EP3180498B1 - Arbre à cames avec bloc de cames coulissantes - Google Patents

Arbre à cames avec bloc de cames coulissantes Download PDF

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Publication number
EP3180498B1
EP3180498B1 EP15734411.0A EP15734411A EP3180498B1 EP 3180498 B1 EP3180498 B1 EP 3180498B1 EP 15734411 A EP15734411 A EP 15734411A EP 3180498 B1 EP3180498 B1 EP 3180498B1
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EP
European Patent Office
Prior art keywords
sliding cam
needle bearing
camshaft
longitudinal groove
passage
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
EP15734411.0A
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German (de)
English (en)
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EP3180498A1 (fr
Inventor
Marcel WEIDAUER
Tobias Mehlhorn
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.)
Thyssenkrupp Dynamic Components Teccenter AG
Original Assignee
ThyssenKrupp Presta TecCenter AG
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Publication of EP3180498A1 publication Critical patent/EP3180498A1/fr
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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
    • F01L1/053—Camshafts overhead type
    • 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 present invention relates to a camshaft to the valve train of an internal combustion engine having a fundamental and at least one sliding cam package comprising a plurality of cam profiles, wherein the fundamental shaft extends through a passage in the sliding cam package, so that it is received axially displaceably on the fundamental shaft, and means for forming a torque transmitting connection between the fundamental and the sliding cam package are provided.
  • Camshafts with sliding cam packs are used for variable valve train for an internal combustion engine and depending on an axial position of the sliding cam package on the fundamental shaft, a tap element for valve control with different, adjacent to each other formed on the sliding cam package cam profiles cooperate.
  • the lifting information is stored in the specific cam profile and may include, for example, different sized valve strokes or a so-called zero stroke.
  • this comprises, in addition to the cam profiles, an adjusting element in which an adjusting element engages, which is arranged in a stationary manner in the receiving body for receiving the camshaft.
  • a receiving body which can be formed for example by a camshaft module in the manner of a hood, which can be applied with pre-assembled camshafts on the cylinder head of the internal combustion engine.
  • Camshafts with a basic shaft and several sliding cam packages can also be mounted directly in the cylinder head itself.
  • camshafts For mounting the camshaft in the receiving body, it is possible to store the sliding cam packages themselves in associated bearing blocks of the receiving body, ie to receive rotatable, then the fundamental wave through the Pass sliding cam packages, which then drives them only rotating.
  • camshafts having a base shaft and a plurality of sliding cam packages applied to the fundamental shaft may also be preassembled, and the preassembled camshaft is then mounted in the receiving body.
  • the camshaft is preferably mounted on the fundamental shaft, for example via corresponding bearing rings, which are applied to the fundamental shaft.
  • the sliding cam packages are freely supported on the basic shaft, and via the means for torque-transmitting connection, the sliding cam packages rotate with the rotation of the fundamental shaft, while the sliding cam packages remain axially displaceable on the fundamental shaft.
  • the shows DE 10 2008 005 639 A1 a camshaft to the valve train of an internal combustion engine with a basic shaft and with sliding cam packages, which have a plurality of cam profiles.
  • the basic shaft extends through a passage in the sliding cam package, wherein means for forming a torque-transmitting connection between the fundamental shaft and the sliding cam package are formed, which are based on a sliding cam teeth between the outside of the basic shaft and the passage of the sliding cam package.
  • a problem with this is that due to manufacturing tolerances of the sliding toothing and concomitant inaccuracies in the radial guidance, inadmissibly high base circle deviations of the cam profiles of the sliding cam package can occur in arrangement on the fundamental shaft.
  • the DE 10 2011 000 511 A1 shows for a generic type camshaft means for forming a torque transmitting connection between the fundamental shaft and the sliding cam package, which are formed as sliding blocks.
  • the fundamental wave must be performed as a solid shaft, otherwise the nuts can not be absorbed in the fundamental wave.
  • the DE 102011 000 510 A1 shows a generic camshaft, and the means for forming a torque-transmitting connection between the basic shaft and the sliding cam package comprise a plurality of balls forming a linear roller bearing for axially displaceable receiving the sliding cam package on the fundamental shaft. Since the sliding cam package is always seated and operated in discrete positions on the basic shaft depending on the cam profiles, there may be the disadvantage that due to the high Hertzian pressure, the balls in the associated recesses can press into the surface of the recesses over a longer service life so that a rotational clearance of the sliding cam package can arise on the fundamental. Further, the balls form only a point contact with the recess in the passage of the sliding cam package or in the outer side of the fundamental shaft, whereby only small torques between the sliding cam package and the fundamental can be transmitted.
  • JP 2008 208737 A is also shown a camshaft in which needle bearing elements are used to allow only a rotation of the cam elements of the camshaft, which, however, in comparison to DE 10 2011 000 510 A1 no rolling function for axially displaceable receiving the cam element on the fundamental meet.
  • WO 2015/176874 A1 is a camshaft to the valve train of an internal combustion engine with a fundamental and at least one sliding cam package comprising a plurality of cam profiles has become known, wherein the fundamental wave through a passage in the sliding cam package through extends so that it is received axially displaceably on the basic shaft, and wherein means for forming a torque transmitting connection between the fundamental shaft and the sliding cam package are provided, wherein the means comprise elongated needle bearing elements, which with a first part of its circular cross-section in a longitudinal groove in the passage of Insert sliding cam pack and locate with a second part of the same cross-section in a longitudinal groove in the outside of the basic shaft.
  • the object of the invention is the improved design of means for forming a torque-transmitting connection between a fundamental and a sliding cam package of a camshaft, the means should be formed as low as possible and it should also be avoided over a prolonged period of use of the camshaft a game between the sliding cam package and the fundamental become. In particular, high surface pressures in contact of the means to the passage of the sliding cam package should be avoided.
  • the invention includes the technical teaching that the means comprise longitudinally formed needle bearing elements which are seated with a first part of their circular cross-section in a longitudinal groove in the passage of the sliding cam package and which are located with a second part of the same cross-section in a longitudinal groove in the outside of the fundamental shaft, wherein the longitudinal groove in the passage of the sliding cam package has a deviating from a circular cross-sectional contour.
  • the formation of the means as a needle bearing elements leads to a wear minimum and permanent formation of a torque transmitting connection between the fundamental and the sliding cam package, and in the Substantially half the insertion of the needle bearing elements both in a longitudinal groove in the passage of the sliding cam element and in a longitudinal groove in the outside of the fundamental shaft allows a force distribution in the contact area between the needle bearing elements and the longitudinal grooves, are avoided in the high force peaks. Due to the cylindrical shape of the needle bearing elements, a curvature-curvature contact is formed in a line shape, so that the stresses of the Hertzian pressure between the needle bearing elements and the longitudinal grooves are minimized.
  • a camshaft can be provided to the valvetrain of an internal combustion engine that does not require the use of splines between the shift cam package and the fundamental shaft, and by the use of the needle bearing members, a high force transmission between the shift cam package and the fundamental shaft is enabled, without the contact force in the circumferential direction leads to increased wear.
  • the longitudinal groove in the outer side of the fundamental wave can have a semicircular cross section which corresponds to the circular cross section of the needle bearing elements.
  • the circular cross-section may have the same radius as the cylindrical shape of the needle bearing elements, and sit the needle bearing elements in this semicircular cross-section, then arises over the semicircular cross-section of the needle bearing elements play-free surface contact in the surface of the longitudinal groove.
  • the needle bearing elements can be displaced by the large contact surface wear minimum in the longitudinal groove in the outer side of the fundamental shaft when the sliding cam package is axially displaced on the fundamental shaft.
  • the needle bearing elements can be accommodated axially fixed in the longitudinal grooves in the passage of the sliding cam package, so that they move along with the axial movement of the sliding cam package.
  • the longitudinal groove in the passage of the sliding cam package has a cross-sectional contour deviating from a circular arc.
  • the deviation can take place in various ways, in particular, the deviation can be designed so that two contact areas for transmitting a contact force between the Needle bearing elements and the sliding cam package are formed in the circumferential direction, as explained in more detail below in two variants.
  • the cross-sectional contour of the longitudinal groove in the passage of the sliding cam package may be defined by two, in particular merging radii which are larger than the diameter of the needle bearing elements, so that two opposite contact areas are formed for contact of the needle bearing element.
  • the radius of the longitudinal groove in the passage of the sliding cam element deviates from the radius of the needle bearing elements, which serves to form the circumferentially approximately opposite defined contact areas.
  • the sliding cam package is preferably made of hardened bearing steel, the special geometry is formed there.
  • the semicircular shape is preferred, which is adapted to the geometry of the needle bearing elements, in order to achieve as far as possible no differences in radii. As a result, the load in the fundamental wave is reduced and the shaft material can meet lower requirements.
  • the cross-sectional contour of the longitudinal groove in the passage of the sliding cam package may have a trapezoidal shape, so that two opposite contact areas are also formed for the contact of the needle bearing element.
  • the dome shape so that the cross section of the longitudinal groove in the passage of the sliding cam package can be performed according to a trapezoidal shape, and the direction of the load attack can thus also be selectively changed.
  • the shape can be reproduced more easily in terms of manufacturing technology than the dome shape and the influence of the manufacturing tolerances on the resulting load direction is lower.
  • the trapezoidal shape has two obliquely arranged trapezoidal flanks, which are connected by a trapezoidal base.
  • the longitudinal groove in the outer side of the fundamental shaft can be formed axially parallel to the extension of the fundamental shaft and / or one and preferably at least two needle bearing elements can be accommodated in a longitudinal groove.
  • a plurality of longitudinal grooves can be provided on the circumference of the basic shaft, distributed equally or unequally, for example two, preferably three and particularly preferably four or more than four longitudinal grooves.
  • a preferably corresponding number of longitudinal grooves can be provided in the passage of the sliding cam package.
  • a spacer element may be present between two needle bearing elements accommodated in a longitudinal groove, wherein the spacer element may in particular be designed as a sheet metal element which at least partially surrounds the fundamental shaft, wherein the spacer element may also comprise a plastic material or another material.
  • the sheet metal element may have a width corresponding to a substantial part of the length of the sliding cam package, and a wide spacer element causes, for example, two needle bearing elements are received in a longitudinal groove only in the outer regions of the sliding cam package.
  • the fundamental wave can be formed from a tubular body.
  • a hollow base shaft has a low weight, and since by the inventively designed means a spline can be omitted, and no nuts must be included in the fundamental wave,
  • the wall of the hollow running basic wave can be made thin. This saves further weight of the camshaft.
  • the outer diameter of the fundamental shaft with the diameter of the passage in the sliding cam package form a fit, so that a substantially play-free sliding fit of the sliding cam package is formed on the fundamental shaft.
  • optimum guidance of a tapping element over the cam profiles of the sliding cam package is achieved by minimizing or avoiding radial bearing play of the sliding cam package on the fundamental shaft, which protects the valve train of the internal combustion engine.
  • no oil can foam in the oil volume of the hydraulic valve clearance compensation elements of the valve train, which serve for the play-free guidance of the pick-off elements on the cam profiles.
  • retaining rings may be provided which are arranged on at least one and preferably on both end sides of the sliding cam package, so that the needle bearing elements are secured axially in the longitudinal grooves by the retaining rings.
  • the needle bearing elements are consequently fixed in the axial direction in the longitudinal groove on the inside by the spacer element and on the outside by the retaining rings.
  • the retaining rings can be introduced into provided circumferential grooves in the end sides of the sliding cam package, for example non-positively, positively, force-positively or cohesively.
  • the retaining rings can be soldered or welded to the side surfaces of the sliding cam package, in particular by electron beam welding, by laser welding or by a Friction welding.
  • the retaining rings can also be arranged by a screw or adhesive connection on the side surfaces of the sliding cam package.
  • the circlips have an inner diameter that is slightly larger than the outer diameter of the fundamental.
  • the inventive design of the camshaft with further advantage results in a simple assembly of the sliding cam packages on the fundamental shaft.
  • the spacer element in the form of a spring plate and the needle bearing elements in the passage of the sliding cam element can be joined, and with the needle roller elements used in the longitudinal grooves in the passage of the sliding cam package this can be pushed onto the basic shaft.
  • the needle bearing elements also engage in the longitudinal grooves in the outside of the fundamental shaft.
  • the retaining rings can be attached to the end sides of the sliding cam package.
  • FIG. 1 shows a perspective view of a camshaft 1 with a basic shaft 10 shown in sections, and on the basic shaft 10 is an example of a sliding cam package 11 is added, which is shown in a half-section and axially slidably seated on the fundamental shaft 10.
  • the sliding cam package 11 can be moved back and forth on the basic shaft 10 in the axial direction, and the sliding cam package 11 has a plurality of mutually different cam profiles 12 which, depending on the adjusted axial position on the basic shaft 10, pass on different lifting information to a picking element.
  • means 14 For transmitting torque between the basic shaft 10 and the sliding cam package 11 are used means 14, and the means 14 comprise according to the invention elongated needle bearing elements 15th
  • longitudinal grooves 16 are introduced in the passage 13 of the sliding cam package 11, through which the fundamental shaft 10 extends.
  • the longitudinal grooves 16 are distributed over the circumference at equal distances from each other and extend with constant cross section in the axial direction in the inner wall of the passage 13.
  • the longitudinal grooves 16 correspond with their number and with their position with longitudinal grooves 17 in the outer side of the fundamental 10 are introduced.
  • the needle bearing elements 15 are seated with a first part of their circular cross section in the longitudinal grooves 16 in the passage 13 of the sliding cam package 11 and with a second part of the same circular cross section sit in the longitudinal grooves 17 in the outside of the fundamental shaft 10, wherein the parts of the circular cross section of the needle bearing elements 15 preferably each half in the longitudinal grooves 16, 17 are seated.
  • a spacer element 18 designed as sheet metal elements.
  • the spacer element 18 encloses the fundamental shaft 10 substantially completely and is seated in a correspondingly rotated centrally arranged recess in the passage 13 of the sliding cam package 11.
  • the needle bearing elements 15, which each sit laterally to the spacer element 18 in the longitudinal grooves 16, 17, are held at a distance from each other.
  • the needle bearing elements 15 are prevented from axially slipping out of the longitudinal grooves 16, 17 by securing rings 19 on the side surfaces of the sliding cam package 11, by which the needle bearing elements 15 are secured axially.
  • the exemplary embodiment shows a hollow basic shaft 10, wherein the camshaft 1 can be mounted via the basic shaft 10 in a receiving body, for example in a hood module or in a cylinder head.
  • FIG. 3 shows a first embodiment for receiving a needle bearing element 15 in the longitudinal grooves 16 and 17, wherein the longitudinal groove 16 is inserted in the passage 13 of the sliding cam package 11 and the longitudinal groove 17 is introduced into the outside of the fundamental shaft 10.
  • the illustration shows the needle bearing element 15, which is half seated in the longitudinal groove 17, wherein the longitudinal groove 17 has a contour with a radius which corresponds approximately to the radius of the cylindrical needle bearing element 15.
  • the longitudinal groove 16 has two radii and through the two radii are defined two areas for the introduction of a contact force F, and in the areas touched the needle bearing element 15, the surface in the longitudinal groove 16.
  • the slight deviation from the radius of the needle bearing element 15 prevents the L jossnutkanten 22 form highly stressed areas, as the Contact force F on the larger areas spaced from the Lssensnutkanten 22 is distributed.
  • FIG. 4 shows in a modification of the embodiment FIG. 3 a longitudinal groove 16 in the passage 13 of the sliding cam package 11 with a trapezoidal shape, while, as in connection with FIG. 3 already described, the longitudinal groove 17 in the outer side of the fundamental shaft 10 has a radius corresponding to the radius of the cylindrical needle bearing element 15.
  • the trapezoidal longitudinal groove 16 has two obliquely arranged, opposite trapezoidal flanks 20, and as a groove bottom extends between the trapezoidal flanks 20 a trapezoidal base side 21st

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

Claims (9)

  1. Arbre à cames (1) pour le mécanisme de distribution d'un moteur à combustion interne, comprenant un arbre de base (10) et comprenant au moins un ensemble de cames coulissantes (11) comportant plusieurs profils de came (12), dans lequel l'arbre de base (10) s'étend à travers un passage (13) dans l'ensemble de cames coulissantes (11), de telle sorte que celui-ci est reçu de manière mobile axialement sur l'arbre de base (10), et dans lequel des moyens (14) servant à former une liaison de transmission de couple entre l'arbre de base (10) et l'ensemble de cames coulissantes (11) sont prévus,
    dans lequel les moyens (14) comportent des éléments de palier à aiguilles (15) de forme allongée qui, par une première partie de leur section transversale circulaire, sont logés dans une rainure longitudinale (16) dans le passage (13) de l'ensemble de cames coulissantes (11) et qui, par une deuxième partie de la même section transversale, sont logés dans une rainure longitudinale (17) dans le côté extérieur de l'arbre de base (10), caractérisé en ce que la rainure longitudinale (16) dans le passage (13) de l'ensemble de cames coulissantes (11) présente un contour en section transversale différent d'un arc de cercle.
  2. Arbre à cames (1) selon la revendication 1, caractérisé en ce que la rainure longitudinale (17) dans le côté extérieur de l'arbre de base (10) présente une section transversale semi-circulaire qui correspond à la section transversale circulaire des éléments de palier à aiguilles (15).
  3. Arbre à cames (1) selon la revendication 1 ou 2, caractérisé en ce que le contour en section transversale de la rainure longitudinale (16) dans le passage (13) de l'ensemble de cames coulissantes (11) est défini par deux rayons qui sont plus grands que le diamètre des éléments de palier à aiguilles (15), de telle sorte que deux régions de contact opposées sont formées pour le contact des éléments de palier à aiguilles (15).
  4. Arbre à cames (1) selon la revendication 1 ou 2, caractérisé en ce que le contour en section transversale de la rainure longitudinale (16) dans le passage (13) de l'ensemble de cames coulissantes (11) présente une forme trapézoïdale, de telle sorte que deux régions de contact opposées sont formées pour le contact des éléments de palier à aiguilles (15).
  5. Arbre à cames (1) selon l'une des revendications précédentes, caractérisé en ce que la rainure longitudinale (17) dans le côté extérieur de l'arbre de base (10) est formée de manière axialement parallèle à l'étendue de l'arbre de base (10) et/ou un élément de palier à aiguilles et de préférence au moins deux éléments de palier aiguilles (15) étant reçus dans une rainure longitudinale (17).
  6. Arbre à cames (1) selon l'une des revendications précédentes, caractérisé en ce qu'un élément d'écartement (18) est présent entre deux éléments de palier à aiguilles (15) reçus dans une rainure longitudinale (17), l'élément d'écartement (18) étant réalisé en particulier sous forme d'élément en tôle entourant au moins partiellement l'arbre de base (10).
  7. Arbre à cames (1) selon l'une des revendications précédentes, caractérisé en ce que l'arbre de base (10) est formé à partir d'un corps tubulaire.
  8. Arbre à cames (1) selon l'une des revendications précédentes, caractérisé en ce que le diamètre extérieur de l'arbre de base (10) et le diamètre du passage (13) dans l'ensemble de cames coulissantes (11) forment l'un par rapport à l'autre une cote d'ajustement, de telle sorte qu'un ajustement glissant sensiblement sans jeu de l'ensemble de cames coulissantes (11) sur l'arbre de base (10) est formé.
  9. Arbre à cames (1) selon l'une des revendications précédentes, caractérisé en ce que des anneaux de fixation (19) sont prévus, lesquels sont disposés au niveau d'au moins l'un des côtés d'extrémité et de préférence au niveau des deux côtés d'extrémité de l'ensemble de cames coulissantes (11), de telle sorte que les éléments de paliers à aiguilles (15) sont fixés axialement.
EP15734411.0A 2014-08-11 2015-07-08 Arbre à cames avec bloc de cames coulissantes Active EP3180498B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014111383.7A DE102014111383A1 (de) 2014-08-11 2014-08-11 Nockenwelle mit Schiebenockenpaket
PCT/EP2015/065558 WO2016023687A1 (fr) 2014-08-11 2015-07-08 Arbre à cames avec bloc de cames coulissantes

Publications (2)

Publication Number Publication Date
EP3180498A1 EP3180498A1 (fr) 2017-06-21
EP3180498B1 true EP3180498B1 (fr) 2019-10-16

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EP (1) EP3180498B1 (fr)
DE (1) DE102014111383A1 (fr)
WO (1) WO2016023687A1 (fr)

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DE102018207438A1 (de) * 2018-05-14 2019-11-14 Thyssenkrupp Ag Nockenwelle, sowie Verfahren zur Herstellung einer Nockenwelle
CN108487962B (zh) * 2018-06-01 2024-03-22 浙江正奥汽配有限公司 一种发动机的气门控制装置
CN110848365B (zh) * 2018-08-21 2022-03-11 上海汽车集团股份有限公司 一种滑移凸轮机构
DE102018133403A1 (de) * 2018-12-21 2020-06-25 Thyssenkrupp Ag Nockenwelle, Verbrennungsmotor und Verfahren zur Herstellung einer Nockenwelle
DE102019105457A1 (de) 2019-03-04 2020-09-10 Thyssenkrupp Ag Nockenwelle, Kraftfahrzeug und Verfahren zum Montieren einer Nockenwelle
DE102019105462A1 (de) * 2019-03-04 2020-09-10 Thyssenkrupp Ag Nockenwelle, Kraftfahrzeug und Verfahren zum Montieren einer Nockenwelle
DE102019206044A1 (de) 2019-04-26 2020-10-29 Thyssenkrupp Ag Nockenwelle

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WO2015176874A1 (fr) * 2014-05-20 2015-11-26 Thyssenkrupp Presta Teccenter Ag Arbre à cames

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JP2008208731A (ja) * 2007-02-23 2008-09-11 Honda Motor Co Ltd 可変バルブタイミング機構
DE102008005639B4 (de) 2008-01-23 2021-10-21 Daimler Ag Ventiltriebvorrichtung
DE102010004579A1 (de) * 2010-01-14 2011-07-21 Audi Ag, 85057 Ventiltrieb einer Brennkraftmaschine
DE102011000510B4 (de) 2011-02-04 2019-03-28 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Schiebenockensystem mit Linearlager
DE102011000511A1 (de) 2011-02-04 2012-08-09 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Schiebenockensystem mit Rasteinrichtung

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Publication number Priority date Publication date Assignee Title
WO2015176874A1 (fr) * 2014-05-20 2015-11-26 Thyssenkrupp Presta Teccenter Ag Arbre à cames
EP3146166A1 (fr) * 2014-05-20 2017-03-29 ThyssenKrupp Presta TecCenter AG Arbre à cames

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WO2016023687A1 (fr) 2016-02-18
EP3180498A1 (fr) 2017-06-21

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