstelleinrichtung für eine Einrichtung zur relativen Drehlagenveränderung einer Welle zu einem antriebsrad, insbesondere einer Nockenwelle einer Brennkraftmaschine
WO2017050327A1 (fr) Soupape de commande pour un déphaseur d'arbre à cames

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

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL 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 RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

17P Request for examination filed

Effective date: 20110922

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: HILITE GERMANY GMBH

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

INTG Intention to grant announced

Effective date: 20130419

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL 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 RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 621098

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130715

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011001003

Country of ref document: DE

Effective date: 20130905

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

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20130710

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131010

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131110

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131111

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130619

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

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131011

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20131021

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

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

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

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

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

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

26N No opposition filed

Effective date: 20140411

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011001003

Country of ref document: DE

Effective date: 20140411

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

Ref country code: LU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140307

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: LI

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

Effective date: 20140331

Ref country code: IE

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

Effective date: 20140307

Ref country code: CH

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

Effective date: 20140331

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

Effective date: 20150307

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: 20150307

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

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

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

Ref country code: RS

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

Effective date: 20130710

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

Ref country code: BE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140331

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20110307

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 621098

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160307

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

Ref country code: AT

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

Effective date: 20160307

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

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

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

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

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20130710

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

Ref country code: FR

Payment date: 20230322

Year of fee payment: 13

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230515

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

Ref country code: DE

Payment date: 20240320

Year of fee payment: 14