US20130180484A1 - Camshaft adjuster for an internal combustion engine - Google Patents

Camshaft adjuster for an internal combustion engine Download PDF

Info

Publication number
US20130180484A1
US20130180484A1 US13/823,783 US201113823783A US2013180484A1 US 20130180484 A1 US20130180484 A1 US 20130180484A1 US 201113823783 A US201113823783 A US 201113823783A US 2013180484 A1 US2013180484 A1 US 2013180484A1
Authority
US
United States
Prior art keywords
adapter
driven pinion
pinion
camshaft
camshaft adjuster
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.)
Abandoned
Application number
US13/823,783
Other languages
English (en)
Inventor
Armin Braun
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co 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 Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BRAUN, ARMIN
Publication of US20130180484A1 publication Critical patent/US20130180484A1/en
Assigned to SCHAEFFLER TECHNOLOGIES GMBH & CO. KG reassignment SCHAEFFLER TECHNOLOGIES GMBH & CO. KG MERGER AND CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: Schaeffler Technologies AG & Co. KG, SCHAEFFLER VERWALTUNGS 5 GMBH
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG
Assigned to Schaeffler Technologies AG & Co. KG reassignment Schaeffler Technologies AG & Co. KG CORRECTIVE ASSIGNMENT TO CORRECT THE PROPERTY NUMBERS PREVIOUSLY RECORDED ON REEL 037732 FRAME 0347. ASSIGNOR(S) HEREBY CONFIRMS THE APP. NO. 14/553248 SHOULD BE APP. NO. 14/553258. Assignors: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—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
    • F01L1/34—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
    • F01L1/352—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 bevel or epicyclic 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
    • F01L1/34—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F1/00—Cylinders; Cylinder heads 
    • F02F1/24—Cylinder heads
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/04—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members
    • F16H1/06—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes
    • F16H1/10—Toothed gearings for conveying rotary motion without gears having orbital motion involving only two intermeshing members with parallel axes one of the members being internally toothed
    • 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
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/36—Toothed gearings for conveying rotary motion with gears having orbital motion with two central gears coupled by intermeshing orbital gears
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • 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
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating

Definitions

  • the invention concerns a camshaft adjuster for an internal combustion engine, comprising a drive pinion that can be connected rotationally fast to a crankshaft, a driven pinion comprising an inner gearing and arranged for rotation relative to said drive pinion about an axis of rotation as well as an adapter that is arranged on an inner circumference of the said driven pinion and through which the driven pinion can be connected rotationally fast to a camshaft.
  • a camshaft adjuster serves for a controlled adjustment of the phase position between a camshaft and a crankshaft in an internal combustion engine and thus enables an optimized setting of valve opening and closing times through the engine load and the speed of rotation of the engine. This enables a clear reduction of fuel consumption and exhaust gas emission as well as an enhancement of the engine performance.
  • electro-mechanical camshaft adjusters have also been used as an alternative to hydraulic camshaft adjusters.
  • an electric adjusting motor in driving connection with an adjusting shaft generally serves as a so-called adjusting member.
  • the transmissions used are generally triple shaft transmissions.
  • Driving power originates from a drive pinion mounted on the crankshaft and through a driving shaft, while power take-off is performed through a driven shaft and a driven pinion connected rotationally fast to a camshaft.
  • the adjusting power is transferred by an electric adjusting engine via an adjusting shaft into the triple shaft transmission and effects a rotation of the driven pinion relative to the drive pinion. Through the relative rotation of the two pinions relative to each other, it is possible to adjust the phase position between the crankshaft and the camshaft.
  • the camshaft adjusting device comprises a drive pinion and a driven pinion that are arranged for rotation relative to each other.
  • the drive pinion is configured as an annulus into which the driven pinion is inserted.
  • the driven pinion is configured on its inner circumference with an internal gearing and with an annular reception section adjoining the inner gearing.
  • the reception section serves to receive and position an adapter through which the driven pinion is connected rotationally fast to a camshaft. This adapter is inserted for this purpose into the driven pinion and welded rotationally fixed within the reception section.
  • camshaft adjuster for an internal combustion engine, which camshaft adjuster comprises a drive pinion that can be connected rotationally fast to a crankshaft, a driven pinion comprising an inner gearing and arranged for rotation relative to said drive pinion about an axis of rotation as well as an adapter that is arranged on the inner circumference of said driven pinion and through which the driven pinion can be connected rotationally fast to a camshaft.
  • the adapter is fixed via the inner gearing on the inner circumference of the driven pinion.
  • the invention takes into account that, to assure a disturbance-free operation of a camshaft adjuster, a reliable torque transmission between the driving element and the driven element must be guaranteed.
  • a drive pinion is mounted on a driven pinion which, in its turn, is connected through an adapter to a camshaft.
  • the adapter itself is arranged typically inside the driven pinion on the inner circumference of the driven pinion. For this purpose, it has been hitherto necessary to provide a separate reception section on the inner circumference. This is not desirable with a view to the complexity of manufacture and the incurred costs.
  • the invention recognizes the fact that, surprisingly, these problems can be overcome by fixing the adapter via the inner gearing of the driven pinion on the inner circumference of the driven pinion. In this way, the hitherto required additional working of the inner circumference of the driven pinion for fixing the adapter can be omitted.
  • the adapter can be arranged on the driven pinion without the need of providing a special reception section for this on the inner circumference of the driven pinion.
  • the drive pinion is configured particularly as an annulus and comprises an inner gearing which is configured partially or continuously on its inner circumference.
  • the driving power for the drive pinion originates from the rotationally fast connection to a crankshaft.
  • the drive pinion can be configured, for instance, as a chain pulley and the rotationally fast connection to the crankshaft can be realized through a chain.
  • the driven pinion may also be configured as a belt pulley and thus be driven through a belt drive.
  • the driven pinion is usually arranged on the inner circumference of the drive pinion, in which case, the drive pinion can be mounted on the driven pinion.
  • the driven pinion is preferably likewise configured as an annulus and comprises an inner gearing.
  • This inner gearing is made in the inner circumference during the manufacturing of the driven pinion with help of a so-called broaching method.
  • a broaching needle with an appropriate contour is drawn or pressed through an already made bore in the driven pinion.
  • the cross-section of the broaching needle corresponds to the contour of the inner gearing to be configured on the inner circumference of the driven pinion by the broaching step.
  • the inner gearing, together with the inner gearing of a driven pinion can form an adjusting gear which can be operated, for instance, through a spur gear of a shaft transmission.
  • only a part of the inner gearing of the driven pinion is available because, in the installed state, the adapter is arranged on the inner circumference of the driven pinion.
  • the adapter is appropriately configured with an outer diameter that is accordingly matched to the inner diameter of the driven pinion.
  • the adapter is configured, for example, with a circular cross-section.
  • the adapter can be pushed into the driven pinion and fixed therein, so that it comes to bear with its outer circumference against the inner circumference of the driven pinion or against the inner gearing thereof.
  • it is also imaginable to configure the adapter with a counter gearing that meshes with the inner gearing of the driven pinion and thus positions the adapter.
  • the adapter can be configured, for instance, as a substantially flat end cap.
  • the adapter is preferably configured with a central bore through which a central screw for fixing the individual components of a camshaft adjuster to one another can be inserted.
  • the adapter can be screwed on the front end of the camshaft through the fixture of the central screw in the bore.
  • the adapter may comprise further recesses into which fixing elements configured on a front end of the camshaft can engage.
  • the adapter is pressed on to the addendum circle of the inner gearing of the driven pinion.
  • the diameter of the addendum circle defines the outer diameter of the tooth circle, that is, the diameter that is defined by the tips of the teeth.
  • connection realized through pressing-in can basically have either a fixed or a movable configuration.
  • the operating forces occurring during the operation of the camshaft adjusting device can be transmitted via the effective surfaces of the connection, that is, the contact points between the tooth tips and the outer circumference of the adapter.
  • empty spaces remain between the teeth and the outer circumference of the adapter. These empty teeth spaces can be utilized for lubrication of the gearing.
  • the inner gearing is configured axially continuous on the driven pinion.
  • the continuous geometry of the inner gearing enables a simple manufacturing or working-in of the inner gearing on the inner circumference of the driven pinion. Because a separate reception or press-in section for the adapter is not required, an enlarged broaching length for making the inner gearing is obtained on the inner circumference. This guarantees a reliable guidance of the broaching needle used.
  • the adapter can be made with a smaller outer diameter that corresponds approximately to the addendum circle diameter of the driven pinion, so that the adapter is smaller than hitherto used adapters.
  • the bearing area ratio of the inner gearing is enhanced so that, for example, its operating life is longer. Because the inner gearing is configured on the entire inner circumference of the driven pinion, the run-out of the gearwheel is situated in the installed state behind the adapter, on an axial end.
  • the adapter is preferably welded to the driven pinion so that a reliable connection between these two components results.
  • the adapter and the driven pinion are welded segment-wise, particularly at the contact points between the tooth tips and the outer circumference of the adapter, so that the tooth empty spaces are available for the lubricant even after welding.
  • Particularly suited in the present case is laser welding which, due to a high welding speed, narrower weld seam shape and small thermal deformation, assures the precision required in making the connection between said components.
  • the adapter is configured as an end cap. Due to the configuration as an end cap, in addition to transmitting torque between a camshaft and a crankshaft in the installed state, the adapter can also close the adjusting gear on the side facing the camshaft in axial direction.
  • the camshaft adjuster is thus protected, for example, from outer influences such as pollutions or also against leakage.
  • the drive pinion is configured as an annulus and mounted on the driven pinion.
  • Particularly suitable for this purpose is a slide mounting with which the two components moving relative to each other are directly in contact with each other. These components slide on each other against the resistance arising from the sliding friction.
  • the resistance can be reduced, for instance, by the choice of a low-friction material pairing or by lubrication.
  • a slide mounting is obviously particularly suitable because this does not require any additional design space.
  • the invention also provides a stop component for the camshaft and this component is counter mounted an axial direction on the drive pinion.
  • This stop component is preferably configured as a stop ring comprising a stop surface for a camshaft.
  • the stop surface can be configured, for instance, with a projection with which a recess in the front end face of the camshaft can engage.
  • the stop component and the drive pinion are welded to each other preferably, at least partially, that is particularly in the region of the counter mounting.
  • the stop component is connected rotationally fast to the drive pinion.
  • even other fixing methods such as staking or screwing are imaginable.
  • FIG. 1 shows a driven pinion in a three-dimensional illustration
  • FIG. 2 shows the driven pinion of FIG. 1 in a longitudinal section
  • FIG. 3 shows the driven pinion of FIG. 1 comprising an adapter, in a longitudinal section,
  • FIG. 4 shows a top view of the driven pinion comprising the adapter of FIG. 3 ,
  • FIG. 5 shows a detail of the driven pinion comprising the adapter of FIG. 3 .
  • FIG. 6 shows a camshaft adjuster comprising a drive pinion as well as the driven pinion and the adapter of FIGS. 3 to 5 , in a longitudinal section.
  • FIG. 1 shows a driven pinion 1 in a three-dimensional illustration.
  • the driven pinion 1 is configured with a ring-shape in form of an annulus and comprises, on its inner circumference 3 , an inner gearing 5 .
  • an adapter can be fixed on the driven pinion 1 in the assembled state. A detailed description of this is to be found in connection with FIGS. 3 to 6 .
  • the inner gearing 5 is configured both axially continuously on the inner circumference 3 of the driven pinion 1 and also continuously on the entire inner circumference 3 . This results in a continuous geometry that enables the inner gearing 5 to be worked in a simple manner by a broaching method into the inner circumference 3 of the driven pinion 1 . Because a separate reception section for an adapter is not required, the manufacturing of the inner gearing 5 is facilitated. An enlarged broaching length is produced on the inner circumference 3 and enables a reliable guidance of the broaching needle used in the broaching step.
  • a broaching needle with an appropriate contour in drawn through a bore in the driven pinion 1 .
  • the broaching needle has a cross-section corresponding to the contour of the inner gearing 5 of the driven pinion 1 that is configured on the inner circumference 3 after broaching.
  • the inner gearing 5 resulting from broaching comprises a number of teeth 7 adjoining one another along the circumference.
  • the diameter of the addendum circle 11 of the inner gearing 5 is defined by the tips 9 of the teeth 7 extending inwards in radial direction from the driven pinion 1 .
  • the teeth 7 extend from the inner circumference 3 , all, equally far radially inwards within the driven pinion 1 .
  • FIG. 2 shows the driven pinion of FIG. 1 in a longitudinal section.
  • the axially continuous inner gearing 5 that is, the inner gearing 5 extending over the entire axial width 12 of the driven pinion 1 can be clearly seen.
  • This configuration is possible because no separate reception section for arranging and fixing an adapter is required.
  • the outer diameter in the region in which an adapter is intended to be fixed corresponds to the diameter of the addendum circle 11 of the inner gearing 5 .
  • a broaching needle used for making the inner gearing 5 is therefore reliably guided over the entire axial width 12 of the driven pinion 1 .
  • FIG. 3 shows the driven pinion 1 with an adapter 13 in a longitudinal section.
  • the adapter 13 is configured as a flat, circular end cap and fixed via the inner gearing 5 on the inner circumference 3 of the driven pinion 1 .
  • the outer diameter 14 of the adapter 13 is approximately as large as the diameter of addendum circle 11 of the driven pinion 1 .
  • the adapter 13 After broaching of the driven pinion 1 , the adapter 13 is pressed in on the addendum circle 11 of the inner gearing 5 .
  • the press-in section 15 that is, the section on which the adapter 13 is positioned on the inner circumference 3 of the driven pinion, is made available by the already existing inner gearing 5 , so that the diameter of the press-in section 15 for the adapter 13 is equal to the diameter of the addendum circle 11 of the inner gearing 5 .
  • the driven pinion 1 and the adapter 13 are welded to each other. Through this welding, these two components are connected rotationally fast to each other. Welding is performed at those points at which the radially inwards extending tips 9 of the teeth 7 contact the outer circumference 14 of the adapter 13 . After welding, tooth empty spaces 17 remain between the teeth 7 and the outer circumference of the adapter 13 and can be utilized for lubrication of the inner gearing 5 with hydraulic fluid.
  • FIG. 4 shows a top view of the driven pinion 1 comprising the adapter 13 of FIG. 3 , in which the tooth empty spaces 17 between the teeth 7 and the outer circumference of the adapter 13 can be clearly seen. Due to the omission of a separate press-in section, the adapter 13 itself can be made with an outer diameter that corresponds approximately to the diameter of the addendum circle 11 of the driven pinion 1 . In this way, material can be saved in the fabrication of the adapter 13 .
  • a central bore 19 is provided at the center of the adapter 13 , and, for assembly, a central screw can be inserted through this central bore 13 .
  • the central screw can then be fixed in a thread on the front end of a camshaft. In this way, the adapter 13 can be screwed rotationally fast to a camshaft.
  • the adapter 13 is configured with two through-bores 21 , 23 that, in the assembled state, serve for a lubricant supply to the camshaft adjuster or adjusting gear.
  • FIG. 5 is a view of a detail of the adapter 13 of FIG. 3 welded to the driven member 1 .
  • the bearing area ratio of the inner gearing 5 is particularly high. Because the inner gearing 5 is configured on the entire inner circumference 3 of the driven pinion 1 , the run-out end 25 of the gearwheel is situated in the installed state on an axial end behind the adapter 13 that is pressed in on the addendum circle 11 .
  • FIG. 6 shows a camshaft adjusting device 31 for an internal combustion engine, which device comprises a driven pinion 1 and the adapter 13 of FIGS. 3 to 5 in a longitudinal section.
  • the driven pinion 1 and the adapter 13 having already been described in detail in connection with FIGS. 1 to 5 , reference can be made here to this description.
  • the camshaft adjusting device 31 further comprises a drive pinion 33 which, similar to the driven pinion 1 , is also configured as an annulus.
  • the drive pinion 33 is mounted through a slide bearing 35 on the driven pinion 1 .
  • the driving power for the camshaft adjusting device 31 is produced during operation via the drive pinion 33 and a crankshaft, not shown.
  • the drive pinion 33 is configured as a chain pulley 38 and can be connected through a chain rotationally fast to a crankshaft.
  • the torque is transmitted through an adjusting motor, not shown, to the drive pinion 33 and the driven pinion 1 and, thus also, to the camshaft. In this way, a controlled adjustment of the phase position between the camshaft and the crankshaft is achieved.
  • the camshaft adjusting device 31 further comprises a stop component 39 configured as a stop ring.
  • the stop component 39 is configured with a stop surface 41 for the camshaft, so that a limitation of the angle of rotation between the drive pinion 33 and the driven pinion 1 , which is connected through the adapter 13 rotationally fast to the camshaft, is achieved.
  • the stop component 39 is welded on its axial support surface 43 to the drive pinion 33 and is thus connected rotationally fast to this.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
US13/823,783 2010-11-11 2011-08-23 Camshaft adjuster for an internal combustion engine Abandoned US20130180484A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102010051051A DE102010051051A1 (de) 2010-11-11 2010-11-11 Nockenwellenversteller für eine Brennkraftmaschine
DE102010051051.3 2010-11-11
PCT/EP2011/064479 WO2012062492A1 (de) 2010-11-11 2011-08-23 Nockenwellenversteller für eine brennkraftmaschine

Publications (1)

Publication Number Publication Date
US20130180484A1 true US20130180484A1 (en) 2013-07-18

Family

ID=44509366

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/823,783 Abandoned US20130180484A1 (en) 2010-11-11 2011-08-23 Camshaft adjuster for an internal combustion engine

Country Status (6)

Country Link
US (1) US20130180484A1 (de)
EP (1) EP2638256B1 (de)
KR (1) KR101831012B1 (de)
CN (1) CN103201468B (de)
DE (1) DE102010051051A1 (de)
WO (1) WO2012062492A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018127858B3 (de) * 2018-11-08 2020-03-26 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Herstellung eines Wellgetriebes

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014221192A1 (de) 2014-10-20 2016-04-21 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008019586A1 (de) * 2008-04-18 2009-10-22 Schaeffler Kg Nockenwellenverstellvorrichtung
US8424500B2 (en) * 2009-08-06 2013-04-23 Delphi Technologies, Inc. Harmonic drive camshaft phaser with improved radial stability

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5417186A (en) * 1993-06-28 1995-05-23 Clemson University Dual-acting apparatus for variable valve timing and the like
DE10248355A1 (de) * 2002-10-17 2004-04-29 Ina-Schaeffler Kg Nockenwellenversteller mit elektrischem Antrieb
DE10323705B4 (de) * 2003-05-22 2017-03-16 Daimler Ag Vorrichtung zum geregelten Verstellen der relativen Drehlage zwischen einer Kurbelwelle und einer Nockenwelle
DE102004009128A1 (de) * 2004-02-25 2005-09-15 Ina-Schaeffler Kg Elektrischer Nockenwellenversteller
DE102005018956A1 (de) * 2005-04-23 2006-11-23 Schaeffler Kg Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
DE102005059884A1 (de) * 2005-12-15 2007-07-05 Schaeffler Kg Nockenwellenversteller
DE102009037403B4 (de) * 2009-08-13 2018-01-11 Schaeffler Technologies AG & Co. KG Elektrischer Nockenwellenversteller

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008019586A1 (de) * 2008-04-18 2009-10-22 Schaeffler Kg Nockenwellenverstellvorrichtung
US8424500B2 (en) * 2009-08-06 2013-04-23 Delphi Technologies, Inc. Harmonic drive camshaft phaser with improved radial stability

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018127858B3 (de) * 2018-11-08 2020-03-26 Schaeffler Technologies AG & Co. KG Wellgetriebe und Verfahren zur Herstellung eines Wellgetriebes

Also Published As

Publication number Publication date
CN103201468B (zh) 2015-07-01
CN103201468A (zh) 2013-07-10
EP2638256B1 (de) 2014-07-16
EP2638256A1 (de) 2013-09-18
KR20130125768A (ko) 2013-11-19
WO2012062492A1 (de) 2012-05-18
KR101831012B1 (ko) 2018-02-21
DE102010051051A1 (de) 2012-05-16

Similar Documents

Publication Publication Date Title
JP4735504B2 (ja) バルブタイミング調整装置
US7926457B2 (en) Device for phase-shifting the rotational angle of a drive wheel relative to an output shaft
US9534513B2 (en) Camshaft phaser actuated by an electric motor
KR101896672B1 (ko) 밸브 타이밍 조정장치
US8726865B2 (en) Harmonic drive camshaft phaser using oil for lubrication
RU2744418C2 (ru) Прецизионная планетарная передача
US20150133256A1 (en) Lantern-type gear unit
US9297283B2 (en) Camshaft unit
US20110067655A1 (en) Device for varying the angular position of a camshaft relative to a crankshaft of an internal combustion engine
US20130180484A1 (en) Camshaft adjuster for an internal combustion engine
CN108026799B (zh) 凸轮轴调节器
JP4877199B2 (ja) バルブタイミング調整装置
US20150135864A1 (en) Camshaft unit
US9840942B2 (en) Camshaft adjuster
US9556759B2 (en) Valve timing controller
JP4200728B2 (ja) トロイダル型無段変速機及び無段変速装置
US8371973B2 (en) Chain tensioner
JPH05263614A (ja) 内燃機関のバルブタイミング調節装置
CN208900517U (zh) 偏心定位的发动机惰齿轮轴结构
CN111479641B (zh) 组装式凸轮轴及用于制造组装式凸轮轴的方法
US20070161442A1 (en) Conical disk pair for a belt-driven conical-pulley transmission
JP6904219B2 (ja) バルブタイミング調整装置
JP4224509B2 (ja) 内燃機関のバルブタイミング制御装置
JP2009108705A (ja) バルブタイミング調整装置
JP2020046051A (ja) 潤滑構造

Legal Events

Date Code Title Description
AS Assignment

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:BRAUN, ARMIN;REEL/FRAME:030018/0492

Effective date: 20130314

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION

AS Assignment

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, GERMANY

Free format text: CHANGE OF NAME;ASSIGNOR:SCHAEFFLER TECHNOLOGIES GMBH & CO. KG;REEL/FRAME:037732/0347

Effective date: 20150101

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, GERMANY

Free format text: MERGER AND CHANGE OF NAME;ASSIGNORS:SCHAEFFLER TECHNOLOGIES AG & CO. KG;SCHAEFFLER VERWALTUNGS 5 GMBH;REEL/FRAME:037732/0228

Effective date: 20131231

AS Assignment

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, GERMANY

Free format text: CORRECTIVE ASSIGNMENT TO CORRECT THE PROPERTY NUMBERS PREVIOUSLY RECORDED ON REEL 037732 FRAME 0347. ASSIGNOR(S) HEREBY CONFIRMS THE APP. NO. 14/553248 SHOULD BE APP. NO. 14/553258;ASSIGNOR:SCHAEFFLER TECHNOLOGIES GMBH & CO. KG;REEL/FRAME:040404/0530

Effective date: 20150101