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EP2196638B1 - Commande de soupape destinée à actionner des soupapes d'échange des gaz de moteurs à combustion interne - Google Patents

Commande de soupape destinée à actionner des soupapes d'échange des gaz de moteurs à combustion interne Download PDF

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Publication number
EP2196638B1
EP2196638B1 EP09400058A EP09400058A EP2196638B1 EP 2196638 B1 EP2196638 B1 EP 2196638B1 EP 09400058 A EP09400058 A EP 09400058A EP 09400058 A EP09400058 A EP 09400058A EP 2196638 B1 EP2196638 B1 EP 2196638B1
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EP
European Patent Office
Prior art keywords
camshaft
contour
cam
valve drive
adjusting
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
EP09400058A
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German (de)
English (en)
Other versions
EP2196638A1 (fr
Inventor
Heiko Neukirchner
Jörg Dr. Ross
Andreas Werler
Jörg Wutzler
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.)
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Original Assignee
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
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
Priority claimed from DE102008061440A external-priority patent/DE102008061440B3/de
Priority claimed from DE102009057691A external-priority patent/DE102009057691A1/de
Application filed by IAV GmbH Ingenieurgesellschaft Auto und Verkehr filed Critical IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Publication of EP2196638A1 publication Critical patent/EP2196638A1/fr
Application granted granted Critical
Publication of EP2196638B1 publication Critical patent/EP2196638B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L2013/0052—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 with cams provided on an axially slidable sleeve

Definitions

  • the invention relates to a valve train for actuating gas exchange valves of internal combustion engines with the features mentioned in the preamble of claim 1.
  • the DE 100 54 623 A1 describes a device for switching a cam package on a camshaft for actuating gas exchange valves, wherein the cam assembly is guided axially displaceably on the camshaft. According to the position of the cam package, the gas exchange valve is in operative connection with different cam contours.
  • the adjustment of the cam package via an actuator in cooperation with a slide track.
  • the adjusting element is a pin which can be displaced radially outwards and cooperates with at least two cam tracks formed in a guide part which is arranged around the cam pack by about 180 ° in the extended state.
  • a major disadvantage of DE 100 54 623 A1 is that to switch to another cam contour of the pin extended from the camshaft and must be meshed in an axially displaceable shift gate. After switching, the pin must be retracted. This construction is very part and production-consuming and there is a risk of damage to the camshaft Malfunction of the pin.
  • Another disadvantage is that the motor speed is limited by the necessary actuating time of the pin. In addition, the adjustment depends on the existing oil pressure.
  • From the DE 10 2004 033 798 A1 is a valve lift switching for gas exchange valves of an internal combustion engine between two different cam contours by means of a rotatably but axially displaceable arranged on the housing of the engine shift gate known.
  • the shift gate partially comprises the camshaft and is provided with a counter-rotating direction of rotation of the camshaft Kulissennut whose side walls each form a slotted edge which is mutually engageable for valve lift in operative connection with a both sides on an axially displaceable second cam contour contact surface.
  • the axially displaceable second cam contour is either pushed over a cam contour of the cam firmly connected to the camshaft or pushed away from the cam contour, so that optionally two different cam contours can be brought into operative connection with the gas exchange valve.
  • the DE 10 2004 055 852 A1 relates to a valve train for an internal combustion engine, in particular for selective cylinder connection.
  • a cam device is arranged axially displaceably on a camshaft driven by the crankshaft.
  • the axial displacement of the cam device is effected by a fork-like design shift gate, which is axially displaceable via a drive spindle.
  • To shift the cam device are mutually the contact surfaces of the shift finger of the fork-like shift gate with the cam device in operative connection can be brought.
  • the disadvantage here is that can not be avoided by the introduced via the drive spindle cam shift errors.
  • the invention has for its object to provide a generic valve train for operating gas exchange valves of internal combustion engines, with a low technical complexity, a small size and low applied switching forces Ventilhubumscnies is made, with malfunction and damage to the camshaft in the valve lift also be avoided at high engine speeds.
  • an adjusting shaft which can be rotated by the camshaft is arranged parallel to a camshaft, on which two adjusting devices are rotatably mounted and two drivers which are axially displaceable on the adjusting shaft between the adjusting devices.
  • the drivers are fixed to an axially displaceable switching gate for valve switching between two different cam profiles of an axially displaceable on the camshaft cam package connected.
  • the end faces of the carriers arranged between the adjusting devices are provided with a contour, which in each case are operatively connected via a contour arranged on the adjusting device or a guide pin.
  • the contours of the two drivers are arranged offset by 180 °.
  • the carriers By rotating the adjusting shaft, the carriers are axially displaced on the adjusting shaft by the guide pins sliding on the contour.
  • the adjusting shaft is switchably engageable and separable via a control gear with the camshaft.
  • the adjusting gear for connecting and disconnecting the camshaft with the adjusting shaft is a toothed gear in which a gear is arranged axially displaceable and rotationally fixed on the adjusting shaft, which is switchably engageable and separable with a camshaft fixed to the toothed segment engageable.
  • the actuating gear for connecting and disconnecting the camshaft with the adjusting shaft consists of a lever system and a profiled link member.
  • the advantage of the solution according to the invention is that with a low effort and a small space required a safe valve lift switching between different cam contours takes place. Due to the controlled rotation of the adjusting shaft via the camshaft and thus the positively controlled displacement of the shift gate, faulty switching during valve lift switching is avoided. Another advantage is that with the solution according to the invention a valve lift switching between two or more cam profiles can be performed.
  • the fact that the members of the adjusting gear are designed as a gate part and lever system, it is achieved that during a switching operation, a gradual engagement of the gear members takes place with each other. As a result, switching shocks and short-term occurring in the control gear peak forces are avoided.
  • the Indian FIG. 1 illustrated valve train according to the invention for the actuation of gas exchange valves consists of a driven by a crankshaft of the internal combustion engine camshaft 1, which parallel to an adjusting 12 for actuating a valve lift switching between two different cam profiles 15; 16 is arranged.
  • an adjustment of two valves of a cylinder takes place.
  • An application of the solution according to the invention can also be used analogously for several cylinders.
  • On the camshaft 1 is rotatably and axially displaceably a cam package 2 is mounted on the camshaft 1 is rotatably and axially displaceably a cam package 2 is mounted on the camshaft 1 is rotatably and axially displaceably a cam package 2 is mounted.
  • the cam package 2 consists of four cams, of which two adjacent cams each have a large cam profile 15 and a small cam profile 16.
  • the cam package 2 can, as in FIGS.
  • FIG. 4 is a switching position shown, in each of which the small cam profile 16 is in operative connection with the gas exchange valves. In this switching position, the small cam profile 16 is above the base circle profile 14.
  • FIG. 5 is a switching position shown, in which the gas exchange valves are actuated by the large cam profiles 15.
  • a detent element is arranged between the displaceable cam part and the camshaft 1.
  • cam package 2 it is also possible to form the cam package 2 as a component which is non-rotatably connected to the camshaft 1, but is axially displaceable on this. It is necessary that the large cam profile 15 and the small cam profile 16 are each provided with a uniform base circle profile 14.
  • a pin 4 is fixed, which is engageable with the inner surfaces of a widening cam groove 20 of an axially movable shift gate 3 for moving the cam package 2 in engagement.
  • the shift gate 3 partially comprises the camshaft 1 and is provided with a groove groove 20 that widens against the direction of rotation of the camshaft 1.
  • the pin 4 passes through the cam groove 20 of the shift gate 3 with each rotation of the camshaft 1.
  • the pin 4 is arranged on the cam package 2, that the axis of the pin 4 is arranged in accordance with a suitable for the phase of the base circle 14 switching, as in FIGS. 4 and 5 shown.
  • a driver 5 Fixed 23, which are mounted axially displaceable on the adjusting shaft 12.
  • a contour 21 On the outer end face of the driver 5 is a contour 21 and on the outer end face of the driver 23 is a contour 22 is arranged.
  • the two drivers 5; 23 are on the adjusting shaft 12 between two on the adjusting shaft 12 rotatably arranged adjusting devices 10; 17 arranged.
  • a guide pin 18 is fixed, which is in operative connection with the contour 21 of the driver 5 stands.
  • a guide pin 24 is fixed, which is in operative connection with the contour 22 of the driver 23.
  • the engagement of the guide pin 18 of the adjusting device 10 on the contour 21 of the driver 5 is arranged offset from the engagement of the guide pin 24 of the adjusting device 17 on the contour 22 of the driver 23 by 180 °.
  • the axes of the guide pins 18; 24 are in an axial direction and the contours 21; 22 are offset from each other by 180 °, or the contours 21; 22 are arranged identically and the guide pins 18; 24 are offset from each other by 180 °.
  • the rotation of the adjusting shaft 12 is effected by the camshaft 1, wherein the adjusting shaft 12 via a control gear with the camshaft 1 switchably engageable and separable.
  • the adjusting gear for connecting and disconnecting the camshaft 1 with the adjusting shaft 12 is, according to a first variant, a gear transmission.
  • a gear 7 is rotatably mounted on the adjusting shaft 12, but axially displaceable.
  • the gear 7 is connected to a drive 6, which extends an adjusting bolt 19 when operating.
  • the axially displaceable gear 7 engages in a toothed segment 8 located on the camshaft 1.
  • the toothed segment 8 extends on the camshaft 1 upon actuation of two gas exchange valves over an angular range of 180 ° and is arranged so that a displacement of the driver 5; 23 takes place only when the pin 4 is outside the sliding groove 20.
  • the toothed segment 8 would only extend over an angular range of 90 °.
  • FIG. 6 a valvetrain is shown, was activated by the commissioning of the drive 6, the switching operation of the intervention of the no cam profile 16 with the gas exchange valves to the large cam profile 15.
  • the cam package 2 is located in front of the initiation of the switching in the in FIG. 4 shown position.
  • the gear 7 is displaced on the adjusting shaft 12 in such a way by the adjusting bolt 19 that it comes into engagement with the toothed segment 8 arranged on the camshaft 1.
  • a displacement of the gear 7 takes place only if it is ensured that in the actual displacement operation no engagement of the gear 7 can be done with the sector gear 8.
  • FIG. 7 shows an intermediate position of the valve lift by the adjusting 12.
  • the adjusting 12 By the rotation of the adjusting 12 at the same time on the adjusting shaft 12 rotatably arranged adjusting 10; 17 and thus the guide pins 18 fixed thereto; 24 twisted. Since the guide pins 18; 24 with each offset by 180 ° arranged contour 21; 22 of the driver 5; 23 are in operative contact, there is an axial displacement of the two drivers 5; 23 on the adjusting shaft 12 in the direction of the adjusting device 17.
  • the driver 5; 23 takes place at the same time an axial displacement of the shift gate 3.
  • FIG. 8 is the side view according to the FIG. 7 and in FIG. 9 the corresponding plan view shown. In the FIG. 8 one can clearly see the interaction of the guide pins 18; 24 with the respective contour 21; 22 of the driver 5; 23 recognize.
  • the contour 21; 22 of the driver 5; 23 is arranged so that a phase-correct switching of the shift gate 3 takes place.
  • a locking device is arranged on the adjusting device 10 or 17.
  • the locking device consists of a spring 11 and a ball 13 which engages in a correspondingly arranged in the adjusting device 10 or 17 recess. In the FIG. 2 you can recognize the latched in the recess 10 of the adjusting balls 13.
  • the drive 6 is deactivated and by the spring force of the adjustment direction of the drive 6 counteracting spring 9, the gear 7 is moved out of the engagement region of the toothed segment 8.
  • FIG. 1 This position is shown with already protestverschobenem gear 7.
  • the cam package 2 is locked in the newly reached switching position. Due to the arrangement of the switching gate 3 and the pin 4 is achieved that a displacement of the cam assembly 2 and thus a valve lift switching only takes place when the respective base circle profile 14 of the camshaft 1 is in operative connection with a gas exchange valve.
  • a return adjustment is analogous to the above description, whereby by the with the contours 21; 22 operatively connected guide pins 18; 24, the drivers 5; 23 are moved in the direction of the adjusting device 10.
  • FIGS. 10 to 12 a variant of the solution according to the invention is shown.
  • the same reference numerals have been used for the same components.
  • the cam package 2 has in each case a small cam profile 16, a central cam profile 25 and a large cam profile 15, so that a valve changeover can take place between three different cam profiles.
  • the shift gate 3 is about two drivers 5; 23 connected axially displaceable.
  • the drivers 5 and 23 can, as in FIG. 10 represented, interconnected and form a component or, as in FIG. 11 shown, split executed.
  • the drivers 5 and 23 are, as described above, axially displaceably mounted on the adjusting shaft 12 between the two adjusting devices 10 and 17.
  • the first adjusting device 10 is operatively connected to the first contour 21 of the first driver 5 via a first mating contour 26 arranged thereon.
  • the second adjusting device 17 is operatively connected to the second contour 22 of the second driver 23 via a second mating contour 27 arranged thereon.
  • the first contour 21 is operatively connected via a guide pin 18 arranged on the first adjusting device 10 and the second contour 22 via a guide pin 24 arranged on the second adjusting device 17. It is also possible, instead of in the preceding examples described guide pins 18 and 24 to the adjusting devices 10 and 17 corresponding counter-contours 26 and 27 to arrange.
  • the rotation of the adjusting shaft 12 also takes place via a control gear in which the adjusting shaft 12 is engageably engaged with the camshaft 1 and separated.
  • the adjusting gear for rotating the adjusting shaft 12 is here, according to a second variant, formed from a lever system 28 and a profiled link member 29.
  • the adjusting gear for rotating the adjusting shaft 12 in this case consists of one on the adjusting shaft 12 fixedly arranged or multi-armed lever system 28 and an axially displaceable on the camshaft 1 and rotatably arranged profiled link member 29, wherein the profiled link member 29 switchable with the lever system 28 into engagement Can be brought and separated.
  • the lever system 28 is arranged axially displaceably on the camshaft 1 and the link member 29 fixed on the adjusting shaft 12.
  • the actuating gear is shown in a rest or detent position in which the link member 29 is not engaged with the lever system 28. In this position, there is no displacement of the driver 5 and 23 and thus no switching to another cam profile.
  • the link member 29 is preferably formed as a cam, which is axially displaced by an actuator 30 on the camshaft 1 to initiate the switchover to another cam contour.
  • the axial displacement of the cam member 29 and optionally of the actuator 30 is shown on the camshaft 1 by a double arrow.
  • the provision of the gate part 29 in the rest or detent position is supported by a force acting on the cam member 29 spring 32.
  • the lever system 28 shown in the embodiment is designed as a four-stage lever system 28, at the ends of each lever a roller 31 is arranged.
  • the lever ends may also be formed as a corresponding sliding surface, not shown.
  • the slide member 29 is axially displaced on the camshaft 1 by actuation of the actuator 30 so that the slide member 29 comes into operative engagement with a roller 31 of the lever system 28 ,
  • the engagement of the link member 29 is shown with the lever system 28.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Mechanically-Actuated Valves (AREA)

Claims (13)

  1. Commande de soupape pour l'actionnement de soupapes d'échange de gaz de moteurs à combustion interne présentant la conception suivante :
    - au moins un arbre à cames (1) entraîné par un vilebrequin du moteur à combustion interne,
    - des cames disposées sur l'arbre à cames (1) et coulissant axialement, qui sont directement ou par le biais d'éléments intermédiaires en liaison active avec la soupape d'échange de gaz concernée,
    - une coulisse de commutation (3) disposée de façon à pouvoir coulisser axialement sur le carter du moteur à combustion interne, qui est dotée d'une rainure de coulisse (20) s'étendant dans le sens contraire au sens de rotation de l'arbre à cames (1), qui peut être mise en liaison active alternativement avec des surfaces de butée d'un contour de came coulissant pour la commutation de la levée de soupape entre différents profils de came (15 ; 16 ; 25),
    - la coulisse de commutation (3) étant reliée à deux entraîneurs (5 ; 23) de façon à pouvoir coulisser axialement,
    - les deux entraîneurs (5 ; 23) étant logés sur un arbre de réglage (12) susceptible de tourner, de façon à pouvoir coulisser axialement entre deux dispositifs de réglage (10 ; 17),
    - les faces frontales, des entraîneurs (5 ; 23) dirigées à chaque fois en direction des dispositifs de réglage (10 ; 17), étant dotées chacune d'un contour (21 ; 22), caractérisée en ce que
    - le premier contour (21) du premier entraîneur (5) est en liaison active au moyen d'un premier contour opposé (26) avec le premier dispositif de réglage (10) logé de façon solidaire en rotation sur l'arbre de réglage (12),
    - le second contour (22) du second entraîneur (23) est en liaison active au moyen d'un second contour opposé (27) avec le second dispositif de réglage (17) logé de façon solidaire en rotation sur l'arbre de réglage (12),
    - l'arbre de réglage (12) peut être mis en prise de façon commutable avec l'arbre à cames (1) au moyen d'un mécanisme de réglage pour la rotation de l'arbre de réglage (12) et peut être séparé.
  2. Commande de soupape selon la revendication 1,
    caractérisée en ce que
    le mécanisme de réglage pour la liaison et la séparation de l'arbre à cames (1) avec le dispositif de réglage (12) est un engrenage, dans lequel une roue dentée (7) est disposée sur l'arbre de réglage (12) de façon à pouvoir coulisser axialement et de façon solidaire en rotation, laquelle roue peut être mise en prise de façon commutable avec un segment denté (8) disposé de façon fixe sur l'arbre à cames (1) et peut être séparée.
  3. Commande de soupape selon la revendication 1,
    caractérisée en ce que
    le mécanisme de réglage pour la liaison et la séparation de l'arbre à cames (1) avec l'arbre de réglage (12) comprend un système de levier (28) et une partie de coulisse (29) profilée.
  4. Commande de soupape selon la revendication 3,
    caractérisée en ce que
    le système de levier (28) conçu avec un ou plusieurs bras est disposé de façon fixe sur l'arbre de réglage (12) et la partie de coulisse (29) profilée est disposée de façon à pouvoir coulisser axialement et de façon solidaire en rotation sur l'arbre à cames (1), la partie de coulisse (29) profilée pouvant être mise en prise par un actionneur (30) de façon commutable avec le système de levier (28) et pouvant être séparée.
  5. Commande de soupape selon la revendication 3,
    caractérisée en ce que
    le système de levier (28) conçu avec un ou plusieurs bras est disposé de façon à pouvoir coulisser axialement et de façon solidaire en rotation sur l'arbre à cames (1) et la partie de coulisse (29) profilée est disposée fixement sur l'arbre de réglage (12), le système de levier (28) pouvant être mis en prise par un actionneur (30) de façon commutable avec la partie de coulisse (29) profilée et pouvant être séparé.
  6. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce
    qu'un ensemble de cames (2) disposé de façon à pouvoir coulisser axialement et de façon solidaire en rotation sur l'arbre à cames (1) est relié fixement à une broche (4), qui peut être mise en prise pour la commutation de soupape avec les côtés intérieurs de la rainure de coulisse (20), s'étendant dans le sens contraire au sens de rotation de l'arbre à cames (1), de la coulisse de commutation (3).
  7. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le premier contour opposé (26) du premier dispositif de réglage (10) est conçu comme première goupille de guidage (18) et le second contour opposé (27) du second dispositif de réglage (17) comme seconde goupille de guidage (24).
  8. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le premier entraîneur (5) et le second entraîneur (23) sont reliés l'un à l'autre.
  9. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    l'engagement du premier contour opposé (26) ou de la première goupille de guidage (18) du premier dispositif de réglage (10) est disposé sur le premier contour (21) du premier entraîneur (5) décalé de 180° par rapport à l'engagement du second contour opposé (27) ou de la seconde goupille de guidage (24) du second dispositif de réglage (17) sur le second contour (22) du second entraîneur (23).
  10. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    le système de levier (28) est conçu de préférence sous forme de système de levier (28) à quatre bras, sur chacune des extrémités duquel est disposé un galet (31), ou bien les extrémités de levier sont conçues sous forme de surfaces de glissement.
  11. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce
    qu'un dispositif de réglage (10 ou 17) est doté d'un dispositif d'arrêt comprenant au moins un ressort (11) et au moins une bille (13).
  12. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce
    qu'un ressort (9), dont la force est orientée dans le sens contraire au sens de coulissement de l'entraînement (6), est disposé sur la roue dentée (7).
  13. Commande de soupape selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    la partie de coulisse (29) est conçue comme une came.
EP09400058A 2008-12-10 2009-12-08 Commande de soupape destinée à actionner des soupapes d'échange des gaz de moteurs à combustion interne Active EP2196638B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008061440A DE102008061440B3 (de) 2008-12-10 2008-12-10 Ventiltrieb zur Betätigung von Gaswechselventilen von Brennkraftmaschinen
DE102009057691A DE102009057691A1 (de) 2009-12-07 2009-12-07 Ventiltrieb zur Betätigung von Gaswechselventilen von Brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP2196638A1 EP2196638A1 (fr) 2010-06-16
EP2196638B1 true EP2196638B1 (fr) 2011-04-13

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EP (1) EP2196638B1 (fr)
AT (1) ATE505625T1 (fr)

Cited By (1)

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DE102011101868A1 (de) 2011-05-16 2012-11-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Vorrichtung zur Variation des Ladungswechselventilhubes bei einer Verbrennungskraftmaschine

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DE102010048005A1 (de) 2010-10-08 2012-04-12 Schaeffler Technologies Gmbh & Co. Kg Aktorvorrichtung zur Verstellung eines Schiebenockensystems
DE102011101871B4 (de) 2011-05-16 2014-09-25 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Brennkraftmaschinen zur Betätigung von Gaswechselventilen
DE102011108728B4 (de) 2011-07-27 2013-02-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Brennkraftmaschinen zur Betätigung von Gaswechselventilen
AT515734B1 (de) * 2014-04-24 2016-05-15 Avl List Gmbh Ventilbetätigungseinrichtung für eine brennkraftmaschine

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JPH033907A (ja) * 1989-05-31 1991-01-10 Isuzu Motors Ltd 可変バルブタイミング・リフト装置
DE10054623A1 (de) * 2000-11-03 2002-05-08 Audi Ag Vorrichtung zum Umschalten zumindest eines Nockenpaketes
DE102004033798B4 (de) 2004-07-12 2015-12-17 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb zur Betätigung von Gaswechselventilen von Brennkraftmaschinen
DE102004055852A1 (de) 2004-09-30 2006-04-13 Bayerische Motoren Werke Ag Ventiltrieb für eine Brennkraftmaschine, insbesondere zur selektiven Zylinderzuschaltung
DE102007010157A1 (de) * 2007-03-02 2008-06-26 Audi Ag Ventiltrieb einer Brennkraftmaschine mit dreistufigen Nockenprofilgruppen und axial beweglichen Kulissen- oder Eingriffselementen

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Publication number Priority date Publication date Assignee Title
DE102011101868A1 (de) 2011-05-16 2012-11-22 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Vorrichtung zur Variation des Ladungswechselventilhubes bei einer Verbrennungskraftmaschine
DE102011101868B4 (de) * 2011-05-16 2013-02-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Vorrichtung zur Variation des Ladungswechselventilhubes bei einer Verbrennungskraftmaschine

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