EP0903471A1 - Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne - Google Patents

Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne Download PDF

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Publication number
EP0903471A1
EP0903471A1 EP98890262A EP98890262A EP0903471A1 EP 0903471 A1 EP0903471 A1 EP 0903471A1 EP 98890262 A EP98890262 A EP 98890262A EP 98890262 A EP98890262 A EP 98890262A EP 0903471 A1 EP0903471 A1 EP 0903471A1
Authority
EP
European Patent Office
Prior art keywords
camshaft
gear
electric motor
drive wheel
planetary gear
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.)
Granted
Application number
EP98890262A
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German (de)
English (en)
Other versions
EP0903471B1 (fr
Inventor
Siegfried Ing. Heer
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.)
TCG Unitech AG
Original Assignee
TCG Unitech AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from AT0158697A external-priority patent/AT407282B/de
Application filed by TCG Unitech AG filed Critical TCG Unitech AG
Publication of EP0903471A1 publication Critical patent/EP0903471A1/fr
Application granted granted Critical
Publication of EP0903471B1 publication Critical patent/EP0903471B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • 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
    • F01L1/352—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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the present invention relates to a device for adjusting the camshaft Internal combustion engine, with an adjustment mechanism that by an electric motor firmly connected to the camshaft or to the drive wheel is operated.
  • the camshaft of an internal combustion engine is usually driven by a sprocket is connected to the crankshaft via a drive chain, or one designed as a pulley Drive wheel, which is connected to the crankshaft via a toothed belt, driven.
  • Adjustment devices are known from DE 41 10 088 C1 and from DE 39 29 619 A1, where between a component connected to the camshaft and a an adjusting element is provided with the drive wheel in connection with the component has two helical gears with the corresponding gears of the camshaft or the drive wheel are engaged.
  • an axial displacement of this adjustment element can cause the camshaft to rotate relative to the drive wheel become.
  • One possibility of the axial displacement of the adjusting element is actuation by a hydraulic piston, which depends on the required adjustment is operated.
  • the disadvantage of this solution is that to achieve the required forces relatively large hydraulic piston is required, which is a great deal of construction represents.
  • the oil consumption by the operation of the piston is relatively large represents a load on the engine by an appropriate oil pump.
  • the camshaft only between two end positions be switched back and forth.
  • an electrical adjustment device is known from DE 41 01 676 A1, in which a Electric motor is provided, which moves the adjusting element via a threaded spindle.
  • a Electric motor is provided, which moves the adjusting element via a threaded spindle.
  • the adjusting element rotates essentially at the camshaft speed, it must an axial thrust bearing can be provided between the electric motor and the adjusting element, that absorbs the relative movement between the torsion-resistant and the rotating component.
  • This thrust bearing is in the known solution practically throughout Engine operation is loaded because of the torsional moments acting between the drive wheel and the camshaft always exerted a force acting in the axial direction on the adjusting element becomes. This thrust bearing is therefore a critical part of the life of the engine restricted.
  • an adjustment mechanism in which an electric motor is provided, which is fixedly connected to the drive wheel which drives the camshaft.
  • the electric motor drives a screw spindle on which an adjusting element is guided, that via a first group of levers with the camshaft and via a second group of Lever is connected to the drive wheel.
  • the operation of the electric motor can in this way a rotation of the camshaft relative to the drive wheel can be effected.
  • Such a device is very complex and requires a relatively large amount of space.
  • DE-A 36 07 256 shows an adjustment device in which the adjustment of the Camshaft is done by a stepper motor that is firmly connected to the drive wheel.
  • this stepper motor must absorb all the torque that drives the Camshaft is required.
  • Such a stepper motor decides due to the required Size and power consumption for practical use.
  • the US-A 5,293,845 shows an adjusting mechanism for a camshaft, which is a planetary gear having.
  • a stationary electric motor causes a phase shift the camshaft.
  • the disadvantage is that the power transmission for driving the Camshaft on the rotating gears of the planetary gear, so that the limited Efficiency of the planetary gear leads to the corresponding losses. Furthermore moves the axis of the drive wheel during an adjustment, which is due to complex Compensate clamping mechanisms.
  • the object of the present invention is to provide a device in which the above Disadvantages described can be avoided, and which makes it possible in particular to enable a quick and reliable adjustment of the camshaft in a simple manner. in particular, the device should take up little space, so that an independent Adjustment of two camshafts with a small axial distance is possible.
  • the adjusting mechanism Planetary gear includes.
  • a planetary gear By using a planetary gear, adjusting elements, which move in the axial direction can be avoided. This allows the mechanical Construction can be simplified and a small size can be achieved.
  • Another The advantage of the invention is that it is relatively easy to seal oil securely ensure that the electric motor runs dry. To also run an emergency run To ensure failure of the adjustment, it is generally provided that the drive torque of the camshaft is reached an end position in which a safe Operation of the internal combustion engine is possible.
  • the planetary gear preferably has a large reduction ratio, which preferably is greater than 1: 8 and particularly preferably greater than 1:12. Through one Reduction ratio can, if necessary, be achieved or at least can be approximately achieved. In this way, the electric motor during normal operation of the internal combustion engine, in which there is no adjustment, not or only minimal burden. This increases the service life and reduces the amount of energy required.
  • the Electric motor and an internally toothed gear of the planetary gear fixed to the drive wheel are connected.
  • the planet carrier of the planetary gear is preferably fixed connected to the camshaft.
  • the output shaft of the electric motor is included the sun gear of the planetary gear. This way, a relatively large one Reduction ratio can be achieved.
  • the planetary gear consists only of an internally toothed gear and a planet carrier with a single planet gear mounted on it.
  • a sun gear is one of them Planetary gear not provided.
  • the number of teeth of the planet gear is preferred only slightly smaller than the number of teeth of the internally toothed gear, and indeed preferably by one. This means that the axis of the planet gear is only slightly opposite the axis of the internally toothed gear is shifted. Stand this way always several teeth of these gears engaged at the same time, so that a very favorable situation with regard to the load is given.
  • Such a device can therefore be extremely be made compact, so that even with a small distance two camshafts independently can be adjusted from each other. It also creates a large reduction ratio achieved what in terms of the required size of the electric motor is cheap.
  • the electric motor is firmly connected to the camshaft and that the planet gear is connected to the drive gear via a synchronization clutch.
  • the Synchronous clutch which is designed as an Oldham clutch, for example, the same axial offset from the planet gear and drive gear.
  • the electric motor is firmly connected to the drive wheel and that the planet gear is connected to the camshaft via a synchronous clutch is.
  • the planet carrier acts as the output shaft of the electric motor is formed, which has a desaxed portion on which the planet gear is stored.
  • Exact control of the adjustment angle can be achieved in that the electric motor is designed as a stepper motor.
  • the present invention relates to an internal combustion engine, which has a device as described above.
  • FIG. 1 a first embodiment variant of the present Invention in longitudinal section
  • Fig. 2 shows another embodiment of the present Invention in longitudinal section
  • Fig. 3 shows the variant of Fig. 2 in a section Line III - III in Fig. 2, wherein individual components are not to increase clarity are shown
  • 4 is an exploded view of the embodiment of FIG. 2 and 3
  • FIG. 5 shows a detail of this embodiment variant.
  • FIG. 1 A first embodiment variant of the present invention is shown in FIG. 1.
  • a bracket 30 On a camshaft 1, a bracket 30 is rotatable, but axially fixed.
  • a toothing 36 is provided on the outer circumference, which for A toothed belt is used to drive the camshaft 1 and thus the drive wheel represents.
  • the holder 30 also carries a plate 31 on which an electric motor 15 is firmly attached. The electric motor 15 thus rotates together with the drive wheel 36. Slip rings 19 are provided, which are fed by fixed sliding contacts 41 become.
  • the pinion 32 of the electric motor 15 stands with a planetary gears 33, 34 Ring gear, i.e. an internally toothed gear 35 which is integral with the bracket 30 is formed.
  • a planet carrier 37 which rotatably supports the planet gears 33, 34, is fixed connected to the camshaft 1. If the electric motor 15 is not activated, it stops the pinion 32 is still with respect to the motor 15, and thus the pinions 32 and Planet carrier 37 at the speed of the drive wheel 36, whereby the camshaft 1 rotates at this speed. By controlling the electric motor 15, a Relative movement of the planet carrier 37 in relation to the drive wheel 36 can be effected. Due to the relatively large translation by the planetary gear, this is achieved accordingly large torques for adjusting the camshaft 1 by a relative underpowered electric motor 15 can be provided. The seal of the system in relation to the oil chamber in the area of camshaft 1 takes place via radial shaft seals 38 and 39. A screw 40 is used to attach the planet carrier the camshaft 1.
  • the planetary gear consisting of the gears 32, 33, 34 and 35, in a known manner and be carried out without play.
  • these gears 32 to 35 can be made of high-strength plastic.
  • the camshaft 1 has one at its end Flange 2.
  • a drive wheel 6 for the camshaft is on the flange 2 via a slide bearing 42 1, which has a toothing 6a on its circumference for receiving a not shown Has drive chain.
  • a holding body 43 is connected to the flange 2 via threaded bolts 8.
  • the threaded bolts 8 pass through openings 10 in the drive wheel 6, which are designed as arc-shaped elongated holes. This is the angular range at the same time the adjustment of the camshaft 1 defined.
  • a shaft nut 44 is fastened to the holding body 43, which carries an electric motor 15 via screws 45. As with the previous one
  • the electric motor 15 is implemented as a variant via slip rings 19 and sliding contacts 41 powered.
  • the output shaft 29 of the electric motor 15 is on the holding body 43 via roller bearings 46 and 47 and mounted on the shaft nut 44 and has one at its end remote from the motor 15 desaxed section 48.
  • the roller bearings 46 and 47 are secured by circlips 49 in Maintained axial direction.
  • At the desaxed section there is a planet gear via a needle bearing 50 51 mounted, which is in engagement with an internally toothed gear 52, which is in one piece is formed with the holding body 43.
  • An axial plain bearing bush 53 ensures that Planet gear 51 in the axial direction.
  • the planet gear 51 is via a so-called Oldham clutch 54, which is a constant velocity joint represents, with the drive wheel 6 in rotary connection.
  • the Oldham coupling 54 has one Engagement part 55, which is connected to the planet gear 51 via a sliding guide 56, which limited movement of the engaging member 55 with respect to the planet gear 51 in the Level of Fig. 2 allows.
  • the engagement part 55 is with an adapter 58 of the Drive wheel 6 via a further sliding guide 57 in connection, which is limited Movement of the engaging part 55 relative to the drive wheel 6 in the plane of FIG. 3 enables. In this way, it is possible to drive the drive torque from the drive wheel 6 to the To transfer planet gear 51, wherein the eccentricity ⁇ is overcome. Screws 59 connect the adapter 58 to the sprocket 6 and at the same time secure the engagement part 55.
  • a housing 60 which seals with a radial shaft sealing ring 61 with respect to the holding part 43 is, separates the engine-side components, such as camshaft 1, Oldham coupling 54 and the planetary gear from the non-oil-wetted components, such as the electric motor 15.
  • the structure of the planetary gear is shown in FIG. 5.
  • the internal gear 52 in the holding body 43 has fourteen teeth, while the planet gear 51 has thirteen teeth.
  • the tip circle of the planet gear touches 51 approximately the tip circle of the internally toothed gear 52.
  • the planetary gear can be made very compact. It also causes one revolution of the output shaft 29 of the electric motor 15 is only a thirteenth revolution of the planet gear 51 with respect to the electric motor 15, so that the load on the Electric motor can also be minimized.
  • the present invention makes it possible to control the valve timing of an internal combustion engine easy and safe to change. It is particularly advantageous that any Intermediate positions can be controlled.
EP98890262A 1997-09-19 1998-09-10 Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne Expired - Lifetime EP0903471B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
AT1586/97 1997-09-19
AT158697 1997-09-19
AT0158697A AT407282B (de) 1997-09-19 1997-09-19 Vorrichtung zur verstellung einer nockenwelle
AT135898 1998-08-06
AT1358/98 1998-08-06
AT135898 1998-08-06

Publications (2)

Publication Number Publication Date
EP0903471A1 true EP0903471A1 (fr) 1999-03-24
EP0903471B1 EP0903471B1 (fr) 2001-12-05

Family

ID=25595638

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98890262A Expired - Lifetime EP0903471B1 (fr) 1997-09-19 1998-09-10 Dispositif pour varier le calage d'un arbre à cames de moteur à combustion interne

Country Status (5)

Country Link
US (1) US6138622A (fr)
EP (1) EP0903471B1 (fr)
AT (1) ATE210243T1 (fr)
DE (1) DE59802310D1 (fr)
ES (1) ES2167864T3 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1039101A2 (fr) 1999-03-23 2000-09-27 TCG UNITECH Aktiengesellschaft Déphaseur d'arbre à cames pour moteur à combustion interne
EP1039100A2 (fr) 1999-03-23 2000-09-27 TCG UNITECH Aktiengesellschaft Déphaseur d'arbre à cames pour moteur à combustion interne
EP1052379A2 (fr) 1999-05-12 2000-11-15 TCG UNITECH Aktiengesellschaft Déphaseur d'arbre à cames pour moteur à combustion interne
EP1136657A2 (fr) 2000-03-09 2001-09-26 TCG UNITECH Aktiengesellschaft Dispositif déphaseur d'arbre à cames
EP1136658A2 (fr) 2000-03-09 2001-09-26 TCG UNITECH Aktiengesellschaft Dispositif de réglage du calage d'un arbre à cames
US6328006B1 (en) 1999-03-23 2001-12-11 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
AT409786B (de) * 1999-03-23 2002-11-25 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle einer brennkraftmaschine mit innerer verbrennung
AT410825B (de) * 1999-03-23 2003-08-25 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle einer brennkraftmaschine mit innerer verbrennung
DE102008006199A1 (de) 2008-01-26 2009-07-30 Schaeffler Kg Stellantrieb für ein Verstellelement
EP2530260A1 (fr) * 2011-06-03 2012-12-05 Magna Powertrain AG & Co. KG Arbre d'embrayage, actionneur, boîte de vitesses à dispositif de réglage d'arbre à came et régulateur de l'arbre à came
WO2013075933A1 (fr) * 2011-11-24 2013-05-30 Magna Powertrain Ag & Co. Kg Entraînement de déphasage avec accouplement oldham

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10054798B4 (de) * 2000-11-04 2009-03-05 Schaeffler Kg Elektrisch angetriebene Vorrichtung zur Drehwinkelverstellung einer Welle gegenüber ihrem Antrieb
AU2002326914A1 (en) * 2001-09-14 2003-04-01 Crane Plastics Company Llc Fence assembly with connectors
DE10207760B4 (de) * 2002-02-23 2019-10-31 Schaeffler Technologies AG & Co. KG Vorrichtung zum lösbaren Verbinden und Verstellen zweier zueinander drehwinkelverstellbarer Wellen
JP3937164B2 (ja) * 2002-04-19 2007-06-27 株式会社デンソー バルブタイミング調整装置
DE10220687A1 (de) * 2002-05-10 2003-11-20 Ina Schaeffler Kg Nockenwellenversteller mit elektrischem Antrieb
JP4012445B2 (ja) * 2002-08-13 2007-11-21 株式会社日立製作所 内燃機関の可変動弁装置
JP4269338B2 (ja) * 2003-10-16 2009-05-27 株式会社デンソー バルブタイミング調整装置
KR101158926B1 (ko) * 2004-06-09 2012-07-03 섀플러 카게 캠축 조정 장치
DE102004038681B4 (de) 2004-08-10 2017-06-01 Schaeffler Technologies AG & Co. KG Elektromotorischer Nockenwellenversteller
DE102005018956A1 (de) * 2005-04-23 2006-11-23 Schaeffler Kg Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
JP4596481B2 (ja) * 2006-08-30 2010-12-08 株式会社デンソー 内燃機関の可変バルブタイミング制御装置
WO2014147583A1 (fr) * 2013-03-20 2014-09-25 Tq-Systems Gmbh Démultiplicateur harmonique à couronne de broches
JP2016044627A (ja) * 2014-08-25 2016-04-04 アイシン精機株式会社 弁開閉時期制御装置
JP6531641B2 (ja) * 2015-12-21 2019-06-19 アイシン精機株式会社 弁開閉時期制御装置
DE102016122845A1 (de) 2016-11-28 2018-05-30 Tq-Systems Gmbh Harmonisches Pinring-Getriebe, Drehmomentmessvorrichtung und Freilaufanordnung
JP2018096387A (ja) * 2016-12-08 2018-06-21 アイシン精機株式会社 歯車伝動機構

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3978829A (en) * 1974-06-10 1976-09-07 Nissan Motor Co., Ltd. Self-adjustable camshaft drive mechanism
GB2182736A (en) * 1985-11-07 1987-05-20 Stidworthy Frederick M A variable drive assembly
EP0234853A1 (fr) * 1986-02-19 1987-09-02 Clemson University Dispositif pour varier le calage des soupapes d'un moteur à combustion interne
DE3607256A1 (de) 1986-03-05 1987-09-10 Bayerische Motoren Werke Ag Vorrichtung zum gesteuerten/geregelten verstellen der relativen drehlage eines getriebenen zu einem treibenden maschinenteil
GB2221513A (en) 1988-08-05 1990-02-07 Ford Motor Co Variable phase drive mechanism
DE3929619A1 (de) 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Kuppelstange fuer eine vorrichtung zur drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine
DE4040486A1 (de) * 1990-06-22 1992-01-02 Schrick Gmbh Dr Vorrichtung bei verbrennungsmotoren zur drehung der nockenwelle relativ zum nockenwellenantriebsrad
DE4110088C1 (en) 1991-03-27 1992-07-09 Bayerische Motoren Werke Ag, 8000 Muenchen, De Relative shaft bearing position changing mechanism - has annular coupler with inner and outer toothing linked to axially displaceable piston
DE4101676A1 (de) 1991-01-22 1992-07-23 Schaeffler Waelzlager Kg Verstellvorrichtung fuer eine nockenwelle
US5293845A (en) 1991-09-02 1994-03-15 Toyota Jidosha Kabushiki Kaisha Control mechanism for engine valve timing

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3320835A1 (de) * 1983-06-09 1984-12-13 Dieter 7460 Balingen Fuoß Multipositionsantrieb
US4967701A (en) * 1989-01-12 1990-11-06 Nippondenso Co., Ltd. Valve timing adjuster
US5117784A (en) * 1991-05-03 1992-06-02 Ford Motor Company Internal combustion engine camshaft phaseshift control system
JPH08260923A (ja) * 1995-03-27 1996-10-08 Unisia Jecs Corp 内燃機関の可変動弁装置のバルブリフト特性検出装置
US5860328A (en) * 1995-06-22 1999-01-19 Chrysler Corporation Shaft phase control mechanism with an axially shiftable splined member
US5673659A (en) * 1995-06-22 1997-10-07 Chrysler Corporation Lead screw driven shaft phase control mechanism
US5680837A (en) * 1996-09-17 1997-10-28 General Motors Corporation Planetary cam phaser with worm electric actuator
AT407282B (de) * 1997-09-19 2001-02-26 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3978829A (en) * 1974-06-10 1976-09-07 Nissan Motor Co., Ltd. Self-adjustable camshaft drive mechanism
GB2182736A (en) * 1985-11-07 1987-05-20 Stidworthy Frederick M A variable drive assembly
EP0234853A1 (fr) * 1986-02-19 1987-09-02 Clemson University Dispositif pour varier le calage des soupapes d'un moteur à combustion interne
DE3607256A1 (de) 1986-03-05 1987-09-10 Bayerische Motoren Werke Ag Vorrichtung zum gesteuerten/geregelten verstellen der relativen drehlage eines getriebenen zu einem treibenden maschinenteil
GB2221513A (en) 1988-08-05 1990-02-07 Ford Motor Co Variable phase drive mechanism
DE3929619A1 (de) 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Kuppelstange fuer eine vorrichtung zur drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine
DE4040486A1 (de) * 1990-06-22 1992-01-02 Schrick Gmbh Dr Vorrichtung bei verbrennungsmotoren zur drehung der nockenwelle relativ zum nockenwellenantriebsrad
DE4101676A1 (de) 1991-01-22 1992-07-23 Schaeffler Waelzlager Kg Verstellvorrichtung fuer eine nockenwelle
DE4110088C1 (en) 1991-03-27 1992-07-09 Bayerische Motoren Werke Ag, 8000 Muenchen, De Relative shaft bearing position changing mechanism - has annular coupler with inner and outer toothing linked to axially displaceable piston
US5293845A (en) 1991-09-02 1994-03-15 Toyota Jidosha Kabushiki Kaisha Control mechanism for engine valve timing

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1039101A2 (fr) 1999-03-23 2000-09-27 TCG UNITECH Aktiengesellschaft Déphaseur d'arbre à cames pour moteur à combustion interne
EP1039100A2 (fr) 1999-03-23 2000-09-27 TCG UNITECH Aktiengesellschaft Déphaseur d'arbre à cames pour moteur à combustion interne
US6257186B1 (en) 1999-03-23 2001-07-10 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
AT410825B (de) * 1999-03-23 2003-08-25 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle einer brennkraftmaschine mit innerer verbrennung
AT409786B (de) * 1999-03-23 2002-11-25 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle einer brennkraftmaschine mit innerer verbrennung
US6302073B1 (en) 1999-03-23 2001-10-16 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6328006B1 (en) 1999-03-23 2001-12-11 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
EP1052379A2 (fr) 1999-05-12 2000-11-15 TCG UNITECH Aktiengesellschaft Déphaseur d'arbre à cames pour moteur à combustion interne
EP1136658A3 (fr) * 2000-03-09 2001-12-19 TCG UNITECH Aktiengesellschaft Dispositif de réglage du calage d'un arbre à cames
AT408897B (de) * 2000-03-09 2002-03-25 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle
AT409030B (de) * 2000-03-09 2002-05-27 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle
EP1136658A2 (fr) 2000-03-09 2001-09-26 TCG UNITECH Aktiengesellschaft Dispositif de réglage du calage d'un arbre à cames
US6543399B2 (en) 2000-03-09 2003-04-08 Tcg Unitech Aktiengesellschaft Apparatus for adjusting a camshaft
EP1136657A2 (fr) 2000-03-09 2001-09-26 TCG UNITECH Aktiengesellschaft Dispositif déphaseur d'arbre à cames
DE102008006199A1 (de) 2008-01-26 2009-07-30 Schaeffler Kg Stellantrieb für ein Verstellelement
DE102008006199B4 (de) 2008-01-26 2022-04-21 Schaeffler Technologies AG & Co. KG Stellantrieb für ein Verstellelement
EP2530260A1 (fr) * 2011-06-03 2012-12-05 Magna Powertrain AG & Co. KG Arbre d'embrayage, actionneur, boîte de vitesses à dispositif de réglage d'arbre à came et régulateur de l'arbre à came
WO2013075933A1 (fr) * 2011-11-24 2013-05-30 Magna Powertrain Ag & Co. Kg Entraînement de déphasage avec accouplement oldham

Also Published As

Publication number Publication date
US6138622A (en) 2000-10-31
ES2167864T3 (es) 2002-05-16
EP0903471B1 (fr) 2001-12-05
DE59802310D1 (de) 2002-01-17
ATE210243T1 (de) 2001-12-15

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