EP2744987B1 - Arbre à cames pour la commande des soupapes d'un moteur à combustion interne - Google Patents

Arbre à cames pour la commande des soupapes d'un moteur à combustion interne Download PDF

Info

Publication number
EP2744987B1
EP2744987B1 EP12743890.1A EP12743890A EP2744987B1 EP 2744987 B1 EP2744987 B1 EP 2744987B1 EP 12743890 A EP12743890 A EP 12743890A EP 2744987 B1 EP2744987 B1 EP 2744987B1
Authority
EP
European Patent Office
Prior art keywords
cam
camshaft
bearing ring
carrier
internal combustion
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
EP12743890.1A
Other languages
German (de)
English (en)
Other versions
EP2744987A1 (fr
Inventor
Heino Schiller
Michael Hinkel
Sebastian Schneider
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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 Volkswagen AG filed Critical Volkswagen AG
Publication of EP2744987A1 publication Critical patent/EP2744987A1/fr
Application granted granted Critical
Publication of EP2744987B1 publication Critical patent/EP2744987B1/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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction

Definitions

  • the invention relates to a camshaft for the valve train of an internal combustion engine and an at least one such camshaft having internal combustion engine.
  • the adjusting device which is designed so that it simultaneously adjusts the two intake and exhaust valves of each cylinder of the internal combustion engine, comprises a cam carrier as part of the camshaft, which is non-rotatably arranged in the axial direction displaceable on a basic shaft of the camshaft.
  • the cam carrier has two cam groups, each with two (in the axial direction) arranged side by side cams with different cam shapes.
  • the adjusting device makes it possible to adjust the stroke of the valves associated with these cam groups in that the cam carrier is displaced into one of a total of three defined axial positions, whereby a contact element of a finger lever, with which the valves are actuated, either with one of the two cams or with a "Zero cam” is brought into contact, which is in principle a portion of the cam carrier, which has no cam lobe.
  • the respective valve actuated with a stroke defined by the respective cam lobe and additionally dependent on the gear ratio of the cam follower.
  • the stroke of the valve corresponding to the missing cam lift is zero. Accordingly, a valve shutdown is realized via the "zero cam”.
  • An adjustment of the individual cam carrier in the axial direction of the camshaft is carried out by means of a respective guide wheel, which constitutes an integral part of the cam carrier.
  • a running in the circumferential direction Y-shaped groove is intergrated.
  • This groove thus has two divergent partial grooves in a section.
  • the actual adjustment is achieved by means of an adjusting device, which has a total of three extendable adjusting pins, one of which, in each case Depending on the respective position of the cam carrier on the fundamental and the desired adjustment, is extended and engages in a portion of the groove. If one of the adjustment pins engages in one of the divergent sub-grooves, this leads to an axial displacement of the cam carrier on the basic shaft as a result of the relative rotation of the guide gear to the pin.
  • a bearing ring is disposed rotatably disposed on the corresponding portion of the cam carrier.
  • the bearing ring is rotatably but slidably disposed in the axial direction within a housing of the internal combustion engine, the cylinder head cover arranged.
  • the bearing ring serves to support the camshaft in the cylinder head cover, wherein the displaceability of the cam carrier is made possible in the direction of the longitudinal axis of the camshaft.
  • the bearing ring forms on the outside a bar-shaped projection, which serves for a rotation of the bearing ring, whereby co-rotation is prevented with the camshaft.
  • three recesses are integrated in the top of the bar-shaped projection, in which a ball of a spring-loaded locking element engages to fix the cam carrier in the respective position in which this has been adjusted by means of the guide wheel.
  • the bearing ring in the valve train of DE 10 2007 010 148 A1 consists of two half-shells, whereby an assembly on the limited by the cams of the two cam groups portion of the cam carrier is made possible.
  • This embodiment of the bearing ring requires an extremely complex processing, since due to the high rotational speeds of the camshaft, which is rotatable relative to the bearing ring, very tight tolerances are required, a rotatory machining of the half shells is not possible.
  • a - albeit less - offset between the bearing halves can not be excluded, which would significantly increase the friction of the bearing ring on the corresponding portion of the cam carrier.
  • the configuration of the bearing ring with the two bar-shaped projections has the disadvantage that the bearing of the bearing ring must be performed split in the cylinder head, which in the valve train of DE 10 2007 010 148 A1 is solved with the help of the cylinder head and a bolted bearing bracket.
  • Such storage is expensive to install and thus increases the cost of the internal combustion engine.
  • the invention has the object, an improved internal combustion engine with a generic, from the DE 10 2007 010 148 A1 specify known valve train.
  • the valve train should be improved so that the camshaft contained in this is easier to install and is characterized by a lower friction loss.
  • camshaft according to the independent claim 1 and by such a camshaft having internal combustion engine according to the independent claim 7.
  • Advantageous embodiments of the camshaft or the internal combustion engine according to the invention are the subject of the dependent claims and will become apparent from the following description of the invention.
  • the bearing of the bearing ring on the corresponding portion of the cam carrier is preferably formed as a hydrodynamic or hydrostatic sliding bearing.
  • the bearing surfaces i.e., the corresponding portion of the outer surface of the cam carrier and the inner surface of the bearing ring
  • a lubricant is supplied.
  • a bearing ring understood that is not composed of two or more sub-shells.
  • Such a bearing ring may preferably also be designed in one piece, i. consist of only one component, of course, it is also possible to form a one-piece bearing ring according to the invention of a plurality of components, in which case at least the component that forms the inner surface is formed closed annular.
  • the bearing ring Due to the integral nature of the bearing ring whose manufacture is simplified because it can be manufactured as a simple turned part. In addition, can be achieved by the one-piece in a simple way a completely paragraph-free inside. Such an inside is in a bearing ring, which consists of two half-shells, as in the valve train in the DE 10 2007 010 148 A1 The case is not certainly avoidable, since an offset during assembly of the two half-shells can not be excluded.
  • the one-piece bearing ring of the camshaft according to the invention is thus characterized in each case by a low friction of its rotational movement on the cam carrier.
  • a “zero cam” is understood according to the invention, which has no cam lobes and over which thus a zero stroke of the thus driven valve of the internal combustion engine is achieved.
  • An internal combustion engine comprises at least one housing and at least one camshaft according to the invention arranged in the housing, wherein the basic shaft of the camshaft is rotatably supported within the housing via the at least one bearing ring of the cam carrier and the bearing ring is also displaceable relative to the housing in the axial direction of the camshaft ,
  • each of the cam carrier of the camshaft according to the invention on a plurality and preferably two cam groups, which are arranged on both sides of the bearing ring.
  • the cam carrier has a support tube, and at least one, preferably all of the cam groups (or. each formed by these cams) as structurally separate from the support tube, but with this (permanently) connectable or connected unit (s) are formed.
  • cam carrier with a support tube and at least one, preferably a plurality of structurally separate cam groups not only has the advantage of mounting with a one-piece bearing ring according to the invention, but it is also possible to form the support ring and the cams (groups) of different materials in order to adapt them optimally to the different demands.
  • the cam carrier of the camshaft according to the invention preferably has a control ring with at least one control groove, which is introduced into its outer side and does not extend in at least one section in a radial plane of the camshaft. This creates the possibility of axially displacing the cam carrier on the fundamental shaft of the camshaft on the fundamental shaft by the temporary engagement of a control pin (not co-rotating with the camshaft) into the control groove.
  • control ring is formed as structurally separate from the support tube, but with the support tube (permanently) connected component.
  • the assembly of the camshaft according to the invention can be simplified, but in any case there is the possibility to optimally adapt by a targeted selection of materials, the support tube or the control ring to the respective stresses.
  • a press fit is preferably provided in which thus at the same component temperatures, the outer diameter of the (insulated) support tube slightly larger than the inner diameter of the (isolated) cam group (s) and / / or of the (isolated) Verschieberings, whereby these components are positively connected to each other in the joined state.
  • the support tube is exposed to a lower temperature than the cam group (s) and / or the Verschiebering before assembly for the production of such a press fit;
  • the support tube can be cooled and / or the cam group (s) and / or the sliding ring are heated. After cooling or reheating of the components after assembly then sets the desired interference fit.
  • the width of the longitudinal groove may have to correspond (at least) to the maximum displacement of the cam carrier on the fundamental shaft. This displacement may optionally be greater than the width of the bearing ring, which may be limited by the distance of the valves which are actuated by the cam groups of the cam carrier. This can complicate a constructive implementation of the lubricant supply, especially in small-volume internal combustion engines, since the integration of a sufficiently long longitudinal groove in the bearing ring does not seem feasible.
  • the outer diameter of the bearing ring is greater than the maximum cam lobe of the directly adjacent cams of the cam groups and the axial extent of the bearing ring - in at least a portion of its outer surface - greater than the distance between the two cam groups.
  • the bearing ring on the outside has a (further) longitudinal groove into which engages a non-rotatable with the camshaft, preferably fixed standing with respect to the housing fuse element to form a rotation of the bearing ring.
  • the bearing ring on the outside forms at least two cavities spaced from one another in the axial direction of the camshaft, wherein a position assurance element not co-rotating with the camshaft, preferably fixed relative to the housing, depending on the respective axial position of the cam carrier on the camshaft engages in one of the recesses and thereby forms a position assurance or locking the cam carrier.
  • the in the Fig. 1 and 2 illustrated cylinder head of an internal combustion engine according to the invention comprises a cylinder head cover 10 as part of a housing of the internal combustion engine.
  • the cylinder head cover 10 forms two storage tunnels 12, in each of which a camshaft 14, 16 according to the invention is mounted.
  • the two camshafts 14, 16 are driven by a crankshaft (not shown) of the internal combustion engine, to which a first of the camshafts 14 is connected to a drive wheel 18 which is connected via a toothed belt, not shown, with a corresponding output gear of the crankshaft.
  • the first camshaft 14 drives the second camshaft 16 via a gearwheel drive, not shown.
  • the second camshaft 16 may be provided with a phaser (not shown) via which a phase shift of the mutually coupled rotational movements of the two camshafts 14, 16 can be achieved.
  • Each of the two camshafts 14, 16 comprises a basic shaft 20, on which a total of four cam supports 22 are arranged secured against rotation.
  • the anti-rotation is achieved via a spline on an inner surface of each of the cam carrier (see. Fig. 6 ) in connection with a corresponding longitudinal toothing on the outer surface of the respective section of the fundamental shaft 20.
  • the longitudinal toothing ensures the inventively provided displaceability of the cam carrier 22 in the longitudinal direction of the camshaft 14, whereby a Hubumscnies of the cam of the Cam carrier 22 actuated valves (not shown) of the internal combustion engine can be realized.
  • Each of the cam supports 22 comprises a support tube 24 and two cam groups 26 structurally separate from the support tube and formed as annular units, each of the cam groups 26 being divided in the axial direction into three adjacent sections. In two of these sections, the cam groups each form a cam, which rises from the cylindrical basic shape of the outer surface at one point of the circumference. The two cams of each of the cam groups 26 have different shapes and in particular different maximum elevations, resulting in different valve lifts for the valves operated therewith. The third section of each of the cam groups 26 has no elevations and represents a zero cam. The zero cam can be used to keep the "actuated" valve closed.
  • a three-stage Ventilhubscnies can be achieved.
  • This Ventilhubscnies is achieved via an axial displacement of the four cam carrier 22 per camshaft 14, wherein in each case an actuating element (not shown), such as a drag lever associated with each of the valves, in contact with one of the cam and the zero cam each the cam groups 26 is brought, whereby the valve is operated or not operated according to the shape of the respective cam or null cam.
  • a Y-shaped cam groove 30 is introduced.
  • a first section of this control groove 30 extends exactly in the circumferential direction, ie in a (radial) plane arranged perpendicular to the longitudinal axis of the control ring 28.
  • a second section connects, in which the control groove 30 is formed of two diverging extending part-grooves.
  • control ring 28 of each of the cam supports 26 is associated with an actuator 32 connected to the cylinder head cover 10 having three control pins (not shown) which may be extended (individually driven) to engage the first portion or one of the sub-grooves of the second portion Control groove 30 of the associated control ring 28 engage and move the cam carrier 22 in one direction on the fundamental shaft 20 due to the relative movement between the rotating control ring 28 and the fixed control pin.
  • each of the cam carriers 22 comprises a bearing ring 34, which is rotatably arranged on the carrier tube 24 of the cam carrier 22 and between the two cam groups 26.
  • the bearing ring 34 serves to support the camshaft 14 within the cylinder head cover 10. Since an axial displacement of the cam carrier 22 on the basic shaft 20 of the camshaft 14 and a corresponding displacement of the bearing ring 34 is required, the bearing of the bearing ring 34 in the cylinder head cover 10 before a corresponding axial displacement.
  • the bearing ring 34 has an outer bearing shell 36, which is mounted displaceably in a section of the cylinder head cover 10 (in the longitudinal direction of the bearing ring or the camshaft).
  • the outer bearing shell 36 has a cylindrical basic shape with a plurality of apertures, so that there is no completely closed cylindrical lateral surface. Furthermore, the bearing ring 34 still has a cylindrical inner bearing shell 38, which are connected to the outer bearing shell 36 via an annular web 40. The inner bearing shell 38 is supported on both sides on the two cam groups 26 of the cam carrier 22.
  • the bearing ring 24 is in one piece according to the invention and also formed in one piece.
  • the outer diameter of the outer bearing shell 26 is greater than the maximum elevation of the directly adjacent cams of the two cam groups 26. Furthermore, the outer bearing shell 36 projects beyond the inner bearing shell 38 in the axial direction and thus partially engages over the adjacent cams. As a result, the bearing ring 34 can be realized with an outer bearing shell 36, which is wider than the distance between the two cam groups 26 of the cam carrier 22 (limited by the distance between the two valves controlled by the respective cam carrier 22). This makes it possible to integrate a longitudinal groove 42 with a sufficient length in the outer bearing shell 36.
  • This longitudinal groove 42 serves to establish a connection between a bore 44 extending from the groove base and extending through the web 40 to the inside of the inner bearing shell 38 and an outlet 46 of a lubricant supply integrated in the cylinder crankcase 10 (cf. Fig. 6 ).
  • longitudinal groove 48 is integrated, into which engages a bolt of a screwed into the cylinder head 10 locking pin 50.
  • a rotation for the bearing ring 34 of each of the cam carrier 22 is realized without hindering its axial displacement.
  • wedge-shaped recesses 52 is introduced into which a spring-loaded ball 54 of a position assurance element 56 can engage. These three recesses 52 define axial positions in which the cam carrier 22 can be fixed by means of the position securing element 56.
  • the individual elements of the cam carrier (carrier tube 24, cam groups 26, bearing ring 34 and control ring 28) are connected by means of press fit. Their assembly is carried out as follows: The cam groups 26, the bearing ring 34 and the control ring 28 are pre-positioned and heated in the order provided. The carrier tube 24 is cooled simultaneously with liquid nitrogen. The cam groups 26, the bearing ring 34 and the control ring 2 are then inserted into a mounting device (not shown) and the support tube 34 then pushed through these elements. Then, the cam groups 26 and the bearing ring 34 and the control ring 28 in the intended positions (relative to each other) are rotated. After an approximation of the temperatures of the elements, the desired interference fit is formed.

Claims (8)

  1. Arbre à cames (14, 16) pour la commande des soupapes d'un moteur à combustion interne, comprenant un arbre de base (20), au moins un porte-cames (22) disposé de manière solidaire en rotation et déplaçable axialement sur l'arbre de base (20), le porte-cames (22) constituant au moins un groupe de cames (26) avec au moins deux cames disposées l'une à côté de l'autre dans la direction axiale avec des formes de cames différentes, et une bague de palier (34) réalisée d'une seule pièce, disposée sur le porte-cames de manière fixée en déplacement axial et de manière rotative, caractérisé en ce que la bague de palier (34) présente dans la surface extérieure une rainure longitudinale (42) et un alésage (44) conduisant depuis une base de la rainure longitudinale (42) jusqu'au côté intérieur de la bague de palier (34).
  2. Arbre à cames selon la revendication 1, dans lequel le porte-cames (22) présente deux groupes de cames (26) qui sont disposés de part et d'autre de la bague de palier (34), caractérisé en ce que le porte-cames (22) présente un tube de support (24) et au moins un des groupes de cames (26) est réalisé sous forme d'unité connectée au tube de support (24), séparée structurellement du tube de support (24).
  3. Arbre à cames selon la revendication 1 ou 2, dans lequel le porte-cames (22) présente une bague de commande (28) avec au moins une rainure de commande (30) réalisée dans une surface extérieure de la bague de commande (28), s'étendant au moins dans une portion non située dans un plan radial de l'arbre à cames, caractérisé en ce que la bague de commande (28) est réalisée sous forme de composant connecté au tube de support (24), séparé structurellement du tube de support (24).
  4. Arbre à cames selon la revendication 2 ou 3, caractérisé en ce que le ou les groupes de cames (26) et/ou la bague de commande (28) est/sont connecté(e)(s) par le biais d'un ajustement serré au tube de support (24).
  5. Arbre à cames selon l'une quelconque des revendications 2 à 4, caractérisé en ce que le diamètre extérieur de la bague de palier (34) est supérieur au rehaussement de came maximum des cames directement adjacentes des groupes de cames (26) et l'étendue axiale de la bague de palier (34) dans au moins une portion de sa surface extérieure est supérieure à la distance entre les deux groupes de cames (26).
  6. Moteur à combustion interne comprenant un boîtier et au moins un arbre à cames (14, 16) disposé dans le boîtier selon l'une quelconque des revendications précédentes, l'arbre de base (20) étant supporté au moyen de la bague de palier (34) de manière rotative à l'intérieur du boîtier et la bague de palier (34) pouvant être déplacée dans la direction axiale de l'arbre à cames (14, 16) par rapport au boîtier.
  7. Moteur à combustion interne selon la revendication 6, caractérisé en ce que la bague de palier (34) présente du côté extérieur une rainure longitudinale (48) dans laquelle s'engage un élément de fixation connecté au boîtier pour la fixation en rotation de la bague de palier (34).
  8. Moteur à combustion interne selon la revendication 6 ou 7, caractérisé en ce que la bague de palier (34) présente du côté extérieur au moins deux renfoncements (52) disposés à distance l'un de l'autre dans la direction axiale de l'arbre à cames (14, 16), un élément de fixation en position (56) connecté au boîtier s'engageant dans l'un des renfoncements (52) en fonction de la position axiale respective du porte-cames (22) sur l'arbre à cames (14, 16).
EP12743890.1A 2011-08-20 2012-07-30 Arbre à cames pour la commande des soupapes d'un moteur à combustion interne Active EP2744987B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110111580 DE102011111580A1 (de) 2011-08-20 2011-08-20 Nockenwelle für den Ventiltrieb einer Brennkraftmaschine
PCT/EP2012/003233 WO2013026520A1 (fr) 2011-08-20 2012-07-30 Arbre à cames pour la commande des soupapes d'un moteur à combustion interne

Publications (2)

Publication Number Publication Date
EP2744987A1 EP2744987A1 (fr) 2014-06-25
EP2744987B1 true EP2744987B1 (fr) 2015-09-16

Family

ID=46639418

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12743890.1A Active EP2744987B1 (fr) 2011-08-20 2012-07-30 Arbre à cames pour la commande des soupapes d'un moteur à combustion interne

Country Status (3)

Country Link
EP (1) EP2744987B1 (fr)
DE (1) DE102011111580A1 (fr)
WO (1) WO2013026520A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014109751B4 (de) * 2014-07-11 2016-06-30 Thyssenkrupp Presta Teccenter Ag Verfahren zur Anordnung einer Nockenwelle in einem Nockenwellenmodul
DE102015101295A1 (de) 2015-01-29 2016-08-04 Thyssenkrupp Ag Verfahren zur Montage einer Nockenwelle in einem Modulkörper
DE102015106308A1 (de) 2015-04-24 2016-10-27 Thyssenkrupp Ag Nockenwellenmodul

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10148243A1 (de) * 2001-09-28 2003-04-10 Ina Schaeffler Kg Ventiltrieb mit Ventilhubumschaltung für die Gaswechselventile eines 4-Takt-Verbrennungsmotors
DE10241920A1 (de) * 2002-09-10 2004-03-18 Bayerische Motoren Werke Ag Ventiltrieb für eine Brennkraftmaschine
DE102004008670B4 (de) * 2004-02-21 2013-04-11 Schaeffler Technologies AG & Co. KG Ventiltrieb mit Nockenumschaltung für die Gaswechselventile eines 4-Takt-Verbrennungsmotors
DE102007022145A1 (de) * 2006-07-26 2008-01-31 Schaeffler Kg Umschaltbarer Ventiltrieb einer Brennkraftmaschine
DE102007010149A1 (de) * 2007-03-02 2008-09-04 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit verschiebbarem Nockenträger und Doppelschneckentrieb
DE102007010148A1 (de) 2007-03-02 2008-09-04 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit einem axial beweglichen Lager
DE102007027979B4 (de) * 2007-06-19 2015-07-23 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit Nockenwellen-Tunnellager
DE102009030373A1 (de) * 2009-06-25 2010-12-30 Schaeffler Technologies Gmbh & Co. Kg Ventiltrieb einer Brennkraftmaschine
DE102010004591B4 (de) * 2010-01-14 2021-08-19 Audi Ag Gebauter Nockenträger für Ventiltrieb

Also Published As

Publication number Publication date
DE102011111580A1 (de) 2013-02-21
EP2744987A1 (fr) 2014-06-25
WO2013026520A1 (fr) 2013-02-28

Similar Documents

Publication Publication Date Title
EP1608849B1 (fr) Commande de soupape d'un moteur a combustion interne presentant une culasse
DE102010004591B4 (de) Gebauter Nockenträger für Ventiltrieb
EP2132418B1 (fr) Mécanisme de distribution pour des soupapes d'échange des gaz d'un moteur à combustion interne, doté d'un porte-came mobile et d'un engrenage à deux vis
EP2315920B1 (fr) Liaison par cannelures et mécanisme de distribution avec liaison par cannelures entre un arbre à cames et des supports de came déplaçables
EP2291578B1 (fr) Distribution pour les soupapes d'echange de gaz d'un moteur a combustion interne avec des supports de came doublement soutenus
DE102008053723B4 (de) Gebaute Nockenwelle
EP3421741B1 (fr) Commande de soupape variable
EP2739830B1 (fr) Commande de soupape d'un moteur à combustion interne, moteur à combustion interne et procédé de fabrication d'une commande de soupape correspondante
EP2676009B1 (fr) Module d'actionnement pour au moins une soupape d'échange des gaz d'un moteur à combustion interne
WO2016110281A1 (fr) Liaison d'un régleur d'arbre à cames à un double arbre à cames
EP2744986B1 (fr) Systeme d'arbre a cames ajustable
WO2011042391A1 (fr) Agencement d'arbre à cames
WO2015113748A1 (fr) Procédé d'assemblage d'un module de véhicule automobile
DE102007010154A1 (de) Ventiltrieb einer Brennkraftmaschine mit dreistufigen Nockenprofilgruppen und verschiebbaren Nockenträgern mit integrierten Stellorganen
EP2744987B1 (fr) Arbre à cames pour la commande des soupapes d'un moteur à combustion interne
DE102008032949B4 (de) Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine
DE102011001661B4 (de) Ventiltrieb für eine Brennkraftmaschine
DE102012016672A1 (de) Brennkraftmaschine mit einem Ventiltrieb
DE102010047993B4 (de) Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit verschiebbaren Nockenträgern und mitrotierenden axialen Endanschlägen sowie Brennkraftmaschine
DE102016208392A1 (de) Nockenwelle
DE102014214125B4 (de) Stelleinrichtung zur Verstellung von Steuerzeiten einer Brennkraftmaschine
DE102013225865B4 (de) Nockenwelle
DE102012016356A1 (de) Verstellbare Nockenwelle und Verbrennungsmotor
DE102012001303B4 (de) Verstellwellenbetätigung eines Ventiltriebs für Brennkraftmaschinen zur Betätigung von Gaswechselventilen
WO2006074736A1 (fr) Dispositif pour modifier les temps de commande d'un moteur a combustion interne

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: 20140320

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

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150507

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): 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: 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: AT

Ref legal event code: REF

Ref document number: 750002

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151015

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502012004594

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20150916

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: 20151216

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: 20150916

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: 20150916

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: 20151217

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: 20150916

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: RS

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: 20150916

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: 20150916

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: 20150916

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: 20150916

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

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: 20160116

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: 20150916

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: 20150916

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: 20150916

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: 20150916

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: 20150916

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: 20150916

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: 20150916

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: 20160118

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502012004594

Country of ref document: DE

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: 20160617

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: 20150916

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: 20150916

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: 20160731

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: 20160730

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: 20150916

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: 20160801

Ref country code: CH

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

Effective date: 20160731

Ref country code: LI

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

Effective date: 20160731

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20170331

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: GB

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

Effective date: 20160730

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

Ref country code: IE

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

Effective date: 20160730

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: 20160730

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; INVALID AB INITIO

Effective date: 20120730

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: 20150916

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: 20150916

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: 20150916

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: 20150916

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: 20150916

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 750002

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170730

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: 20150916

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: 20150916

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: 20170730

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

Effective date: 20230523

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

Ref country code: DE

Payment date: 20230731

Year of fee payment: 12