EP2136041B1 - Vanne pour déphaser un arbre à cames - Google Patents

Vanne pour déphaser un arbre à cames Download PDF

Info

Publication number
EP2136041B1
EP2136041B1 EP09005039A EP09005039A EP2136041B1 EP 2136041 B1 EP2136041 B1 EP 2136041B1 EP 09005039 A EP09005039 A EP 09005039A EP 09005039 A EP09005039 A EP 09005039A EP 2136041 B1 EP2136041 B1 EP 2136041B1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
valve
camshaft
valve according
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.)
Not-in-force
Application number
EP09005039A
Other languages
German (de)
English (en)
Other versions
EP2136041A3 (fr
EP2136041A2 (fr
Inventor
Andreas Knecht
Dirk Pohl
Patrick Gautier
Markus Todt
Jan Eimert
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
Hydraulik Ring GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP2136041A2 publication Critical patent/EP2136041A2/fr
Publication of EP2136041A3 publication Critical patent/EP2136041A3/fr
Application granted granted Critical
Publication of EP2136041B1 publication Critical patent/EP2136041B1/fr
Not-in-force 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
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0475—Hollow camshafts
    • 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
    • F01L2001/34433—Location oil control valves

Definitions

  • the invention relates according to claim 1, a valve for pivoting a camshaft.
  • the DE 196 37 174 A1 shows a valve for a phaser in which a piston is longitudinally displaceable within a bore having a longitudinal axis. From the inner wall of the bore go from two working ports A, B and a pressure medium connection P. The pressure medium connection P is arranged axially between the two working ports A, B.
  • a valve for a phaser From the DE 198 53 670 B4 is also known a valve for a phaser. From the inner wall of the bore go two working ports A, B and a tank drain T from. The tank outlet T is arranged axially between the two working ports A, B. A front side of the valve arranged pressure medium connection P leads to the bore or the hollow piston from the inside pressure.
  • the object of the invention is to provide an axially very short camshaft adjuster.
  • the pressure medium connection P is immediately followed by the first working connection A.
  • This first working connection A is followed directly or indirectly by the second working connection B.
  • the camshaft adjuster can be designed axially correspondingly narrow in a valve, for example, arranged centrally to the camshaft adjuster valve.
  • the pressure medium connection P is arranged axially after or in front of the two working connections A, B.
  • this pressure medium connection P can be connected outside of the camshaft adjuster to channels in the valve, which can promote the supply pressure from a fluid feed pump to the working ports A and B respectively. Consequently, bores in the camshaft adjuster, which conduct the supply pressure from the fluid feed pump to the pressure medium connection P within the camshaft adjuster, are not necessary.
  • Such holes, in particular by the rotor of the camshaft adjuster increase the processing effort and weaken the rotor. In a particularly advantageous manner, therefore, the hydraulic fluid is passed through the piston of the valve.
  • the pressure medium connection P can be arranged in front of or behind the camshaft adjuster.
  • the arrangement behind the camshaft adjuster can be arranged in front of or behind the camshaft adjuster.
  • Camshaft adjuster is explained to the illustrated embodiments of this application.
  • a possible arrangement of the pressure medium connection P before the camshaft adjuster is for example in the DE 10 2004 038 252 A1 shown.
  • the hydraulic fluid is passed within the piston via a pressure chamber inlet channel from the pressure medium connection P to the respective working port A and B respectively.
  • This pressure chamber inlet channel is composed of two transverse channels and a central channel arranged between them.
  • the lengths of these channels are in a minimum relationship to each other that the lengths of the transverse channels in the direction of the longitudinal axis of the piston together are at least as long as the length of the intermediate central channel.
  • a camshaft adjuster can be used in a particularly advantageous manner, which designed as die gelzellenversteller is.
  • the invention can also find application in a camshaft adjuster according to the axial piston principle or a chain adjuster.
  • two tank connections are provided for quickly emptying the pressure chambers. These two tank connections can be provided in a further advantageous embodiment at the two ends of the valve.
  • the piston is guided axially in a bore.
  • the bore can be incorporated in a particularly advantageous manner in the socket of a cartridge valve.
  • the bore may also be arranged in a housing.
  • the bore is incorporated directly into a central screw, which screws the rotor of the camshaft adjuster with the camshaft.
  • Fig. 1 shows a detail of an internal combustion engine in the range of a camshaft adjuster 1.
  • This camshaft adjuster 1 is provided with a centrally disposed valve 2, which is designed as a 4/3-way proportional valve.
  • the valve 2 is designed as a so-called cartridge valve and comprises a hydraulic part 3 and an electromagnetic actuator 4.
  • the electromagnetic actuator 4 is arranged in alignment with a piston 5 of the hydraulic part 3.
  • An abutment body 6 of a plunger 7 of the actuator 4 abuts against the end face 8 of the piston 5.
  • a housing 9 and a pole core 10 of the electromagnetic actuator 4 are axially fixedly connected via a housing connection not shown in detail with a bush 11 of the hydraulic part 3, in the central bore 12 of the piston 5 is guided axially displaceable. This axial displacement is due to energization of the electromagnetic actuator 4 against the spring force, a helical compression spring 31st
  • valve 2 Function of the valve 2 is the hydraulic pressure on several pressure chambers 13a, 13b of the also in Fig. 5 distributed camshaft adjuster 1, so that a with a rotor 15 of the camshaft adjuster 1 axially and rotationally fixed camshaft 14 is pivoted in the one pivot direction or the opposite other pivoting direction.
  • two pressure chambers 13a, 13b are associated with opposite directions of pivoting.
  • the one of the pivoting direction associated pressure chambers 13a are connected via a in Fig. 2 closer apparent first working port A in the socket 11 is acted upon by a coming from a pressure medium port P pressure.
  • the pressure chambers 13b associated with the opposite direction of rotation are acted upon via a second working port B with the pressure coming from the pressure medium connection P.
  • the valve 2 further has two bypass ports A1 and B1.
  • the bushing 11 has three annular grooves 18, 19, 20, which are separated from each other by means of two annular webs 21, 22.
  • the front - in the drawing plane right - annular groove 18 and the middle annular groove 19 correspond to recesses 23 and 25 in the camshaft 14 and recesses 24 and 26 in the rotor 15. These recesses 23, 24, 25, 26 lead to the pressure chambers 13a, 13b.
  • the front annular groove 18 via the front recesses 25 of the camshaft 14 and the recesses 26 of the rotor 15 leads to the associated one direction of rotation pressure chambers 13b.
  • the middle annular groove 19 leads via the rear recesses 23 of the camshaft 14 and the recesses 24 of the rotor 15 in the pressure chambers 13 a associated with the other direction of rotation.
  • the rear annular groove 20 has a bore 27 which is connected to an annular channel 68, which is in communication with a fluid feed pump 30.
  • an end-side annular web 28, 29 is provided at the ends of the bush 11, which prevents fluid leakage from the rear annular channel 20 and the front annular channel 18.
  • radial bores in the groove bottom of the annular grooves are distributed circumferentially in defined angular positions.
  • the front annular groove 18 from front to rear axially successive bores for the working port B and the bypass port B1.
  • the middle annular groove 19 has From the front to the rear axially successive holes for the bypass port A1 and the working port A on.
  • the left annular groove 20 has from front to rear axially successive holes for the pressure medium connection P.
  • Fig. 3 and Fig. 4 show a valve 102 with a simplified piston 105, wherein with respect to the valve 2 according to Fig. 1 and Fig. 2 No bypass connections A1 and B1 are provided. Otherwise, the piston 105 is constructed equal to the piston 5.
  • the opposite Fig. 1 and Fig. 2 Substantially modified components have increased by 100 reference numerals. Substantially identical components are also provided with the same reference numerals.
  • Fig. 3 shows the piston 105 in a section analog Fig. 1
  • Fig. 4 shows the piston 105, however, 90 ° rotated about its longitudinal axis 34.
  • the piston 105 is in both Fig. 3 as well as in Fig. 4 shown in the foremost position. In this position, the piston 105 is pressed by a helical compression spring 31 when the electromagnetic actuator 4 is energized only slightly or not at all. In this case, a pressure chamber inlet channel 32 extends from the pressure medium connection P to the second working connection B. The pressure chambers 13b assigned to the working connection B are thus filled. At the same time runs to empty the other pressure chambers 13 a, the hydraulic fluid from the first working port A via an in Fig. 4 apparent pressure chamber outlet channel 33 to two tank drains T 1 , T 2 .
  • the shape of the piston 105 makes it possible for the pressure chamber outlet channel 33 to be separated from the pressure chamber inlet channel 32, although these two are guided past one another. That is to say, the pressure chamber outlet channel 33 and the pressure chamber inlet channel 32 run partially in the same axial regions of the valve 102.
  • the piston 105 has a substantially tubular basic shape with a tube wall 80.
  • a slot 35 is provided along the longitudinal axis 34 of the piston 105.
  • This slot 35 has a circumferentially closed wall 36, which separates the slot 35 against two in the tube on both sides of the wall 36 forming part-channels 65a, 65b.
  • said end face 8 is arranged at the front end of the slot 35.
  • an end face 37 is arranged, which supports the helical compression spring 31 elastically against a compression sleeve, which is pressed into the socket 11 to measure.
  • the pressure chamber outlet channel 33 extends to the tank drains T 1 , T 2 through the two partial channels 65a, 65b.
  • the pressure chamber inlet channel 32 extends through the slot 35.
  • the helical compression spring need not be supported on the wall 36 of the piston 105, but in an alternative embodiment also on an in Fig. 4 paragraph 40.
  • the piston 5 and 105 is produced by metal powder injection molding.
  • the tube shape of the piston is exemplary.
  • the piston has a complex integral geometry.
  • One such manufacturing process is injection molding.
  • the metal injection molding process metal injection molding
  • Injection molding processes also include such processes as injection-compression molding.
  • the separation of the pressure chamber discharge channel from the pressure chamber inlet channel takes place with a centrally extending slot. Due to the symmetry, the slot arranged centrally has the advantage that no torques act on the hydraulically actuated piston.
  • Fig. 6 shows in a further embodiment, a central valve 202, which is incorporated directly into a central screw 211, which screws the rotor 215 of the camshaft adjuster 201 with the camshaft 214.
  • a central screw 211 which screws the rotor 215 of the camshaft adjuster 201 with the camshaft 214.
  • an internal thread is cut in the camshaft 214, in which the external thread of the central screw 211 is screwed.
  • a lock 299 can be seen, by means of which the rotor 215 against a stator 298 rotatably locked. This lock 299 can be unlocked by a pressure in the two pressure chambers of the camshaft adjuster 201.
  • the lock is in communication with the pressure medium connection, so that the lock is unlocked immediately depending on the working pressure, the locking analog Fig. 6 done by means of spring force.
  • the camshaft adjuster is preferably designed as die gelzellenversteller.
  • an axial piston adjuster which converts the axial movement into a pivoting movement of the camshaft via helical gearing.
  • Such Axialkolbenversteller find especially in sporty engines with very strong valve springs of the gas exchange valves application, since there due to the high valve spring forces strong change moments of the camshaft must be overcome, which are not forwarded to the axial piston by the self-locking effect of the helical teeth in Axialkolbenversteller.
  • the camshaft may for example be a built camshaft.
  • compression sleeve can also be provided a screwed sleeve, or it may be provided integrally with the socket manufactured bottom.
  • the piston can also be displaced by means of a further hydraulic auxiliary piston.
  • a further hydraulic auxiliary piston depending on the ratio, for example, a force amplification or a very fine positioning of the piston can be achieved.
  • a tank drain on an end face of the piston or an end face of the socket suffice.
  • a tank drain on an end face of the piston or an end face of the socket suffice.
  • a massive design of the piston on one end face of the support surface for the helical compression spring can be increased and voltages can be kept low in the region of this support surface.
  • the tank drains do not have to be arranged on the front side. So it is also possible to run the tank drains as radial holes in the piston and / or in the socket.
  • the outer diameter of the bush or the piston can be rotated in a Spanabhub before the three annular grooves are turned off.
  • the Socket and / or the piston also have stepped outer diameter, wherein the rearmost outer diameter is smallest and the front outer diameter is the largest.
  • This is particularly advantageous for valves with sealing rings - in particular O-rings.
  • These sealing rings can be used in annular grooves in the outer diameter.
  • the sealing rings can be used in êtringnuten the rotor.
  • the stepped design of the outer diameter prevents damage to the seals.
  • Such sealing rings are particularly advantageous for valves for particularly high hydraulic pressures or high demands on the leak-tightness.
  • the use of O-rings is also advantageous when using different materials for the valve components with different thermal expansion coefficients.
  • the piston can be made of metal or plastic.
  • the plastic is produced by injection molding. When using a plastic and a fiber reinforced plastic is advantageous, as this already in the unpublished DE 10 2007 026 831 is shown.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Claims (12)

  1. Soupape (2) pour un déphaseur d'arbre à cames (1), dans laquelle un piston (5) est disposé à l'intérieur d'un alésage (12) de façon à être mobile dans le sens de la longueur ;
    - un raccord d'agent de pression (P) ; et
    - à la suite immédiate de celui-ci dans le plan axial, un premier raccord de travail (A) et ;
    - à la suite du raccord d'agent de pression (P) et du premier raccord de travail (A) dans le plan axial, un deuxième raccord de travail (B) ;
    ressortant de la paroi intérieure (79) dudit l'alésage ; le piston (5) comportant un canal d'alimentation de chambre de pression (32) et un canal d'évacuation de chambre de pression (33) disposé de façon séparée par rapport à celui-ci, le piston (5 et/ou 105) comportant une paroi tubulaire (80) pour l'essentiel en forme de tube avec une fente (35) centrale, dont la paroi (36) est contigüe à la paroi tubulaire (80), de sorte que la paroi (36) de la fente (35) du canal d'évacuation de chambre de pression (33) sert de séparation d'avec un canal d'alimentation de chambre de pression (32), le canal d'évacuation de chambre de pression (33) se divisant en deux parties de canaux (65a, 65b) le long de la fente, le piston (11) étant fabriqué selon un procédé de moulage par injection et le canal d'alimentation de chambre de pression (32) s'étendant à travers :
    - un canal d'admission (91) s'étendant transversalement par rapport à un axe longitudinal (34) du piston avec une longueur LP par rapport à l'axe longitudinal (34) ;
    - un canal central (92) s'étendant le long de l'axe longitudinal (34) avec une longueur LM par rapport à l'axe longitudinal (34) ; et
    - un canal d'évacuation (93) s'étendant transversalement par rapport à l'axe longitudinal (34) avec une longueur LAB par rapport à l'axe longitudinal (34) ;
    sachant que LM ≤ LP + LAB pour les longueurs.
  2. Soupape selon la revendication 1,
    caractérisée en ce qu'une soupape antiretour (77) est placée dans le raccord d'agent de pression (P).
  3. Soupape selon la revendication 2,
    caractérisée en ce que la soupape antiretour (77) prend la forme d'une bande (76) insérée dans une rainure annulaire intérieure (78) ressortant de la paroi intérieure (79) de l'alésage (12).
  4. Soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que l'évacuation de réservoir (T1 et/ou T2) ressort côté frontal hors du piston (11).
  5. Soupape selon la revendication 4,
    caractérisée en ce que des évacuations de réservoir (T1, T2) ressortent des deux côtés du piston (11).
  6. Soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce qu'au moins un raccord de déviation (A1 et/ou B1) est prévu dans le plan axial entre les deux raccords de travail (A, B) avec lequel le fluide hydraulique de la chambre de pression à vider peut être guidé dans la chambre de pression à remplir dans le cas dans lequel la pression augmente dans la chambre de pression à vider du fait de la pression de la chambre de pression à remplir.
  7. Soupape selon la revendication 6,
    caractérisée en ce que deux raccords de déviation (A1, B1) sont prévus directement l'un à côté de l'autre dans le plan axial entre les deux raccords de travail (A, B).
  8. Soupape selon la revendication 6 ou 7,
    caractérisée en ce que le raccord de déviation (A1 et/ou B1) comprend une soupape antiretour (16 et/ou 17) prenant la forme d'une bande insérée dans une rainure annulaire intérieure (75 et/ou 74) ressortant de la paroi intérieure (79) de l'alésage (12).
  9. Soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que la soupape (2) est disposée de façon alignée par rapport à un arbre à cames (14), un actionneur électromagnétique (4) étant disposé sur un côté du déphaseur d'arbre à cames (1) opposé par rapport à la culasse, tandis que le raccord d'agent de pression (P) est disposé sur l'autre côté du déphaseur d'arbre à cames (1).
  10. Soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que la soupape (2) est disposée de façon alignée par rapport à un arbre à cames (14), un actionneur électromagnétique (4) étant disposé sur un côté du déphaseur d'arbre à cames (1) opposé par rapport à la culasse tandis qu'un alésage (27) est prévu sur l'autre côté du déphaseur d'arbre à cames (1) dans l'arbre à cames (14) dans lequel débouche le raccord d'agent de pression (P).
  11. Soupape selon l'une quelconque des revendications 9 ou 10,
    caractérisée en ce que le raccord d'agent de pression (P) débouche au moins indirectement dans un évidement du palier d'arbre à cames (70).
  12. Soupape selon la revendication précédente,
    caractérisée en ce que le piston est fabriqué selon le procédé de moulage par injection de poudre de métal (MIM).
EP09005039A 2008-06-19 2009-04-06 Vanne pour déphaser un arbre à cames Not-in-force EP2136041B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008028846 2008-06-19

Publications (3)

Publication Number Publication Date
EP2136041A2 EP2136041A2 (fr) 2009-12-23
EP2136041A3 EP2136041A3 (fr) 2010-07-14
EP2136041B1 true EP2136041B1 (fr) 2011-06-08

Family

ID=41082411

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09005039A Not-in-force EP2136041B1 (fr) 2008-06-19 2009-04-06 Vanne pour déphaser un arbre à cames

Country Status (2)

Country Link
EP (1) EP2136041B1 (fr)
AT (1) ATE512285T1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010019005B4 (de) * 2010-05-03 2017-03-23 Hilite Germany Gmbh Schwenkmotorversteller
DE102010049551A1 (de) * 2010-10-25 2012-04-26 Schaeffler Technologies Gmbh & Co. Kg Steuerventil für einen Nockenwellenversteller
DE102010060181B4 (de) * 2010-10-26 2014-08-21 Hilite Germany Gmbh Zentralventil
DE102010060180B4 (de) * 2010-10-26 2017-06-29 Hilite Germany Gmbh Zentralventil
JP6354560B2 (ja) 2014-12-12 2018-07-11 株式会社デンソー 電磁アクチュエータ

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3666072B2 (ja) 1995-09-13 2005-06-29 アイシン精機株式会社 切替弁
DE19853670C5 (de) 1998-11-20 2019-01-10 Hilite Germany Gmbh Einrichtung zur Nockenwellenverstellung
GB0303571D0 (en) * 2003-02-17 2003-03-19 Delphi Tech Inc Oil flow control valve for a cam phaser
DE102004038252A1 (de) 2004-05-14 2005-12-15 Ina-Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102005013085B3 (de) 2005-03-18 2006-06-01 Hydraulik-Ring Gmbh Ventil mit Rückschlagventil
DE102005041393A1 (de) 2005-09-01 2007-03-08 Schaeffler Kg Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine
DE102006012775B4 (de) 2006-03-17 2008-01-31 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102006012733B4 (de) 2006-03-17 2008-03-27 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102007026831B3 (de) 2007-06-06 2008-10-02 Hydraulik-Ring Gmbh Elektrohydraulisches Ventil

Also Published As

Publication number Publication date
ATE512285T1 (de) 2011-06-15
EP2136041A3 (fr) 2010-07-14
EP2136041A2 (fr) 2009-12-23

Similar Documents

Publication Publication Date Title
EP2870327B1 (fr) Dephaseur à ailettes oscillantes avec vanne de commande hydraulique
DE19717295C2 (de) Fluid-Maschine
DE102010045358A1 (de) Schwenkmotornockenwellenversteller mit einem Hydraulikventil
DE102004035035A1 (de) Nockenwellenversteller für Brennkraftmaschinen
EP2220373A1 (fr) Module de pompe pour appliquer une pression synchronisée sur deux circuits de fluide
EP2136041B1 (fr) Vanne pour déphaser un arbre à cames
EP2370714B1 (fr) Unité de commande électromagnétique
DE10144641A1 (de) Entspannungsventil
DE102010032133A1 (de) Zentralventil
EP1205652A1 (fr) Variation de taux de compression avec deux soupapes commandées hydrauliquement dans le vilebrequin
EP0669469B1 (fr) Actionneur fluidique rotatif
EP3530892B1 (fr) Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
DE102019101115A1 (de) Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle
DE102012208808A1 (de) Steuerventil zur Steuerung von Druckmittelströmen eines Nockenwellenverstellers
DE102010013777A1 (de) Zentralventil
DE102017107719A1 (de) Hydraulikventil zum Einstellen eines Hydraulikflüssigkeitsstroms eines Pleuels für eine Brennkraftmaschine mit variabler Verdichtung
DE102014115903A1 (de) Hydraulikventil und Schwenkmotorversteller
DE102013202917A1 (de) Zahnradmaschine mit erhöhter Partikelrobustheit
DE102011000591A1 (de) Zentralventil
DE3526319C2 (fr)
DE102006060433B4 (de) Flügelzellenpumpe
DE102010020356A1 (de) Schmiermittelpumpe, Regelkolben
EP3530891B1 (fr) Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
DE102011000522A1 (de) Schwenkmotorversteller mit einem Hydraulikventil
DE112008003332B4 (de) Hydrostatisches Gerät oder hydrostatische Maschine,insbesondere Axialkolbenmaschine, mit einer Ventilanordnung inWechselventilbauweise mit einem Filter

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: 20090424

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 TR

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

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 TR

AX Request for extension of the european patent

Extension state: AL BA RS

RIC1 Information provided on ipc code assigned before grant

Ipc: F01L 1/344 20060101AFI20100908BHEP

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): 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 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: 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: 502009000734

Country of ref document: DE

Effective date: 20110721

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20110608

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

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: 20110608

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: 20110608

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: 20110608

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: 20110908

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

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: 20110608

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: 20110608

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: 20110608

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: 20110919

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: 20110608

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: 20110909

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: 20110608

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

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

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: 20110608

Ref country code: IE

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: 20110608

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: 20110608

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: 20111010

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: 20111008

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

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: 20110608

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: 20110608

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: 20110608

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: HILITE GERMANY GMBH

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: 20120309

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: 20110608

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: 20110608

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502009000734

Country of ref document: DE

Effective date: 20120309

BERE Be: lapsed

Owner name: HYDRAULIK-RING G.M.B.H.

Effective date: 20120430

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 NON-PAYMENT OF DUE FEES

Effective date: 20120430

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

Ref country code: BE

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

Effective date: 20120430

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: 20110608

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

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: 20110908

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502009000734

Country of ref document: DE

Owner name: HILITE GERMANY GMBH, DE

Free format text: FORMER OWNER: HYDRAULIK-RING GMBH, 97828 MARKTHEIDENFELD, DE

Effective date: 20130521

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: 20110608

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20130406

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: 20130406

Ref country code: CH

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

Effective date: 20130430

Ref country code: LI

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

Effective date: 20130430

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: 20110608

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 NON-PAYMENT OF DUE FEES

Effective date: 20120406

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

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

Effective date: 20090406

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 512285

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140406

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: 20140406

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 9

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

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

Ref country code: FR

Payment date: 20180420

Year of fee payment: 10

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

Ref country code: DE

Payment date: 20190418

Year of fee payment: 11

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: 20190430

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502009000734

Country of ref document: DE

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: 20201103