WO2006103004A1 - Dispositif de reglage d'arbre a cames - Google Patents

Dispositif de reglage d'arbre a cames Download PDF

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Publication number
WO2006103004A1
WO2006103004A1 PCT/EP2006/002518 EP2006002518W WO2006103004A1 WO 2006103004 A1 WO2006103004 A1 WO 2006103004A1 EP 2006002518 W EP2006002518 W EP 2006002518W WO 2006103004 A1 WO2006103004 A1 WO 2006103004A1
Authority
WO
WIPO (PCT)
Prior art keywords
camshaft adjuster
vibration damper
camshaft
mass
intermediate body
Prior art date
Application number
PCT/EP2006/002518
Other languages
German (de)
English (en)
Inventor
Dirk Heintzen
Rainer Ottersbach
Ahmet Deneri
Original Assignee
Schaeffler Kg
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 Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2006103004A1 publication Critical patent/WO2006103004A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/121—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon using springs as elastic members, e.g. metallic springs
    • F16F15/124—Elastomeric springs
    • F16F15/126—Elastomeric springs consisting of at least one annular element surrounding the axis of rotation
    • 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
    • F01L1/022—Chain drive
    • 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
    • F01L1/024—Belt drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34403—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft
    • F01L1/34406—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using helically teethed sleeve or gear moving axially between crankshaft and camshaft the helically teethed sleeve being located in the camshaft driving pulley
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—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 making the angular relationship oscillate, e.g. non-homokinetic drive
    • 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
    • F01L2301/00—Using particular materials
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/033—Hydraulic engines

Definitions

  • the invention relates to a camshaft adjuster for an internal combustion engine, in which the relative angular relationship between a drive element and an output element is variable via a control unit, in particular according to the preamble of claim 1.
  • An uneven transmission of the drive movement between the crankshaft and a drive element of the camshaft adjuster in particular irregularities as a result of tooth engagement of a traction device in a drive wheel of the crankshaft and a drive wheel of the camshaft adjuster.
  • a toothed chain or a toothed belt is used as traction means with non-uniform tooth engagement and / or different spring and damping properties of
  • Traction means depending on the number of dental interventions. Vibration excitations by the operation of the camshaft adjuster, for example, as a result of the application of the steep movement, play or lots o. ⁇ ..
  • speed-adaptive vibration absorbers which are preferably used in the area of a flywheel or the crankshaft and which have a speed-dependent and / or amplitude-dependent natural cycle frequency, whereby the eradication effect on the application and the operating conditions and over an increased frequency range improved can be.
  • speed-adaptive vibration absorber For example only reference is made to document DE 198 31 159 B4; Further publications are searchable under the search term "speed-adaptive vibration absorber".
  • an electrically driven camshaft adjuster in which a three-shaft gear is formed with the drive element, the output element and a motor shaft of the electric actuator.
  • the motor shaft has a coupling which has an elastic polymer ring, which causes a vibration damped introduction of the drive torque of the actuator.
  • a vibration damper for a camshaft or crankshaft which has a torsion spring rod and a TiI- germasse, with torsion spring rod and absorber mass are arranged within the cam or crankshaft.
  • the invention has for its object to provide a camshaft adjuster, which has improved dynamic properties in compliance with the building conditions.
  • the camshaft adjuster has a vibration damper.
  • a vibration absorber is understood in particular to mean a degree of freedom system, a multi-degree-of-freedom system or an oscillatory continuum which is not arranged in series in the force flow of the camshaft adjuster between the drive element and the output element, but rather parallel to it.
  • the vibration absorber according to the invention may be a vibration absorber of any design which has, for example, one or more constant frequencies or is speed-adaptive or amplitude-adaptive.
  • the vibration absorber In addition to an adaptation of the vibration absorber on the speed and / or amplitude of a vibration movement and an "active" adjustment of the mechanical properties of the vibration is possible. This can be done in particular via a suitable adjusting unit or via the adjusting movement of the camshaft adjuster, so that the mechanical properties of the vibration absorber are dependent on the setting angle. In the event that a hydraulic control unit is used, the adjustment of the mechanical properties of the vibration damper can also take place via the existing hydraulic control pressure.
  • the vibration absorber preferably has a discrete mass, for example a metallic component, which is connected via an elastic and / or damping element to the component of the camshaft adjuster.
  • a discrete mass for example a metallic component, which is connected via an elastic and / or damping element to the component of the camshaft adjuster.
  • Such an element may be formed with rubber, plastic, rubber or an elastomeric body.
  • the vibration damper is supported against an associated component of the camshaft adjuster, which lies directly or indirectly in the aforementioned power flow.
  • an associated component of the camshaft adjuster which lies directly or indirectly in the aforementioned power flow.
  • reaction forces resulting from the vibration damper can be fed into the camshaft adjuster via the component, such that an improved vibration response, at least in a partial region of the frequency band, from the superimposition of the forces resulting from the vibration absorber and the remaining movements and forces of the camshaft adjuster. give an improved frequency spectrum and smoother running of the camshaft adjuster.
  • a tuning of the vibration damper is done by design specification, when commissioning the camshaft adjustment or by adaptation during operation.
  • An adaptation can be made as a function of the application of the camshaft adjusting, in accordance with the expected speeds of the camshaft Verstellelier and in dependence of the components of the internal combustion engine involved, for example, depending on the expected Dreun- unguniformities of the spherical wave, of polygon effects of a sprocket, rotational irregularities caused by the traction means are caused by the Nockenwellentriebs, rotational nonuniformities due to the camshaft adjustment itself or vibration excitations, which have their cause in the rotational movement of the camshaft and / or the adjusting movement of the valves.
  • the embodiment of the invention can allow in a particularly simple manner that camshaft adjuster optionally be equipped with a vibration absorber, since the power flow of the camshaft adjusting per se is not affected by the vibration damper, since the vibration damper is not turned on in the power flow, but is connected in parallel thereto.
  • camshaft adjuster optionally be equipped with a vibration absorber, since the power flow of the camshaft adjusting per se is not affected by the vibration damper, since the vibration damper is not turned on in the power flow, but is connected in parallel thereto.
  • a camshaft adjuster (in addition or subsequently) to be equipped with a vibration absorber, so this vibration absorber can be separately, u. U. by a supplier, are manufactured and then connected to the camshaft adjuster on the component.
  • Another advantage is the location of the arrangement of the vibration damper, since this is the camshaft upstream and thus keeps the introduction of any vibrations of the drive member of the camshaft.
  • Another advantage may be the use of a vibration damper in the region of the camshaft adjuster instead of in the region of the crankshaft, since the camshaft and thus the camshaft adjuster rotates at half the speed of the crankshaft.
  • the vibration absorber can be connected in a variety of ways to the associated component of the camshaft adjuster, for example via a fastening means such as a screw or positively. According to another proposal of the invention, however, the vibration absorber is firmly bonded to the camshaft adjuster. This embodiment can lead to the following advantages:
  • the cohesive connection can be provided in a particularly cost-effective manner, for example by means of an adhesive or by an elastic element of the vibration damper is vulcanized directly on the associated component of the camshaft adjuster.
  • a cohesive connection also allows relative to a screw changed degrees of freedom of the elastic element: for example, the elastic element connected by oriented in the axial direction of the camshaft adjuster screws with the associated component, the screw is a fixed point of the elastic member, from which elastic deformations can be brought about only by intermediate material regions of the elastic element in the circumferential direction or upstream regions in the axial direction.
  • fasteners require suitable mating surfaces on the associated component of the camshaft adjuster, such as holes for a screw connection, which mean increased manufacturing costs for the associated component of the camshaft adjuster.
  • a cohesive connection with an arbitrarily designed assigned component of the camshaft adjuster can take place.
  • a fastener such as a screw connection also requires a passage or connection of the fastener with the elastic member, which u. U. may mean a weakening of the elastic element. Such a weakening does not occur for a cohesive connection of the vibration absorber.
  • the configuration according to the invention can lead to better maintenance of required round runs, because in the tolerance chain an adapted screwed part such as mass and intermediate body with associated shape and position tolerances is not present.
  • the vibration damper is a rotation damper.
  • a rotation damper can be coupled in a particularly simple manner with the rotary drive movement and any undesired dynamic states of motion of the camshaft adjuster.
  • a Rotationstilger u. U. a reduced installation space, since this changes its configuration only slightly or not at all in the course of its repayment movement.
  • a particularly simple embodiment of a vibration damper as Rotationsstilger results when the mass and the intermediate body are formed approximately hollow cylinder linderförmig.
  • the mass is firmly bonded to an outer surface of the intermediate layer.
  • the intermediate layer is bonded to the component of the camshaft adjuster in the region of an opposing outer surface.
  • this may for example be such that the intermediate body is connected via its end faces on the one hand to the mass and on the other hand to the associated component of the camshaft adjuster, so that the aforementioned components are arranged axially adjacent to each other.
  • the aforementioned components are nested radially into one another, wherein the intermediate body in the region of a radially outer circumferential surface and in the region of a radially inner circumferential surface is connected to the mass or the camshaft adjuster associated component.
  • the production and / or assembly possibilities for the camshaft adjuster according to the invention can be improved by reducing the vibration supply damper is firmly bonded to a cover of the camshaft adjuster.
  • the vibration absorber is materially connected to a drive wheel of the camshaft adjuster
  • U large diameter of the drive wheel in the region of the junction to be exploited, so that caused by the vibration damper forces in the connection area have a large lever arm. This can u.
  • U. the vibration damper can be designed with reduced dimensions and / or the eradication effect can be strengthened.
  • a particularly suitable connection point for the vibration damper is, for example, given by an axial extension of the drive wheel, a surface inside of the toothing of the drive wheel or an outer Mantelflä- surface of a housing of the camshaft adjuster.
  • FIG. 2 shows the camshaft adjuster according to FIG. 1 in a front view
  • FIG. 3 shows a second exemplary embodiment of the camshaft adjuster according to the invention in a longitudinal section IV-IV;
  • FIG. 4 shows the camshaft adjuster according to FIG. 3 in a front view
  • FIG. 5 shows a third exemplary embodiment of a camshaft adjuster according to the invention in a longitudinal section Vl-Vl;
  • FIG. 6 shows the camshaft adjuster according to FIG. 5 in a front view
  • FIG. 7 shows a fourth exemplary embodiment of a camshaft adjuster according to the invention in a longitudinal section VIII-VIII and FIG
  • Figure 8 shows the camshaft adjuster according to Figure 7 in front view.
  • the invention relates to a camshaft adjuster of any type, for example in paraxialkolbenbauart or with a three-shaft, an eccentric or a swash plate gear, the adjusting movement is preferably brought about on the basis of a hydraulic actuator or an electric control unit.
  • Figure 1 shows a camshaft adjuster 1 with a drive wheel 2, which is connected via a traction means in drive connection with a crankshaft.
  • the camshaft adjuster 1 has a Tilger 3, which is connected to an associated component 4, which is part of the power flow between the drive wheel 2 and a camshaft.
  • the associated component 4 is formed as a drive wheel 2, while it is in the embodiment of Figure 5 in the component 4 is a lid 18.
  • the component 4 can be any component of the camshaft adjuster 1, provided that it is coupled to the power flow from the drive element to the output element.
  • the vibration damper (3) can also be integrated in a housing of the camshaft adjuster and / or the component (4) can be an element of a geared connection used in the camshaft adjuster.
  • the vibration damper 3 has a mass 5 and an elastic intermediate body 6, which is interposed between mass 5 and component 4, on. While the. Mass 5 is stiff, the elastic intermediate body 6 has elastic and / or damping properties.
  • the mass 5 is designed as a hollow-cylinder-shaped or annular metallic ring 7, which is arranged concentrically to a longitudinal axis 8-8 of the camshaft adjuster 1.
  • the elastic intermediate body 6 is formed as a hollow cylindrical or annular ring 9 with a radial extent corresponding to the extension of the ring 7.
  • the extent of the ring 9 in the direction of the longitudinal axis 8-8 is preferably smaller than that of the ring 7 and is half to one quarter of the extent of the ring 7 in the direction of the longitudinal axis 8-8.
  • this is cohesively and over a large area attached to the ring 7.
  • the ring 9 is firmly bonded to the component 4 over a large area.
  • the drive wheel 2 has a substantially hollow cylindrical drive wheel body 10, which forms the drive toothing 11 radially outboard.
  • a housing 12 Radially inwardly of the drive wheel 10, a housing 12 is formed, which emerges from the drive wheel 10 to the left in the axial direction according to FIG.
  • the housing 12 and the drive wheel body 10 are connected to one another via a radial, annular web 14 which surrounds the longitudinal axis 8-8.
  • An inner circumferential surface 15 of the drive wheel body 10, an associated end face of the web 14 and the lateral surface 13 form a recess 16 in the circumferential direction about the longitudinal axis 8-8, which is U-shaped in the longitudinal half section from the drive wheel 2.
  • the vibration damper 3 is inserted into the recess 16 in such a way that it terminates approximately flush with the drive wheel body 10 in the axial direction, wherein the elastic intermediate body 6 is firmly bonded to the web 14.
  • the elastic intermediate body 6 and the mass 5 have a radial clearance both with respect to the lateral surface 13 and with respect to the lateral surface 15.
  • the mass 5 can rotate relative to the drive wheel 2 about the longitudinal axis 8-8, the elastic intermediate body 6 being subjected to shear in this case.
  • the mass is also used in the recess 16a, but the elastic intermediate body 6a radially inwardly bonded to the lateral surface 13a of the housing 12a cohesively, while the mass 5a cohesively on a cylindrical outer surface of the elastic intermediate body 6a is connected.
  • mass 5a and elastic intermediate body 6a form a radial gap to the lateral surface 15a and an axial gap to the web 14a.
  • Mass 5a and elastic intermediate body 6a are slightly out of the drive wheel 2a in the axial direction to the left.
  • drive wheel 2b and housing 12b are fixedly connected via a fastening means, here a screw 17, with a lid 18 which at least partially closes the housing 12b to the outside.
  • the elastic intermediate body 6b formed as an annular body with a relatively large radial extent.
  • the elastic intermediate body 6b is materially connected to the axially outer end face of the lid 18 and carries cohesively on the cover 18 opposite end face the mass 5b, which is also formed with respect to the previous embodiments, increased radial extent.
  • Mass 5b and elastic intermediate body 6b have a central bore, in which a further cover 19 extends and through which this can be mounted, wherein the cover 19 can close a remaining opening or bore of the lid 18.
  • the lid 18 may also be omitted, so that the elastic intermediate body 6b and the mass 5b replace the functions of the lid 18, if the elastic intermediate body 6b is tightly connected to the housing 12b.
  • the dekelkel 19 can be used for example in the mass 5b, whereby both covers 18, 19 co-determine the mass moment of inertia of the mass 5b.
  • the component 4c of the camshaft adjuster 1c which is connected to the vibration absorber 3c, is formed by the drive wheel 2c, wherein the drive wheel has an axial, hollow-cylindrical extension 20 in the region of the drive wheel body 10c starting from the drive wheel body 10c projects beyond the housing 12c, lid 18c and lid 19c.
  • the cylindrical lateral surface 21 of the extension 20 is cohesively connected to a corresponding cylindrical inner surface of the elastic intermediate body 6c.
  • Radially outwardly a cylindrical lateral surface of the elastic intermediate body 6c is cohesively connected to the mass 5c.
  • the vibration absorber 3c in this case is located approximately at the radial distance of the teeth of the drive wheel 2c from the longitudinal axis 8c-8c.
  • the elastic intermediate body 6 is formed for example as a rubber ring. A substance-coherent compound can be made in particular by vulcanization or an extrusion process.
  • the mass 5 may be one made of steel or metal or lead.
  • the elastic intermediate body 6 is preferably made of rubber, plastic, rubber or an elastomeric material. Preferably, materials 5 with a higher specific weight than the intermediate body 6 are used for the mass.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

Dispositif de réglage d'arbre à cames pour un moteur à combustion interne, à l'aide duquel la relation angulaire relative entre une roues d'entrée (2) et un élément de sortie se trouvant en relation de sortie avec un arbre à cames peut être modifiée par l'intermédiaire d'un bloc de réglage. Selon la présente invention, le dispositif de réglage (1) d'arbre à cames, en particulier la roue d'entrée (2), possède un amortisseur d'oscillations (3). Ledit amortisseur d'oscillations (3) permet la réduction des oscillations, forces et couples indésirables se produisant lors du fonctionnement du dispositif de réglage de l'arbre à cames. Selon un mode de réalisation particulier de la présente invention, ledit amortisseur d'oscillations (3) est relié par liaison de matière à la partie structurale associée du dispositif de réglage (1) de l'arbre à cames.
PCT/EP2006/002518 2005-04-01 2006-03-20 Dispositif de reglage d'arbre a cames WO2006103004A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005014883.2 2005-04-01
DE102005014883A DE102005014883A1 (de) 2005-04-01 2005-04-01 Nockenwellenversteller

Publications (1)

Publication Number Publication Date
WO2006103004A1 true WO2006103004A1 (fr) 2006-10-05

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/002518 WO2006103004A1 (fr) 2005-04-01 2006-03-20 Dispositif de reglage d'arbre a cames

Country Status (2)

Country Link
DE (1) DE102005014883A1 (fr)
WO (1) WO2006103004A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10352205B2 (en) * 2017-06-26 2019-07-16 Schaeffler Technologies AG & Co. KG Variable cam phaser with damper

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008032029A1 (de) 2008-07-07 2010-01-14 Schaeffler Kg Nockenwellenversteller
JP5414795B2 (ja) * 2008-08-15 2014-02-12 ボーグワーナー インコーポレーテッド ダンパと補償器とを備えたスプロケット

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992018754A1 (fr) * 1991-04-10 1992-10-29 Ab Volvo Agencement relatif aux moteurs a combustion interne
DE19724878A1 (de) * 1997-06-12 1998-12-24 Pahl Gummi Asbest Drehschwingungstilger
JPH11287295A (ja) * 1998-04-03 1999-10-19 Nok Megulastik Co Ltd ダンパ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1992018754A1 (fr) * 1991-04-10 1992-10-29 Ab Volvo Agencement relatif aux moteurs a combustion interne
DE19724878A1 (de) * 1997-06-12 1998-12-24 Pahl Gummi Asbest Drehschwingungstilger
JPH11287295A (ja) * 1998-04-03 1999-10-19 Nok Megulastik Co Ltd ダンパ

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 01 31 January 2000 (2000-01-31) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10352205B2 (en) * 2017-06-26 2019-07-16 Schaeffler Technologies AG & Co. KG Variable cam phaser with damper

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DE102005014883A1 (de) 2007-05-10

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