EP1114917A2 - Dispositif de variation de phase - Google Patents

Dispositif de variation de phase Download PDF

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Publication number
EP1114917A2
EP1114917A2 EP00890379A EP00890379A EP1114917A2 EP 1114917 A2 EP1114917 A2 EP 1114917A2 EP 00890379 A EP00890379 A EP 00890379A EP 00890379 A EP00890379 A EP 00890379A EP 1114917 A2 EP1114917 A2 EP 1114917A2
Authority
EP
European Patent Office
Prior art keywords
rotary member
camshaft
tension member
spindle
tension
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.)
Withdrawn
Application number
EP00890379A
Other languages
German (de)
English (en)
Other versions
EP1114917A3 (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
Application filed by TCG Unitech AG filed Critical TCG Unitech AG
Publication of EP1114917A2 publication Critical patent/EP1114917A2/fr
Publication of EP1114917A3 publication Critical patent/EP1114917A3/fr
Withdrawn legal-status Critical Current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
    • 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

Definitions

  • the present invention relates to a transmission for adjusting a first rotary member opposite a second rotary member, with a drive shaft that is concentric to the first and second rotary members.
  • GB 2 243 203 A, WO 92/04532 and WO 92/00441 show camshaft adjusting devices, where between a drive wheel and the camshaft a flexible link or a lever arrangement is interposed.
  • the camshaft can be adjusted by means of a braking device.
  • Such devices increase fuel consumption because in the braking device Energy is dissipated. It can also drive camshafts briefly become negative, which in the known devices unintended switching operations.
  • EP 0 041 708 A EP 0 016 331 A and US 5,040,651 A, and described in US 2,005,655 A flexible couplings, in which the The elasticity of one or more cables is used to compensate for shocks. In this way, however, a camshaft adjustment device can be used cannot be realized.
  • No. 4,540,223 A also shows a mechanism for the electrical connection two components that can be rotated against each other. A transmission of torques is not technically feasible with such a device.
  • the object of the present invention is to avoid these disadvantages and a To create gears that are robust, with little or no play and that can be trained with very large reduction ratios.
  • the drive shaft is connected to a spindle is on which a tension member is wound, and that one end of the tension member is firmly connected to the first rotary member, and that the tension member around at least one deflection roller is deflected, which is fixed to the second rotary member connected is. Since the transmission according to the invention has no gears, there is no backlash. With appropriate material selection for the Traction means can be achieved that this is jerky due to its own elasticity Balances and dampens loads, so that even in rough operation long life is achieved.
  • the tension member is band-shaped. This enables transmission of high torques with low loads in the area of the deflection rollers.
  • the tension member is designed as a rope is.
  • the advantage of using a rope is that it is helical can be wound on the spindle, the winding diameter not changed.
  • both the distance of the attachment point of the tension member on first rotary member and the distance of the axis of the deflection roller from the common Axis is large compared to the diameter of the spindle. It is particularly favorable if the distance of the attachment point of the tension member from the common axis in a range between five times to fifty times, preferably between ten times and thirty times The diameter of the spindle is.
  • the Winding diameter depending on the length of the wound tape slightly changed. This leads, if no other measures are provided, to change the gear ratio over the adjustment range of the transmission. Furthermore, the gear ratio depends on the respective Angular position of the rotary links to each other. If such an effect is undesirable is, it can in particular be provided that in the first rotary member Area of the attachment point of the tension member a drain cam for guidance the tension member is formed. By appropriate training of the drain cam you can achieve that the gear ratio over the whole Adjustment range is approximately uniform. For special applications However, a targeted change can also be made by designing the drain cam the gear ratio over the adjustment range.
  • a particularly large transmission ratio can be achieved that the tension member is guided over several pulleys that alternate with are connected to the first rotary member and to the second rotary member.
  • the tension member is in the manner of a pulley back and forth between the pulleys led here.
  • the present invention relates to a device for adjusting the Camshaft of an internal combustion engine, in which the camshaft is adjustable relative to a drive wheel.
  • the camshaft is fixedly connected to the first rotary member and the drive wheel is firmly connected to the second rotary member.
  • the transmission described above is particularly suitable for use with devices suitable for adjusting camshafts.
  • the compact and at the same time robust Version with a large gear ratio and the backlash-free operation are excellent prerequisites for use in internal combustion engines internal combustion.
  • an electric motor for adjusting the camshaft is connected to the drive shaft of the transmission. It is advantageous in this context if a housing of the electric motor is fixed the camshaft or the drive wheel is connected.
  • the rotating electric motor for example via slip rings or contactless by induction controlled.
  • a first rotary member 1 is opposite one second rotary member 2, which is shown with broken lines, pivoted about an axis 3.
  • Concentric to axis 3 is one Spindle 4 provided on which a tension member 5 consisting of a steel strip or a steel cable is arranged to be wound up.
  • the tension member 5 is fixed connected to the spindle 4.
  • this extends Tension member 5 via a deflection roller 7, which is rotatable about an axis 7a on the second Rotary member 2 is arranged and further to a drain cam 8 which is fixed with the first rotary member 1 is connected.
  • the tension member 5 is fixed to the Drain cam 8 connected.
  • the tension member 5 wound on the spindle 4. Due to the resulting tension, the Tension members 1 and 2 rotated against each other so that the distance between the guide roller 7 and the drain cam 8 shortened. If, for example, that the first rotating member 1 is arranged fixed in space, the second Rotary member 2 rotated counterclockwise.
  • the gear ratio corresponds essentially to the double ratio of the respective Normal distance r of the tension member 5 in the area between the deflection roller 7 and the drain cam 8 from the axis 3 to the diameter D of the Spindle 4. If the tension member 5 is a steel band, the diameter D must be Spindle 4 corrected for the respective thickness of the roll in this calculation become.
  • Fig. 1 has a torque transmission allowed in one direction only.
  • a two-sided torque transmission the mirror-inverted arrangement of another tension member, not shown, is required.
  • spindles 4a and 4b are two spindles 4a and 4b provided which are in engagement with a pinion 10 via gear wheels 9a and 9b, which is firmly connected to the drive shaft 11. This way an additional one Reduction caused, which is multiplicative with the reduction linked to the actual transmission.
  • the spindles 4a, 4b are symmetrical to each other mounted in the second rotary member 2, which carries four deflection rollers 7.
  • On each of the spindles 4a, 4b is a pair of tension members 5aa, 5ab; 5ba, 5bb in opposite directions wound up and guided around a deflection roller 7.
  • On one first rotary member 1 are molded pins 12 with which the tension members 5aa, 5ab; 5ba, 5bb are connected.
  • a traction device 5 is based on the Spindle 4 successively around three guide rollers 7a, 7b and 7c and is ultimately on a pin 12 which is fixedly connected to the first rotary member 1 is attached.
  • the first and the third deflection roller 7a and 7c are on second rotary member 2 arranged while the second guide roller 7b with the first rotary member 1 is firmly connected.
  • 5 is in the In the sense of a pulley, a multiple translation is achieved, so that a total significantly increased reduction ratio is achieved.
  • By opposing Arrangement of a second tension member 5 can also transmit torque here can be achieved in both directions.
  • FIG. 6 schematically shows a device for adjusting the camshaft an internal combustion engine shown.
  • the camshaft is indicated at 20 and stands with a first rotary member 1 of the above Gear in connection.
  • the second rotary member 2 of the transmission is also available a drive wheel 21 in connection via which a toothed belt, not shown or a chain, not shown, is guided.
  • the drive shaft 11 is through an electric motor 22 which is connected to the drive wheel 21 in a rotationally fixed manner is and is supplied with power via slip rings 23.
  • the camshaft 20 When the electric motor 22 is not driven, the camshaft 20 also moves in the same direction the drive wheel 21 driven. By rotating the drive shaft the electric motor 22 can be adjusted in advance or readjusted by the camshaft 20 what the timing of the controlled by the camshaft 20, Valves of the internal combustion engine, not shown, changed. By the big one A reduction ratio of the transmission according to the invention is sufficient small electric motor 22 in order to apply the corresponding adjustment torques.
  • the gearbox according to the invention makes it possible in particular for the camshaft to adjust an internal combustion engine free of play, efficiently and quickly.
  • the gearbox is robust and of small size. The adjustment of tax times of valves allows fuel consumption and exhaust emissions lower from internal combustion engines.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Quick-Acting Or Multi-Walled Pipe Joints (AREA)
  • Friction Gearing (AREA)
EP00890379A 2000-01-04 2000-12-18 Dispositif de variation de phase Withdrawn EP1114917A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT32000 2000-01-04
AT32000 2000-01-04

Publications (2)

Publication Number Publication Date
EP1114917A2 true EP1114917A2 (fr) 2001-07-11
EP1114917A3 EP1114917A3 (fr) 2002-03-06

Family

ID=3487427

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00890379A Withdrawn EP1114917A3 (fr) 2000-01-04 2000-12-18 Dispositif de variation de phase

Country Status (4)

Country Link
US (1) US20010006050A1 (fr)
EP (1) EP1114917A3 (fr)
AU (1) AU2173301A (fr)
WO (1) WO2001050057A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1416126A1 (fr) * 2002-11-04 2004-05-06 BorgWarner Inc. Système variateur de phase d'arbre à cames avec mécanisme de verrouillage électromagnétique pour actionnement de déphasage et de verrouillage
DE102005026247A1 (de) * 2005-06-08 2006-12-14 Schaeffler Kg Nockenwellentrieb für eine Brennkraftmaschine eines Kraftfahrzeugs

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10245742B4 (de) * 2002-10-01 2006-09-07 Josef Martin Gmbh & Co. Kg Mehrfach-Kupplungseinrichtung
EP1783333A1 (fr) * 2005-11-04 2007-05-09 Delphi Technologies, Inc. Dispositif variateur de phase
JP4718979B2 (ja) 2005-12-02 2011-07-06 トヨタ自動車株式会社 可変バルブタイミング装置
EP1801367A1 (fr) * 2005-12-23 2007-06-27 Delphi Technologies, Inc. Dispositif variateur de phase
AT503556B1 (de) * 2006-11-15 2007-11-15 Josef Martin Gmbh & Co Kg Kupplungseinrichtung für leitungen, insbesondere für hydraulikleitungen
DE102016007818A1 (de) * 2016-06-23 2017-12-28 Daimler Ag Verstellgetriebe mit einer verzahnungsfreien Wirkverbindung
KR102388166B1 (ko) 2016-09-02 2022-04-19 파커-한니핀 코포레이션 다수-라인 연결 신속 다중-커플링

Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2005655A (en) 1933-02-25 1935-06-18 Eclipse Aviat Corp Driving mechanism
GB497749A (en) 1937-06-25 1938-12-28 Standard Telephones Cables Ltd Improvements in or relating to operating means for manually operated variable condensers and like toning devices
US3307415A (en) 1965-02-17 1967-03-07 Harriette E Dobbs Reversible drive unit
US3691871A (en) 1970-06-25 1972-09-19 Rolamite Inc Rotary motion transmitting apparatus
US4106371A (en) 1976-05-06 1978-08-15 Mitsubishi Denki Kabushiki Kaisha Clamping tool
EP0016331A1 (fr) 1979-02-16 1980-10-01 E.I. Du Pont De Nemours And Company Accouplement à torsion absorbant l'énergie
EP0041708A2 (fr) 1980-06-09 1981-12-16 E.I. Du Pont De Nemours And Company Dispositif d'accouplement d'arbres, pour la transmission de couple; et transmission d'automobile
DE3415584A1 (de) 1983-04-29 1984-10-31 Lamb Technicon Corp., Warren, Mich. Kettenantrieb mit abtriebsseitiger periodischer ruhezeit
US4550223A (en) 1981-04-17 1985-10-29 Poitevin Jean Pierre R Test device, and method for locating faults in a two-lead line
US5040651A (en) 1990-07-17 1991-08-20 Eaton Corporation Self actuator for cam phaser with sprag clutch
GB2243203A (en) 1990-04-18 1991-10-23 Ford Motor Co Phase change mechanism
WO1992000441A1 (fr) 1990-06-26 1992-01-09 Ford Motor Company Limited Mecanisme de changement de phase
WO1992004532A1 (fr) 1990-09-12 1992-03-19 Ford Motor Company Limited Moteur a combustion interne a phases de distribution variables
WO1995021340A1 (fr) 1994-02-03 1995-08-10 Gilles Nard Variateur de vitesse en continu a entrainement positif
EP0773106A1 (fr) 1995-05-18 1997-05-14 Harmonic Drive Systems Inc. Dispositif de reglage de phase
WO1998032993A1 (fr) 1997-01-23 1998-07-30 Davinci Technology Corporation Transmission et entrainement par courroie d'engrenages planetaires

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3527480A (en) * 1969-03-17 1970-09-08 Harnischfeger Corp Multiple fluid coupling connection mechanism
US4747375A (en) * 1982-08-31 1988-05-31 Williams John K Device for controlling the phased displacement of rotating shafts
FR2645242B1 (fr) * 1989-03-29 1991-08-23 Etud Innovation Mat Agricole Connecteur fluidique multiple
ATE130919T1 (de) * 1991-07-09 1995-12-15 Faster Srl Schnellkupplung zum jeweils gleichzeitigen herstellen oder lösen der verbindungen mehrerer kupplungen und/oder anschlussstecker, insbesondere kupplungsblock für anbaufrontlader an fahrzeugen.

Patent Citations (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2005655A (en) 1933-02-25 1935-06-18 Eclipse Aviat Corp Driving mechanism
GB497749A (en) 1937-06-25 1938-12-28 Standard Telephones Cables Ltd Improvements in or relating to operating means for manually operated variable condensers and like toning devices
US3307415A (en) 1965-02-17 1967-03-07 Harriette E Dobbs Reversible drive unit
US3691871A (en) 1970-06-25 1972-09-19 Rolamite Inc Rotary motion transmitting apparatus
US4106371A (en) 1976-05-06 1978-08-15 Mitsubishi Denki Kabushiki Kaisha Clamping tool
EP0016331A1 (fr) 1979-02-16 1980-10-01 E.I. Du Pont De Nemours And Company Accouplement à torsion absorbant l'énergie
EP0041708A2 (fr) 1980-06-09 1981-12-16 E.I. Du Pont De Nemours And Company Dispositif d'accouplement d'arbres, pour la transmission de couple; et transmission d'automobile
US4550223A (en) 1981-04-17 1985-10-29 Poitevin Jean Pierre R Test device, and method for locating faults in a two-lead line
DE3415584A1 (de) 1983-04-29 1984-10-31 Lamb Technicon Corp., Warren, Mich. Kettenantrieb mit abtriebsseitiger periodischer ruhezeit
GB2243203A (en) 1990-04-18 1991-10-23 Ford Motor Co Phase change mechanism
WO1992000441A1 (fr) 1990-06-26 1992-01-09 Ford Motor Company Limited Mecanisme de changement de phase
US5040651A (en) 1990-07-17 1991-08-20 Eaton Corporation Self actuator for cam phaser with sprag clutch
WO1992004532A1 (fr) 1990-09-12 1992-03-19 Ford Motor Company Limited Moteur a combustion interne a phases de distribution variables
WO1995021340A1 (fr) 1994-02-03 1995-08-10 Gilles Nard Variateur de vitesse en continu a entrainement positif
EP0773106A1 (fr) 1995-05-18 1997-05-14 Harmonic Drive Systems Inc. Dispositif de reglage de phase
WO1998032993A1 (fr) 1997-01-23 1998-07-30 Davinci Technology Corporation Transmission et entrainement par courroie d'engrenages planetaires

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1416126A1 (fr) * 2002-11-04 2004-05-06 BorgWarner Inc. Système variateur de phase d'arbre à cames avec mécanisme de verrouillage électromagnétique pour actionnement de déphasage et de verrouillage
US6883479B2 (en) 2002-11-04 2005-04-26 Borgwarner Inc. VCT phaser having an electromagnetic lock system for shift and lock operation
DE102005026247A1 (de) * 2005-06-08 2006-12-14 Schaeffler Kg Nockenwellentrieb für eine Brennkraftmaschine eines Kraftfahrzeugs

Also Published As

Publication number Publication date
US20010006050A1 (en) 2001-07-05
EP1114917A3 (fr) 2002-03-06
WO2001050057A1 (fr) 2001-07-12
AU2173301A (en) 2001-07-16

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