[go: up one dir, main page]

US20100064997A1 - Continuous camshaft phase shifting apparatus - Google Patents

Continuous camshaft phase shifting apparatus Download PDF

Info

Publication number
US20100064997A1
US20100064997A1 US12/441,841 US44184107A US2010064997A1 US 20100064997 A1 US20100064997 A1 US 20100064997A1 US 44184107 A US44184107 A US 44184107A US 2010064997 A1 US2010064997 A1 US 2010064997A1
Authority
US
United States
Prior art keywords
planet
sun gear
gear
input
phase shift
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
US12/441,841
Other languages
English (en)
Inventor
Xiaolan Ai
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.)
JTEKT Bearings North America LLC
Original Assignee
Timken Co
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 Timken Co filed Critical Timken Co
Priority to US12/441,841 priority Critical patent/US20100064997A1/en
Assigned to THE TIMKEN COMPANY reassignment THE TIMKEN COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AI, XIAOLAN, MR.
Assigned to KOYO BEARINGS USA LLC reassignment KOYO BEARINGS USA LLC PATENT ASSIGNMENT AGREEMENT Assignors: THE TIMKEN COMPANY
Publication of US20100064997A1 publication Critical patent/US20100064997A1/en
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
    • 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
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation

Definitions

  • Camshaft phase shifting mechanisms are used in internal combustion engines to vary valve timing to achieve benefits of improving fuel consumption and improve exhaust gas quality. It is possible, with an adequate camshaft shifter, to vary valve timing for maximum comfort and/or maximum torque and for the highest performance.
  • camshaft phase shifting mechanisms are hydraulic powered. These camshaft phase shifting mechanisms generally consist of a hydraulic shifter unit, a regulation valve and a control circuit.
  • the shifter unit has to have a low leakage rate and a sufficiently large chamber/piston to ensure adequate stiffness.
  • the regulation valve has to ensure high flow rate during adjustment cycles while providing a precise regulation to fix the set-point angles.
  • Some camshaft phase shifting mechanisms require a separate high-pressure supply. These current mechanisms are complex, expensive and need regular maintenance. Additionally, the performance of these current mechanisms depends mainly on temperature parameters.
  • This invention relates to a phase shifting mechanism, and more specifically to an electro-mechanical phase shifting mechanism for a camshaft of an internal combustion engine.
  • the phase shifting mechanism of the present disclosure comprises a positive epicyclic gear train with frictional locking capability.
  • the gear train has three co-axial rotatable branches. The first branch operatively couples to an input shaft (i.e., the crankshaft), the second branch operatively couples to an output shaft and the third branch, a lockable branch, operatively couples to a rotor of an electric machine.
  • the gear train can only be unlocked during phase adjustment by the electric machine that is connected to the third branch, the lockable branch.
  • the input shaft couples to the crankshaft
  • the output shaft couples to the camshaft
  • the planetary gear train co-axially aligns around the input shaft and the output shaft.
  • An input sun gear of the planetary gear train couples to the input shaft and an output sun gear of the planetary gear train couples to the output shaft.
  • the planetary gear train has first and second planet gears that engage the input and output sun gears, respectively, and are united to rotate about a common axis at the same angular velocity.
  • the carrier includes a planet shaft and a first planet bearing and a second planet bearing on which the united first and second planet gears respectively rotate.
  • a locking mechanism of the phase shifting mechanism locks the planetary gear train in a locked condition by preventing the planet gears from rotating relative to the carrier to rotate the input sun gear, the output sun gear and the carrier as a unit such that the phase shift angle for the output shaft with respect to the input shaft remains the same and the output shaft rotates with the input shaft at the same angular velocity.
  • the electric machine applies torque to the locking mechanism in order to unlock the locking mechanism such that the output shaft rotates at a different angular velocity with respect to the input shaft.
  • FIG. 1 illustrates a schematic view of components of an internal combustion engine illustrating a drive, a camshaft and a phase shifting mechanism constructed in accordance with and embodying the present disclosure
  • FIG. 2 illustrates a cross sectional view of an input shaft, an output shaft and the phase shifting mechanism
  • FIG. 3 illustrates an exploded view of a phase shifting mechanism constructed in accordance with and embodying the present disclosure illustrating a planetary gear train and locking mechanism of the phase shifting mechanism wherein first and second planet gears of the planetary gear train are identical and integrated with one another;
  • FIG. 4 illustrates another exploded view of components of the phase shifting mechanism of FIG. 3 ;
  • FIG. 5 illustrates a cross sectional view of the gear train and locking mechanism constructed in accordance with and embodying the present disclosure
  • FIG. 6 illustrates a perspective view of an input sun gear and an extension of a limiting device of the phase shifting mechanism
  • FIG. 7 illustrates a perspective view of an output sun gear and another embodiment of an extension of a limiting device of the phase shift mechanism.
  • an electro-mechanic phase shifting mechanism generally shown as A is shown ( FIGS. 1 and 2 ).
  • the phase shifting mechanism A is located between a drive 10 and a camshaft 12 of an internal combustion engine 14 .
  • the phase shifting mechanism A comprises a sprocket 16 , an input shaft 18 coupled to the drive 10 (crankshaft) ( FIG. 1 ), an epicyclic gear train generally shown as 20 having a locking mechanism generally shown as 22 , an electric machine generally shown as 24 and an output shaft 26 coupled to the camshaft 12 ( FIG. 1 ).
  • the epicyclic gear train 20 co-axially aligns around the input shaft 18 and the output shaft 26 .
  • the epicyclic gear train 20 comprises a first branch in the form of an input sun gear 28 , a second branch in the form of an output sun gear 30 , a lockable third branch in the form a carrier 32 , a first set of planet gears 34 and a second set of planet gears 36 .
  • the input sun gear 28 meshes with the first set of planet gears 34
  • the output sun gear 30 meshes with the second set of planet gears 36 .
  • Each planet gear 34 in the first planet gear set couples to, and thus rotates as a unit with, a corresponding planet gear 36 in the second planet gear set.
  • the planet gears 34 , 36 are substantially identically formed and are integrated as a single gear. Planet gears 34 , 36 together form a planetary gear pair to rotate about a common axis at the same angular velocity.
  • the planetary gear pairs are supported by a set of planet shafts 38 ( FIG. 1 ), through bearings.
  • the carrier 32 is supported in a housing 40 though bearings 42 .
  • the input shaft 18 connects to sprocket 16 at one end and to the input sun gear 28 at the other end.
  • the input shaft 18 is supported in the housing 40 though bearing 44 .
  • the output shaft 26 connects to the output sun gear 30 at one end and couples to camshaft 12 ( FIG. 1 ) at the other end.
  • the electric machine 24 includes a rotor 46 and a stator 48 .
  • the rotor 46 fits over the carrier 32 to establish a firm mechanical connection, so that the carrier 32 rotates with the rotor 46 as a unit.
  • the stator 48 mounts to the housing 40 .
  • the input shaft 18 and output shaft 26 may extend beyond the input sun gear 28 and the output sun gear 30 with one piloted on the other through bearing 49 ( FIG. 1 ). Input shaft 18 is allowed to rotate with respect to the output shaft 26 when phase shift between the two shafts 18 , 26 is desirable. To prevent excessive angular displacement between the two shafts 18 , 26 an angular position limiting device generally shown as 50 ( FIGS. 1 , 3 - 5 ) may be employed to provide mechanical stops in both rotating directions.
  • the limiting device 50 rotatably couples the input sun gear 28 with the output sun gear 30 .
  • the limiting device 50 in an embodiment, comprises a slot 52 positioned on a face 54 of the input sun gear 28 and comprises an extension 56 protruding from another face 58 of the output sun gear 30 such that the extension 56 slidably engages with the slot 52 .
  • the extension 56 comprises pins protruding from the output sun gear 30 .
  • an extension 60 comprise key members protruding from the face 54 of the input sun gear 28 ( FIG. 6 ) and/or protruding from the face 58 of the output sun gear 30 ( FIG. 7 ).
  • the key members slidably engage the appropriate mating surface positioned on the opposing sun gear.
  • the extensions 56 slidably reciprocate within the opposing slot 52 such that the slots limit travel movement of the extensions 56 to prevent excessive angular displacement between the shafts 18 , 26 .
  • the epicyclic gear train 20 has a basic gear ratio “SR 0 ” defined as
  • the basic gear ratio can be determined by tooth numbers of the gears in the epicyclic gear train 20 , as below
  • phase shifting angle for the output shaft 26 with respect to the input shaft 18 is determined as
  • ⁇ ⁇ ⁇ ⁇ ( 1 - SR 0 ) ⁇ ⁇ 0 t ⁇ ( ⁇ S ⁇ ⁇ 1 - ⁇ C ) ⁇ ⁇ ⁇ . ( 3 )
  • the locking mechanism 22 of the epicyclic gear train 20 is designed to have a configuration and internal geometry that ensure an internal jam or lock when no external torque is applied to the carrier 32 .
  • the locking mechanism 22 comprises conical bearings 62 , 64 , that, under radial load, impose frictional resistant torque on the planetary gear pairs 34 , 36 that tend to prevent them from rotating about their support shafts 38 .
  • the radial load is in direct proportion to the amount of torque being transmitted.
  • the frictional resistant torque is also in proportion to the input and output torque.
  • the input torque from the input sun gear 28 and the output torque from the output sun gear 30 result in a differential torque that tries to rotate the planetary gears 34 , 36 . If the maximum available frictional torque is greater than the differential applied torque, the epicyclic gear train 20 is frictionally locked. To ensure this condition, the following internal geometry relationship between the planetary gear train 20 and the coefficients of friction between the first planet gear 34 and the first planet bearing 42 and between the second planet gear 36 and the second planet bearing 44 is characterized as
  • the locking mechanism 22 prevents the planet gears 34 , 36 from rotating relative to the carrier 32 to rotate the input sun gear 28 , the output sun gear 30 and the carrier 32 as a unit such that the phase shift angle for the output shaft 26 with respect to the input shaft 18 remains the same and the output shaft 26 rotates with the input shaft 18 at the same angular velocity.
  • the locking mechanism 22 comprises friction torques caused by coefficients of friction between the first planet gear 34 and the first planet bearing 62 and between the second planet gear 36 and the second planet bearing 64 .
  • the electric machine 24 couples to the carrier 32 .
  • the electric machine 24 applies a torque to the planetary gear train 20 for unlocking the friction torques enabling the carrier 32 to rotate relative to at least one of the input sun gear 28 and the output sun gear 30 wherein the phase shift angle for the output shaft 26 with respect to the input shaft 18 changes so that the output shaft 26 assumes a different angular velocity with respect to the input shaft 18 .
  • the electro-mechanic camshaft phase shifting mechanism A has three operation modes.
  • the first operating mode relates to a neutral mode in which the electric machine 24 is switched off (i.e., consuming no electric power or generating any electric power); and thus, exerting no torque on the carrier 32 .
  • the epicyclic gear train 20 With no actuation torque exerting on the carrier 32 , the epicyclic gear train 20 is frictionally locked or “internally jammed” by the locking mechanism 22 . In this locked state, the epicyclic gear train 20 can only be rotated as unit.
  • the second operating mode relates to a generating mode, in which the electric machine 24 applies a resistant torque to the gear train 20 , slowing the rotor 46 down such that ⁇ C ⁇ S1 .
  • the epicyclic gear train 20 converts mechanical power into electric power, acting as a generator.
  • the resistant torque unlocks the epicyclic gear train 20 .
  • the output shaft 26 rotates with the input shaft 18 in the same direction but at a faster or slower angular velocity. From equation (3), there will be a continuous phase advancing, if SR 0 >1, or retarding, if SR 0 ⁇ 1, of the output shaft with respect to the input shaft 18 . Accordingly, in this operating mode, there is a continuous phase advancing or retarding of output shaft 26 with respect to the input shaft 18 .
  • the torque applied by the electric machine 24 to the planetary gear train 20 comprises a resistant torque which unlocks the carrier 32 by overcoming the torque caused by friction between the first planet gear 34 and the first planet bearing 62 and between the second planet gear 36 and the second planet bearing 64 .
  • the resistant torque unlocks the carrier 32 to change the phase shift angle such that the output shaft 26 rotates with respect to the input shaft 18 at a different angular velocity.
  • the output shaft 26 rotates with respect to the input shaft 18 in the same angular direction.
  • the third operating mode relates to a motoring mode, in which the electric machine 24 applies a driving torque to the gear train 20 , speeding the rotor 46 and carrier 32 up such that ⁇ C > ⁇ S1 .
  • the electric machine 24 draws electric power from a supplier (not shown) and converts it into mechanical power. In doing so, the electric machine 24 acts as a motor.
  • the driving torque unlocks the epicyclic gear train 20 .
  • the output shaft 26 rotates with the input shaft 18 in the same direction but at a slower or faster angular velocity. From equation (3), there will be a continuous phase retarding, if SR 0 >1 or advancing, if SR 0 ⁇ 1 of the output shaft 26 with respect to the input shaft 18 . Accordingly, in this operating mode, there is a continuous phase retarding or advancing of output shaft 26 with respect to the input shaft 18 .
  • the torque applied by the electric machine 24 to the planetary gear train 20 comprises a driving torque which unlocks the carrier 32 by overcoming the torques caused by friction between the first planet gear 34 and the first planet bearing 62 and between the second planet gear 36 and the second planet bearing 64 .
  • the driving torque unlocks the carrier 32 to change the phase shift angle such that the output shaft 26 rotates with respect to the input shaft 18 in the same angular direction and at a different angular velocity.
  • the output shaft 26 rotates with respect to the input shaft 18 in the same angular direction.
  • phase shifting mechanism A uses low cost bearings.
  • the phase shifting mechanism A uses low cost electric machines, such as a switched reluctance motor, to reduce the overall cost.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
US12/441,841 2006-09-19 2007-09-18 Continuous camshaft phase shifting apparatus Abandoned US20100064997A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US12/441,841 US20100064997A1 (en) 2006-09-19 2007-09-18 Continuous camshaft phase shifting apparatus

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US84569206P 2006-09-19 2006-09-19
PCT/US2007/078755 WO2008036650A1 (fr) 2006-09-19 2007-09-18 Appareil de déphasage pour arbre à cames en continu
US12/441,841 US20100064997A1 (en) 2006-09-19 2007-09-18 Continuous camshaft phase shifting apparatus

Publications (1)

Publication Number Publication Date
US20100064997A1 true US20100064997A1 (en) 2010-03-18

Family

ID=38819626

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/441,841 Abandoned US20100064997A1 (en) 2006-09-19 2007-09-18 Continuous camshaft phase shifting apparatus

Country Status (5)

Country Link
US (1) US20100064997A1 (fr)
EP (1) EP2064417A1 (fr)
JP (1) JP2010504470A (fr)
KR (1) KR20090074161A (fr)
WO (1) WO2008036650A1 (fr)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8562471B2 (en) 2011-04-14 2013-10-22 GM Global Technology Operations LLC Electric motor assembly with movable rotor segments to reduce back electromotive force
US9077227B2 (en) 2012-01-20 2015-07-07 GM Global Technology Operations LLC Electric motor assembly with electric phasing of rotor segments to reduce back electromotive force
WO2015200190A1 (fr) * 2014-06-25 2015-12-30 Borgwarner Inc. Systèmes de dispositif de mise en phase d'arbre à cames et dispositifs de mise en phase de verrouillage pour ces derniers
US10180088B2 (en) 2015-05-29 2019-01-15 Borgwarner Inc. Tapered roller drive for electric VCT phaser
US20190078473A1 (en) * 2017-09-08 2019-03-14 Borgwarner Inc. Electric phaser with orbiting eccentric gears
US10247055B2 (en) 2017-01-13 2019-04-02 Schaeffler Technologies AG & Co. KG Cam phaser having a retention feature for aiding assembly
US10480361B2 (en) 2017-01-13 2019-11-19 Schaeffler Technologies AG & Co. KG Cam phaser having a retention feature for aiding assembly
US10514068B2 (en) 2017-07-31 2019-12-24 Borgwarner, Inc. EPhaser cushion stop
US10544715B1 (en) 2018-09-10 2020-01-28 Schaeffler Technologies AG & Co. KG Cam phaser assembly
CN114076028A (zh) * 2020-08-17 2022-02-22 胡斯可汽车控股有限公司 用于可变压缩比定相器的系统和方法
US20220195898A1 (en) * 2019-05-03 2022-06-23 Husco Automotive Holdings Llc Systems and Methods for Controlled Relative Rotational Motion

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102317584A (zh) * 2008-12-11 2012-01-11 美国光洋轴承有限责任公司 紧凑的电动凸轮相位器
US20110073053A1 (en) 2009-09-30 2011-03-31 Koyo Bearings Usa Llc Method for cam-shaft phase shifting control using cam reaction force
DE102017111223B3 (de) * 2017-05-23 2018-09-13 Schaeffler Technologies AG & Co. KG Nockenwellenversteller

Citations (15)

* 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
US4561390A (en) * 1982-11-12 1985-12-31 Toyota Jidosha Kabushiki Kaisha Variable valve-timing apparatus in an internal combustion engine
US4722315A (en) * 1984-10-11 1988-02-02 M.A.N. Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Method for improved internal exhaust gas recirculation in an internal combustion engine
US5174253A (en) * 1991-01-11 1992-12-29 Toyota Jidosha Kabushiki Kaisha Apparatus for shifting phase between shafts in internal combustion engine
US5327859A (en) * 1993-06-09 1994-07-12 General Motors Corporation Engine timing drive with fixed and variable phasing
US5361736A (en) * 1990-07-13 1994-11-08 Lancelot Phoenix Variable valve timing
US5680836A (en) * 1996-09-17 1997-10-28 General Motors Corporation Planetary cam phaser with lash compensation
US6129061A (en) * 1997-11-21 2000-10-10 Mazda Motor Corporation Apparatus for controlling rotational phase
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
US6328008B1 (en) * 1999-08-03 2001-12-11 Unisia Jecs Corporation Valve timing control system for internal combustion engine
US6502537B2 (en) * 2001-01-31 2003-01-07 Unisia Jecs Corporation Valve timing control device of internal combustion engine
US6622677B2 (en) * 2002-02-22 2003-09-23 Borgwarner Inc. Worm gear driven variable cam phaser
US6675754B2 (en) * 2001-10-12 2004-01-13 Hitachi Unisia Automotive, Ltd. Valve timing control apparatus
US6948464B2 (en) * 2003-03-06 2005-09-27 Denso Corporation Protection method for an engine having a variable valve timing controller and protection apparatus for the same
US7100556B2 (en) * 2005-01-26 2006-09-05 Denso Corporation Variable valve timing controller

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4110195C2 (de) * 1991-03-28 2000-02-10 Schaeffler Waelzlager Ohg Verstellvorrichtung für eine Nockenwelle
DE102004023548A1 (de) * 2004-05-13 2005-12-08 Daimlerchrysler Ag Verstelleinrichtung einer Nockenwelle, Vorrichtung für eine Verstelleinrichtung sowie Verfahren zum Betreiben einer Verstelleinrichtung
DE102004033522A1 (de) * 2004-07-10 2006-02-09 Ina-Schaeffler Kg Nockenwellenversteller mit elektrischem Antrieb

Patent Citations (15)

* 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
US4561390A (en) * 1982-11-12 1985-12-31 Toyota Jidosha Kabushiki Kaisha Variable valve-timing apparatus in an internal combustion engine
US4722315A (en) * 1984-10-11 1988-02-02 M.A.N. Maschinenfabrik Augsburg-Nurnberg Aktiengesellschaft Method for improved internal exhaust gas recirculation in an internal combustion engine
US5361736A (en) * 1990-07-13 1994-11-08 Lancelot Phoenix Variable valve timing
US5174253A (en) * 1991-01-11 1992-12-29 Toyota Jidosha Kabushiki Kaisha Apparatus for shifting phase between shafts in internal combustion engine
US5327859A (en) * 1993-06-09 1994-07-12 General Motors Corporation Engine timing drive with fixed and variable phasing
US5680836A (en) * 1996-09-17 1997-10-28 General Motors Corporation Planetary cam phaser with lash compensation
US6129061A (en) * 1997-11-21 2000-10-10 Mazda Motor Corporation Apparatus for controlling rotational phase
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
US6328008B1 (en) * 1999-08-03 2001-12-11 Unisia Jecs Corporation Valve timing control system for internal combustion engine
US6502537B2 (en) * 2001-01-31 2003-01-07 Unisia Jecs Corporation Valve timing control device of internal combustion engine
US6675754B2 (en) * 2001-10-12 2004-01-13 Hitachi Unisia Automotive, Ltd. Valve timing control apparatus
US6622677B2 (en) * 2002-02-22 2003-09-23 Borgwarner Inc. Worm gear driven variable cam phaser
US6948464B2 (en) * 2003-03-06 2005-09-27 Denso Corporation Protection method for an engine having a variable valve timing controller and protection apparatus for the same
US7100556B2 (en) * 2005-01-26 2006-09-05 Denso Corporation Variable valve timing controller

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8562471B2 (en) 2011-04-14 2013-10-22 GM Global Technology Operations LLC Electric motor assembly with movable rotor segments to reduce back electromotive force
US9077227B2 (en) 2012-01-20 2015-07-07 GM Global Technology Operations LLC Electric motor assembly with electric phasing of rotor segments to reduce back electromotive force
WO2015200190A1 (fr) * 2014-06-25 2015-12-30 Borgwarner Inc. Systèmes de dispositif de mise en phase d'arbre à cames et dispositifs de mise en phase de verrouillage pour ces derniers
US9771839B2 (en) 2014-06-25 2017-09-26 Borgwarner Inc. Camshaft phaser systems and locking phasers for the same
DE112015002518B4 (de) * 2014-06-25 2017-11-16 Borgwarner Inc. Nockenwellenverstellersysteme und zugehörige Versteller mit Verriegelung
US10180088B2 (en) 2015-05-29 2019-01-15 Borgwarner Inc. Tapered roller drive for electric VCT phaser
US10480361B2 (en) 2017-01-13 2019-11-19 Schaeffler Technologies AG & Co. KG Cam phaser having a retention feature for aiding assembly
US10247055B2 (en) 2017-01-13 2019-04-02 Schaeffler Technologies AG & Co. KG Cam phaser having a retention feature for aiding assembly
US10514068B2 (en) 2017-07-31 2019-12-24 Borgwarner, Inc. EPhaser cushion stop
US20190078473A1 (en) * 2017-09-08 2019-03-14 Borgwarner Inc. Electric phaser with orbiting eccentric gears
US10544715B1 (en) 2018-09-10 2020-01-28 Schaeffler Technologies AG & Co. KG Cam phaser assembly
CN112513432A (zh) * 2018-09-10 2021-03-16 舍弗勒技术股份两合公司 凸轮相位器总成
US20220195898A1 (en) * 2019-05-03 2022-06-23 Husco Automotive Holdings Llc Systems and Methods for Controlled Relative Rotational Motion
US11821342B2 (en) * 2019-05-03 2023-11-21 Husco Automotive Holdings Llc Systems and methods for controlled relative rotational motion
CN114076028A (zh) * 2020-08-17 2022-02-22 胡斯可汽车控股有限公司 用于可变压缩比定相器的系统和方法

Also Published As

Publication number Publication date
WO2008036650A1 (fr) 2008-03-27
EP2064417A1 (fr) 2009-06-03
JP2010504470A (ja) 2010-02-12
WO2008036650A8 (fr) 2008-05-02
KR20090074161A (ko) 2009-07-06

Similar Documents

Publication Publication Date Title
US20100064997A1 (en) Continuous camshaft phase shifting apparatus
US9664254B2 (en) Split ring carrier with eccentric pin with spring compliance and speed dependence
US8800513B2 (en) Axially compact coupling for a camshaft phaser actuated by electric motor
RU2699515C1 (ru) Устройство передачи мощности
US11815169B2 (en) Transmission, drive train and vehicle having a transmission
US8327815B2 (en) Adjustable camshaft with a planetary gear
KR20150144770A (ko) 무단 변속기
FR2508973A1 (fr) Prise de couple auxiliaire sur moteur thermique a explosion ou a combustion interne
EP0596001A1 (fr) Structure a poussee d'extremite pour un differentiel a axes paralleles.
JP4735504B2 (ja) バルブタイミング調整装置
CN101163908B (zh) 带式无级变速器
JP2009162268A (ja) シフトレンジ切替装置
JPH11153008A (ja) 回転位相制御装置
EP2373875A1 (fr) Dispositif de mise en phase de came électrique compact
US20020053327A1 (en) Electrically driven device for angular adjustment of a shaft relative to its drive
JP4584171B2 (ja) 動力伝達装置およびその組立方法
WO2009049001A1 (fr) Dispositif de déphasage non synchrone d'arbre à cames entraîné par courroie
JP2020070880A (ja) 車両用駆動伝達装置
US7458351B2 (en) Valve timing controller
JPH07279632A (ja) 内燃機関のカム軸位相可変装置
CN101270680B (zh) 相位调节装置
JP4200728B2 (ja) トロイダル型無段変速機及び無段変速装置
JP2004346938A (ja) クランクシャフトとカムシャフトとの間の相対回転位置を制御調整するための装置
US20080163836A1 (en) Camshaft phaser having dual counter-threaded helical mechanisms
US11965437B2 (en) Electric actuator

Legal Events

Date Code Title Description
AS Assignment

Owner name: THE TIMKEN COMPANY,OHIO

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:AI, XIAOLAN, MR.;REEL/FRAME:022425/0392

Effective date: 20060929

AS Assignment

Owner name: KOYO BEARINGS USA LLC,OHIO

Free format text: PATENT ASSIGNMENT AGREEMENT;ASSIGNOR:THE TIMKEN COMPANY;REEL/FRAME:023812/0223

Effective date: 20091231

Owner name: KOYO BEARINGS USA LLC, OHIO

Free format text: PATENT ASSIGNMENT AGREEMENT;ASSIGNOR:THE TIMKEN COMPANY;REEL/FRAME:023812/0223

Effective date: 20091231

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO PAY ISSUE FEE