EP2715078B1 - Dispositif de réglage d'arbre à cames - Google Patents

Dispositif de réglage d'arbre à cames Download PDF

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Publication number
EP2715078B1
EP2715078B1 EP12719612.9A EP12719612A EP2715078B1 EP 2715078 B1 EP2715078 B1 EP 2715078B1 EP 12719612 A EP12719612 A EP 12719612A EP 2715078 B1 EP2715078 B1 EP 2715078B1
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EP
European Patent Office
Prior art keywords
tappet
camshaft
units
axis
rotation axis
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
EP12719612.9A
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German (de)
English (en)
Other versions
EP2715078A1 (fr
Inventor
Matthias Werner
Thomas Golz
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.)
ETO Magnetic GmbH
Original Assignee
ETO Magnetic 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 ETO Magnetic GmbH filed Critical ETO Magnetic GmbH
Priority to PL12719612T priority Critical patent/PL2715078T3/pl
Publication of EP2715078A1 publication Critical patent/EP2715078A1/fr
Application granted granted Critical
Publication of EP2715078B1 publication Critical patent/EP2715078B1/fr
Active legal-status Critical Current
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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
    • 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
    • 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
    • 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
    • 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
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/101—Electromagnets

Definitions

  • the present invention relates to a camshaft adjusting device according to the preamble of patent claim 1, comprising a camshaft rotational axis defined by a camshaft, in particular a carrier shaft of a camshaft, about which the camshaft is rotatable
  • the electromagnetic multi-plunger adjusting device comprising a plurality of (typically selectively, ie independently) controllable plunger units sufficiently compact, so that on the one hand a sufficient electromagnetic functionality is ensured (such with regard to the necessary setting stroke of the tappet units and reaction or switching times), on the other hand no unwanted mutual influence - mechanical or electromagnetic - is present.
  • a camshaft adjusting device in which the cooperating with a respective drive unit ram units are arranged such that their respective ram longitudinal center axis intersects the axis of rotation of the camshaft.
  • the drive units are arranged offset in the circumferential direction of the camshaft, so that the ram longitudinal center axes of the ram units extend at an angle to each other. This results in a comparatively large necessary installation space. Also disadvantageous are manufacturing difficulties.
  • the object of the present invention is therefore to provide a camshaft adjusting device, comprising an electromagnetic multi-plunger adjusting device according to the preamble of the main claim, which is still further optimized space, while ensuring that the largest possible overlap area (contact surface) between the attack side (drive side ) End sides of the plunger units and the attack surface of the respectively associated drive unit is given.
  • camshaft adjusting device having the features of the main claim.
  • Advantageous developments of the invention are specified in the subclaims. In the context of Invention, all combinations of at least two of the features disclosed in the description, the claims and / or the figures.
  • the invention is based on the idea, in a camshaft adjusting device comprising an electromagnetic multi-plunger adjusting device, to arrange the mutually axis-parallel plunger units such that the plunger longitudinal axis of at least one of the plunger units in departure from the teaching of the prior art, preferably defined by a support shaft axis of rotation of the camshaft does not intersect, but is spaced apart in an imaginary plane in which the aforesaid axis of rotation lies and to which all ram longitudinal center axes extend perpendicularly, in particular by a dimension of more than 0.3 mm, preferably by more than 0.5 mm.
  • the invention deliberately takes the supposed disadvantage of an off-center force application of the cam member, preferably axially relative to the aforementioned axis of rotation, in order to advantageously achieve a space-optimized arrangement of the drive units with associated ram units, the arrangement according to the invention the ram units advantageously ensures that the largest possible overlap between ram units and drive units is given.
  • Each drive unit is preferably formed by one, in particular permanent magnet, armature.
  • each armature is associated with its own coil (energizable winding), wherein also a Ausfertigungsform can be realized in the example according to the in the DE 20 2008 015 980 U1 described principle, several anchors are driven by a common coil.
  • a plurality of ram longitudinal center axes in the aforementioned plane preferably spaced by the same amount from the axis of rotation of the camshaft, in particular a carrier shaft of the camshaft and at least one, preferably only one, Streteell Kunststoffsstoffachse the axis of rotation intersects.
  • the drive of the elongated (even preferably cylindrical, more preferably realized from a metal material) ram units takes place in known per se, for example in the DE 10 2007 028 600 A1 described Way in that the ram units sit on an attack surface of a respective associated drive unit (preferably there adhere by means of magnetic effect) wherein the attack surface typically forms the distal end of an anchor unit of the respective drive unit.
  • the at least one spaced in the aforementioned plane of the axis of rotation of the cam shaft ram longitudinal center axis is spaced by a minimum of 0.5 mm from the axis of rotation.
  • the distance between 0.5 mm and 8.0 mm, preferably between 1.0 mm and 5.0 mm, even more preferably between 1.0 mm and 2.0 mm, most preferably the distance is about 1.5 mm.
  • the at least one ram longitudinal center axis preferably all ram longitudinal center axes spaced from the axis of rotation of the camshaft, in the plane to the camshaft rotational axis by a dimension, in particular the same amount, which is calculated on the basis of the base circle half diameter of the associated shift groove.
  • a dimension, in particular the same amount which is calculated on the basis of the base circle half diameter of the associated shift groove.
  • the distance measured in the aforementioned plane is between about 3% and about 80%, preferably between about 3% and about 50%, even more preferably between about 3% and about 30%, even more preferably between about 3% and about 20% of this Grundnikcher penmessers the respective ram unit associated, preferably spirally extending shift groove. In general, it is preferred if the distance is less than 15% of this base circle half diameter and / or more than 5%.
  • the multi-plunger adjusting device comprises a total of at least three, preferably only three, drive units, each with an associated plunger unit, wherein the at least three plunger units, in particular the exclusively three plunger units will be explained as follows can.
  • a single one of the plurality of ram longitudinal axis axes it is possible for only a single one of the plurality of ram longitudinal axis axes to arrange the camshaft rotational axis, the further ram longitudinal center axes, preferably the two further ram longitudinal axis in the previously explained plane of the camshaft of the axis of rotation, preferably spaced by the same amount. It is particularly expedient in the case of providing a total of three tappet units with respect to the longitudinal extent of the axis of rotation medium ram unit to arrange the axis of rotation cutting.
  • At least two, preferably only two of the at least three, in particular the only three push rod longitudinal central axes intersect the camshaft rotational axis.
  • these are two adjacent to one another in the direction of the longitudinal extent of the axis of rotation of the camshaft, that is to say adjacent ram longitudinal center axes.
  • all of the at least three, preferably the only three ram longitudinal center axes in the aforementioned plane are spaced from the camshaft rotational axis, in particular by the same amount in each case.
  • each plunger longitudinal center axis defines a plunger plane that receives the respective plunger longitudinal center axis, the plunger planes arranged side by side in the direction of the longitudinal extension of the rotational axis being spaced apart by the same amount.
  • the arrangement of the plunger units becomes particularly compact in that at least one of the plunger units is seated eccentrically and / or with only a partial surface of the attack-side end face on the associated engagement surface with its attack-side end face.
  • the drive units are assigned a common housing which particularly preferably interacts with a housing guide section on the front side, which guides-typically in the form of through openings running parallel to each other, in particular through-holes-guides for the several ram units offers, which are then to be arranged relative to each other and the camshaft rotation axis, that at least one push rod longitudinal axis does not intersect the aforementioned axis of rotation.
  • Fig. 1 and 2 are exemplary embodiments of variable gas exchange valve drives for a in Fig. 1 indicated internal combustion engine 2 shown.
  • the Fig. 1 and 2 show possible embodiments of camshaft adjusting devices 3 with an electromagnetic multi-ram adjustment 4.
  • the Nockenwellenverstellvorraumen 3 according to the Fig. 1 and 2 each comprise a camshaft 5, comprising a support shaft 6 on the rotationally fixed and axially displaceable cam piece 7 is arranged with a plurality of cam lobes of different geometry.
  • the carrier shaft 6 is rotatably driven about a camshaft rotational axis D by means of the internal combustion engine 2.
  • Each of the cylindrical, elongate plunger units 9, 10, 11 defines a plunger longitudinal center axis A1, A2, A3, wherein the plunger longitudinal center axes A1, A2, A3 are arranged parallel to one another and perpendicular to the camshaft rotational axis D.
  • the plunger units 9, 10, 11 each act with a side facing away from the cam piece 7, not shown (attack side or actuator side) end face in the in the DE 10 2007 028 600 A1 described in detail with each one drive unit together, more precisely with a plane attack surface of the respective drive unit.
  • the arrangement and the interaction of the plunger units on the drive units is on the disclosure of the DE 10 2007 028 600 A1 Reference is made to the Applicant, the disclosure content of this document being deemed to be included in the present disclosure as belonging to the present invention.
  • the drive units not shown separately are accommodated in a common, cylindrical housing 14, which cooperates at the front with a housing guide portion 15 in which the plunger units 9, 10, 11 are guided longitudinally displaceable.
  • Fig. 2 results is the ram longitudinal center axis A2 of a central (second) ram unit 10 in a plane E laterally spaced or arranged offset to the camshaft rotational axis D (axis of rotation), so this does not intersect.
  • the aforesaid plane E receives the camshaft rotational axis D and extends perpendicular to all the longitudinal axis of the push rods A1, A2, A3.
  • the other two (outer) and first and second plunger units 9, 11 are arranged such that they intersect the axis of rotation D in the plane E.
  • Fig. 3 is an embodiment of a multi-plunger electromagnetic actuator 4 of an otherwise in Fig. 3 not shown camshaft adjusting device 3 shown in a view from below. Shown is the camshaft rotational axis D, which is arranged in a plane perpendicular to the longitudinal axis of the push rod A1 to A3 plane E.
  • the ram units 9, 10, 11 are longitudinally displaceably guided in the guide section 15 of the housing such that the two outer longitudinal axes A1 and A3 viewed in the direction of the longitudinal extent of the camshaft rotational axis D intersect the camshaft rotational axis D in the plane E, whereas the longitudinal axis of the ram A2 of FIG the middle ram unit 10 is arranged laterally spaced from the camshaft rotation axis D and that by the dimension a, of about 1.5 mm in the embodiment shown.
  • the two outer ram longitudinal center axes A1, A3 are in the direction of the axial extent of the camshaft rotational axis D equidistant from the central ram longitudinal center axis A2, by the dimension b of about 7 mm in the embodiment shown.
  • the diameter of the circular-cylindrical ram units 9, 10, 11 is in the embodiment about 4.5 mm.
  • the diameter of the hollow cylindrical housing 14 is about 20 mm.
  • FIG. 4 an alternative embodiment of a multi-ram adjusting device 4 of a camshaft adjusting device 3 is shown. Recognizable again is the camshaft rotational axis D, which is arranged in the plane E, to which the ram longitudinal center axes A1 to A3 are perpendicular.
  • the plunger units 9, 10, 11 are arranged such that viewed in the direction of the longitudinal extent of the camshaft rotational axis D average (second) ram unit 10 or its Streteelllindsffenachse A2 intersects the camshaft rotational axis D in the plane E, whereas in the middle St FinallyellHarsmitteachse A2 parallel ram longitudinal axis A1, A3 of the outer plunger units 9, 10 in the plane E are spaced from the camshaft rotation axis D and that by the same absolute dimension a, of about 1.5 mm in the embodiment shown. It can be seen that the outer ram longitudinal center axes A1, A3 are arranged on different sides of the camshaft rotational axis D.
  • a multi-tappet adjusting device 4 a camshaft adjusting device 3 has with the embodiment according to Fig. 3 in common that only a ram longitudinal center axis in the plane E is spaced from the camshaft rotation axis D. In contrast to the embodiment according to Fig. 3 However, it is not about the average ram longitudinal center axis, but about an outer ram longitudinal center axis A1, here the first ram unit 9, while the push rod longitudinal axes A2, A3 of the middle (second) ram unit and the third ram unit 11 intersect the camshaft rotation axis D.

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

Claims (12)

  1. Dispositif de réglage d'arbre à cames (3), comprenant un axe de rotation d'arbre à cames (D) et un dispositif électromagnétique de réglage à plusieurs poussoirs (4) avec au moins deux unités d'entraînement électromagnétiques, qui peuvent être commandées de façon à exercer une force de réglage sur un nombre correspondant d'unités de poussoir (9, 10, 11) allongées, montées à axes parallèles l'une par rapport à l'autre et définissant respectivement un axe central longitudinal de poussoir (A1, A2, A3) disposé perpendiculairement à l'axe de rotation d'arbre à cames (D), afin de s'engager avec les unités de poussoir (9, 10, 11) dans des gorges de commande (8) d'une pièce de came réglable (7), dans lequel les unités d'entraînement forment respectivement à une extrémité d'attaque respectivement associée à une des unités de poussoir (9, 10, 11) une face d'attaque déplaçable dans une direction de réglage des unités d'entraînement et une face frontale respectivement d'une des unités de poussoir (9, 10, 11) à l'opposé de la gorge de commande (8) respectivement associée coopère avec la face d'attaque,
    caractérisé en ce qu'au moins une des unités de poussoir (9, 10, 11) est disposée par rapport à l'axe de rotation d'arbre à cames (D) d'une manière telle que son axe central longitudinal de poussoir (A1, A2, A3) s'étendant parallèlement aux axes centraux longitudinaux de poussoir (A1, A2, A3) de ladite au moins une autre unité de poussoir (9, 10, 11) soit espacé de l'axe de rotation d'arbre à cames (D) dans un plan (E) contenant l'axe de rotation d'arbre à cames (D) et orienté perpendiculairement aux axes centraux longitudinaux de poussoir (A1, A2, A3).
  2. Dispositif de réglage d'arbre à cames selon la revendication 1, caractérisé en ce que ledit au moins un axe central longitudinal de poussoir (A1, A2, A3) espacé de l'axe de rotation d'arbre à cames (D) est espacé dans le plan d'une distance, mesurée perpendiculairement à l'axe de rotation d'arbre à cames (D), comprise dans une plage de valeurs entre 0,5 mm et 8,0 mm, de préférence entre 1,0 mm et 5,0 mm, et de préférence encore entre 1,0 mm et 2,0 mm.
  3. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que ledit au moins un axe central longitudinal de poussoir (A1, A2, A3) espacé de l'axe de rotation d'arbre à cames (D) est espacé de l'axe de rotation d'arbre à cames (D) dans le plan entre 3 % et 80 %, de préférence entre 3 % et 50%, de préférence encore entre 3 % et 30 %, de préférence particulière entre 3 % et 20 %, de préférence de moins de 15 %, de préférence de plus de 5 %, du demi-diamètre du cercle de base de la gorge de commande associée (8).
  4. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il est prévu au moins trois, de préférence exclusivement trois, unités d'entraînement avec des unités de poussoir correspondantes (9, 10, 11).
  5. Dispositif de réglage d'arbre à cames selon la revendication 4, caractérisé en ce qu'un seul des axes centraux longitudinaux de poussoir (A1, A2, A3), de préférence l'axe central longitudinal de poussoir (A1, A2, A3) d'une unité centrale des unités de poussoir (9, 10, 11) coupe l'axe de rotation d'arbre à cames (D).
  6. Dispositif de réglage d'arbre à cames selon la revendication 4, caractérisé en ce qu'au moins deux, de préférence exclusivement deux, en particulier deux axes centraux longitudinaux de poussoir (A1, A2, A3) extérieurs ou disposés l'un à côté de l'autre coupent l'axe de rotation d'arbre à cames (D).
  7. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que tous les axes centraux longitudinaux de poussoir (A1, A2, A3) sont dans le plan espacés de l'axe de rotation d'arbre à cames (D).
  8. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que chaque axe central longitudinal de poussoir (A1, A2, A3) définit un plan de poussoir traversé perpendiculairement par l'axe de rotation d'arbre à cames (D), et en ce que la distance mesurée dans la direction de l'extension longitudinale de l'axe de rotation d'arbre à came (D) entre chaque fois deux plans de poussoir voisins est la même pour tous les plans de poussoir respectivement voisins.
  9. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moins une des unités de poussoir (9, 10, 11) s'applique avec sa face frontale côté d'attaque de façon excentrique et/ou avec seulement une surface partielle de la face frontale côté d'attaque sur la face d'attaque correspondante.
  10. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que les unités d'entraînement sont disposées dans un boîtier commun (14), de préférence cylindrique creux.
  11. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que les unités de poussoir (9, 10, 11) sont fixées à au moins une unité d'actionneur par adhérence magnétique.
  12. Dispositif de réglage d'arbre à cames selon l'une quelconque des revendications précédentes, caractérisé en ce que les unités de poussoir (9, 10, 11) présentent respectivement une extrémité d'engagement durcie, venant en interaction avec au moins une des gorges de commande (8).
EP12719612.9A 2011-05-30 2012-04-18 Dispositif de réglage d'arbre à cames Active EP2715078B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL12719612T PL2715078T3 (pl) 2011-05-30 2012-04-18 Układ przestawiania wału krzywkowego

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011050730A DE102011050730A1 (de) 2011-05-30 2011-05-30 Nockenwellenverstellvorrichtung
PCT/EP2012/057039 WO2012163591A1 (fr) 2011-05-30 2012-04-18 Dispositif de réglage d'arbre à cames

Publications (2)

Publication Number Publication Date
EP2715078A1 EP2715078A1 (fr) 2014-04-09
EP2715078B1 true EP2715078B1 (fr) 2015-01-07

Family

ID=46046130

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12719612.9A Active EP2715078B1 (fr) 2011-05-30 2012-04-18 Dispositif de réglage d'arbre à cames

Country Status (6)

Country Link
US (1) US8939119B2 (fr)
EP (1) EP2715078B1 (fr)
CN (1) CN103597175B (fr)
DE (1) DE102011050730A1 (fr)
PL (1) PL2715078T3 (fr)
WO (1) WO2012163591A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013108027A1 (de) * 2013-07-26 2015-01-29 Eto Magnetic Gmbh Elektromagnetische Stellvorrichtung und System zur Verstellung einer Funktionalität eines Kraftfahrzeugaggregats
DE102014008156B4 (de) * 2014-05-30 2022-04-14 Daimler Ag Ventiltrieb für eine Brennkraftmaschine
EP3016117B1 (fr) 2014-10-31 2017-12-06 Husco Automotive Holdings LLC Appareil d'actionneur de broche-poussoir
CN105863765A (zh) * 2016-05-18 2016-08-17 宁波圣龙汽车动力系统股份有限公司 气门升程可变的滑动式凸轮轴
CN106121764A (zh) * 2016-07-18 2016-11-16 杰锋汽车动力系统股份有限公司 一种用于可变气门升程系统的凸轮轴调节装置
JP7153586B2 (ja) * 2019-02-27 2022-10-14 株式会社オティックス 内燃機関の可変動弁機構

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10360287A1 (de) * 2003-02-05 2004-10-14 Ina-Schaeffler Kg Stößel in einem Ventiltrieb einer Brennkraftmaschine
DE102004037198A1 (de) * 2004-07-30 2006-03-23 Ina-Schaeffler Kg Ventiltrieb einer Brennkraftmaschine
DE102006051809A1 (de) 2006-11-03 2008-05-08 Schaeffler Kg Stellvorrichtung
DE102007028600B4 (de) 2007-06-19 2011-06-22 ETO MAGNETIC GmbH, 78333 Elektromagnetische Stellvorrichtung
DE102007040677A1 (de) 2007-08-29 2009-03-05 Schaeffler Kg Brennkraftmaschine mit variablem Gaswechselventiltrieb
DE102007057811B4 (de) * 2007-11-30 2015-04-30 Volkswagen Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
WO2010012498A1 (fr) * 2008-08-01 2010-02-04 Eto Magnetic Gmbh Dispositif de réglage électromagnétique
DE202008015980U1 (de) 2008-12-03 2010-04-29 Eto Magnetic Gmbh Elektromagnetische Aktuatorvorrichtung
DE102009015486A1 (de) * 2009-03-28 2010-09-30 Schaeffler Technologies Gmbh & Co. Kg Elektromagnetischer Aktuator
DE102009030375A1 (de) 2009-06-25 2010-12-30 Schaeffler Technologies Gmbh & Co. Kg Elektromagnetische Stellvorrichtung

Also Published As

Publication number Publication date
PL2715078T3 (pl) 2015-04-30
US20140190430A1 (en) 2014-07-10
DE102011050730A1 (de) 2012-12-06
CN103597175B (zh) 2016-09-07
CN103597175A (zh) 2014-02-19
US8939119B2 (en) 2015-01-27
WO2012163591A1 (fr) 2012-12-06
EP2715078A1 (fr) 2014-04-09

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