WO2014092963A1 - Dispositif de mise en phase de came planétaire à couronne fendue - Google Patents
Dispositif de mise en phase de came planétaire à couronne fendue Download PDFInfo
- Publication number
- WO2014092963A1 WO2014092963A1 PCT/US2013/071202 US2013071202W WO2014092963A1 WO 2014092963 A1 WO2014092963 A1 WO 2014092963A1 US 2013071202 W US2013071202 W US 2013071202W WO 2014092963 A1 WO2014092963 A1 WO 2014092963A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- ring gear
- side ring
- gear
- drive
- planetary gears
- Prior art date
Links
- RDYMFSUJUZBWLH-UHFFFAOYSA-N endosulfan Chemical compound C12COS(=O)OCC2C2(Cl)C(Cl)=C(Cl)C1(Cl)C2(Cl)Cl RDYMFSUJUZBWLH-UHFFFAOYSA-N 0.000 title claims abstract description 34
- 238000002485 combustion reaction Methods 0.000 claims abstract description 8
- 230000005540 biological transmission Effects 0.000 claims abstract description 7
- 238000000034 method Methods 0.000 claims description 5
- 239000000446 fuel Substances 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 230000010363 phase shift Effects 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 230000000979 retarding effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
- Y10T29/00—Metal working
- Y10T29/49—Method of mechanical manufacture
- Y10T29/49462—Gear making
- Y10T29/49467—Gear shaping
Definitions
- the invention relates to a planetary gear assembly for dynamically adjusting a phase angle or rotational relationship of a camshaft with respect to an engine crankshaft to improve fuel efficiency of an internal combustion engine.
- a cam phaser for dynamically adjusting a rotational relationship of a camshaft of an internal combustion engine with respect to an engine crank shaft.
- the cam phaser can include a planetary gear system having a drive-side ring gear driven by the engine crank shaft through sprocket and an endless loop power transmission member, a number of planetary gears, and a centrally located sun gear.
- the cam phaser further includes an output-side ring gear concentric with the sun gear and connected to the camshaft.
- the output-side ring gear can have a different number of teeth (greater or lesser) than compared with the drive-side ring gear by a value corresponding to a multiple of the number of planetary gears to provide tooth alignment at an engagement position of each of the planetary gears.
- the drive-side ring gear can be piloted radially by the output-side ring gear.
- An electric motor can be connected to the sun gear for driving the sun gear in relation to the planetary gears.
- the electric motor can rotate at a speed equal to the drive-side ring gear to maintain a constant phase position, and variance of the electric motor speed from an equal value can cause a cam phase change function to occur.
- the drive-side ring gear, the output-side ring gear, the number of planetary gears, and the sun gear define an epicyclic gear drive connection having a high numerical gear ratio allowing accurate phasing angle adjustment with a relatively low driving torque requirement for the electric motor.
- the drive-side ring gear and output-side ring gear define a split ring gear.
- the planetary gears can be supported by first and second carrier plates axially piloted by the drive-side ring gear and the output-side ring gear for securing the number of planetary gears in an axial direction.
- a cam phaser for dynamically adjusting a rotational relationship of a camshaft of an internal combustion engine with respect to an engine crank shaft can include a planetary gear system having a split ring gear including a drive-side ring gear to be driven by the engine crank shaft through a sprocket and an endless loop power transmission member and an output-side ring gear connectable for rotation with the camshaft.
- the planetary gear system can have a sun gear located concentric with the split ring gear, and a number of planetary gears in meshing engagement between the sun gear and the split ring gear.
- the output-side ring gear can have a different number of teeth (greater or lesser) than compared with the drive-side ring gear by a value corresponding to a multiple of the number of planetary gears to provide tooth alignment at an engagement position of each of the planetary gears.
- the drive-side ring gear piloted radially by the output-side ring gear.
- An electric motor can be connected to the sun gear for driving the sun gear in relation to the planetary gears. The electric motor can rotate at a speed equal to the drive-side ring gear to maintain a constant phase position, wherein variance of the electric motor speed from an equal value can cause a cam phase change function to occur.
- the drive-side ring gear, the output-side ring gear, the number of planetary gears, and the sun gear define an epicyclic gear drive connection having a high numerical gear ratio allowing accurate phasing angle adjustment with a relatively low driving torque requirement of the electric motor.
- the planetary gears can be supported by first and second carrier plates axially piloted by the drive-side ring gear and the output-side ring gear for securing the number of planetary gears in an axial direction.
- a method for assembling and dynamically adjusting a rotational relationship of a camshaft of an internal combustion engine with respect to an engine 5 crank shaft can include assembling a planetary gear system having a split ring gear including a drive-side ring gear to be driven by the engine crank shaft through a sprocket engaging an endless loop power transmission member and an output-side ring gear connectable for rotation with the camshaft, locating a sun gear of the planetary gear system concentric with the split ring gear, engaging a number of o planetary gear in meshing engagement between the sun gear and the split ring gear, and providing the output-side ring gear with a different number of teeth (greater or lesser) than compared with the drive-side ring gear by a value corresponding to a multiple of the number of planetary gears to provide tooth alignment at an engagement position of each of the planetary gears.
- the planetary gear system assembly can be rotated as a unit with the sprocket to minimize frictional losses.
- An electric motor connected to the sun gear can be driven at the same speed as the drive-side ring gear to maintain a constant phase position, or can be driven at a speed not equal to the drive-side ring gear to cause a phase change function.
- Figure 1 is a perspective view of a cam phaser with one end plate removed showing an internally located planetary gear set having a split ring gear, a concentrically located sun gear and a number of planetary gears in meshing
- Figure 2 is a cross sectional view of the cam phaser of Figure 1, where the output-side ring gear has a different number of teeth (greater or lesser) than compared with the drive-side ring gear by a value corresponding to a multiple of the number of planetary gears to provide tooth alignment at an engagement position of each of the planetary gears.
- the cam phaser 10 can include a planetary gearset 12 with a centrally located sun gear 14, a number of identical planetary gears 16a, 16b, 16c, and a split ring gear 18 defined by two ring gears (i.e. a drive-side ring gear 18a and an output- side ring gear 18b).
- Each of the two ring gears 18a, 18b has a different number of teeth with respect to the other ring gear, where the difference in the number of teeth equals a multiple of the number of planetary gears 16a, 16b, 16c in the planetary gearset 12.
- the gear teeth of the two ring gears 18a, 18b can have modified profiles to allow the ring gears 18a, 18b to mesh properly with the planetary gears 16a, 16b, 16c.
- the planetary gears 16a, 16b, 16c can be maintained in a fixed relationship to each other by a planetary carrier 20a, 20b.
- An engine crankshaft (not shown) can be rotationally engaged through a timing chain (not shown) to one of the two ring gears 18a through a sprocket 22, and the engine camshaft 24 can be rotationally engaged to the other of the two ring gears 18b.
- An electric motor 26 can be rotationally engaged with the sun gear 14 of the planetary gearset 12.
- the cam phaser 10 can be used for dynamically adjusting the rotational relationship of the camshaft 24 to the engine crankshaft to improve the fuel efficiency of the engine.
- the cam phaser 10 achieves this cam phasing function with lower factional losses and at a lower overall cost than previously known devices.
- the adjustment of the cam phasing angle is done with the planetary gearset 12, which provides a high numerical ratio (by way of example and not limitation, such as approximately 57: 1 in the illustrated configuration), so that the cam phasing angle can be adjusted accurately with a relatively low driving torque of the adjusting electric motor 26.
- the entire cam phaser 10 assembly rotates as a unit which minimizes frictional losses.
- the adjusting electric motor 26 can be driven at the same speed as the camshaft to maintain a constant cam phase position.
- the adjusting electric motor 26 can be driven at a speed not equal to the rotational speed of the split ring gear 18 to cause a cam phase shift function to occur in either the advancing or retarding directions.
- the timing chain which is driven by the engine crankshaft can be engaged with teeth of a sprocket 22.
- the number of teeth on the engine crank sprocket can be nineteen (19) and the number of teeth on sprocket 22 can be thirty- eight (38), which yields a ratio such that the sprocket 22 can be driven at half the speed of the engine crank.
- the planetary gearset 12 assembly as illustrated can have a single sun gear 14, and three planetary gears 16a, 16b, 16c, which can be in a driving meshing relationship with the sun gear 14. There can be two separate ring gears 18a, 18b concentric with the sun gear 14.
- the sprocket 22 can have the ring gear teeth of the drive-side ring gear 18a formed on an inner diameter and can be piloted radially by the output-side ring gear 18b.
- the number of teeth on the drive- side ring gear 18a can be either greater or less than the number of teeth on the output- side ring gear 18b, where the difference in number of teeth is a multiple of the number of planetary gears 16a, 16b, 16c. In this way, there is tooth alignment at the engagement position of each of the three planetary gears 16a, 16b, 16c.
- the drive-side ring gear 18a can have seventy (70) internal teeth and the output-side ring gear 18b can have sixty-seven (67) teeth.
- the sun gear can have twenty-six (26) teeth in the illustrated and described configuration, while each of the planetary gears 16a, 16b, 16c can have twenty-one (21) teeth. This arrangement results in a very high gear ratio of one ring gear to the other ring gear. If the drive-side ring gear 18a is held stationary, the sun gear 14 can turn 57.55 times to cause one revolution of the output- side ring gear 18b.
- one degree of cam phase change can require almost sixty (60) degrees of relative rotation of the sun gear 14 to the sprocket 22. It should be recognized by those skilled in the art that different gear ratios can be achievable with the disclosed invention and therefore the invention is not limited to the specific configuration illustrated and discussed herein.
- the output- side ring gear 18b can be rotationally secured to an end plate 28 which can be secured, by way of example and not limitation, by a bolt 36 to the camshaft 24.
- the output-side ring gear 18b and the end plate 28 can be joined to one another and act as one with the camshaft 24 which can be securely piloted for rotation to the engine block without needing additional piloting features.
- the relative speed of sprocket 22 and connected drive-side ring gear 18a to the output-side ring gear 18b is low and a simple steel-on-steel or bushing is sufficient to properly radially locate the parts relative to one another.
- Another end plate (not shown in Figures 1-2) can be provided to axially locate sprocket 22 and the connected drive-side ring gear 18a.
- the three planetary gears 16a, 16b, 16c can be circumferentially and radially located in position by the two carrier halves 20a, 20b, which by way of example and not limitation, can be secured to each other by three bolts 30a , 30b, 30c. It is believed that the planetary gears 16a, 16b, 16c can be located radially and circumferentially by the intermeshing gear teeth, which would further reduce the cost of the assembly by eliminating the two carrier halves. It is further believed that the planetary gears 16a, 16b, 16c can be axially located by being interposed between two spaced apart end plates, similar to the illustrated end plate 28, if the carrier halves 20a, 20b are not present.
- gears 14, 16a, 16b, 16c, 18a, 18b only rotate relative to each other during the phasing of the camshaft, noise should not be a problem.
- the gears 14, 16a, 16b, 16c, 18a, 18b can all be spur gears which produce no axial loading components.
- An indexing electric motor 26 can be attached to the device housing
- a sensor 32 can be used as feedback to a motor controller 34 to measure a current position of the sprocket 22 to the camshaft 24 to determine what adjustment, if any, is desired at any point in time to achieve optimal engine efficiency.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2015546500A JP2015537158A (ja) | 2012-12-10 | 2013-11-21 | スプリットリングギヤ遊星カム位相器 |
DE112013005415.9T DE112013005415T5 (de) | 2012-12-10 | 2013-11-21 | Planeten-Nockenwellenverstellsystem mit geteiltem Hohlrad |
CN201380062453.0A CN104822909A (zh) | 2012-12-10 | 2013-11-21 | 分离的环齿轮行星式凸轮相位器 |
US14/649,982 US20150315939A1 (en) | 2012-12-10 | 2013-11-21 | Split ring gear planetary cam phaser |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US201261735513P | 2012-12-10 | 2012-12-10 | |
US61/735,513 | 2012-12-10 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014092963A1 true WO2014092963A1 (fr) | 2014-06-19 |
Family
ID=50934818
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/US2013/071202 WO2014092963A1 (fr) | 2012-12-10 | 2013-11-21 | Dispositif de mise en phase de came planétaire à couronne fendue |
Country Status (5)
Country | Link |
---|---|
US (1) | US20150315939A1 (fr) |
JP (1) | JP2015537158A (fr) |
CN (1) | CN104822909A (fr) |
DE (1) | DE112013005415T5 (fr) |
WO (1) | WO2014092963A1 (fr) |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
CN105275524A (zh) * | 2014-07-22 | 2016-01-27 | 株式会社电装 | 阀定时控制设备 |
WO2016044044A1 (fr) * | 2014-09-17 | 2016-03-24 | Borgwarner Inc. | Déphaseur d'arbre à cames variable de moteur à train planétaire |
DE102016206623A1 (de) | 2015-05-05 | 2016-11-10 | Borgwarner Inc. | Axial versetzt vorgespannter spielfreier planetenantrieb für e-phasenverschiebungsvorrichtung |
DE102016209023A1 (de) | 2015-05-29 | 2016-12-01 | Borg Warner Inc. | Federbelastete Planetenanordnung |
DE102016209191A1 (de) | 2015-05-29 | 2016-12-01 | Borgwarner Inc. | Elastisch nachgiebiger und drehzahlabhängiger geteilter Hohlradträger mit Exzenterstift |
WO2017019585A1 (fr) * | 2015-07-30 | 2017-02-02 | Borgwarner Inc. | Butée de déplacement pour engrenages planétaires d'un dispositif de mise en phase électrique |
WO2017202971A1 (fr) * | 2016-05-27 | 2017-11-30 | Sonceboz Automotive Sa | Dephaseur d'arbre a cames electrique a arbre unique |
DE102017120810A1 (de) | 2016-09-13 | 2018-03-15 | Borgwarner Inc. | Nachgiebiger planetenradträger |
US10408096B2 (en) | 2017-03-16 | 2019-09-10 | Borgwarner Inc. | Engine variable camshaft timing phaser with planetary gear set |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2016036529A1 (fr) * | 2014-09-04 | 2016-03-10 | Borgwarner Inc. | Déphaseur d'arbre à cames variable de moteur avec ensemble d'engrenage planétaire |
JP6874983B2 (ja) * | 2016-06-24 | 2021-05-19 | 株式会社Soken | 減速装置 |
CN107559410B (zh) | 2016-06-30 | 2022-02-18 | 博格华纳公司 | 用于裂环行星传动的行星架止动件 |
US10190450B2 (en) * | 2016-12-14 | 2019-01-29 | GM Global Technology Operations LLC | Camshaft deactivation system for an internal combustion engine |
US10557385B2 (en) * | 2017-02-28 | 2020-02-11 | Borgwarner Inc. | Engine variable camshaft timing phaser with planetary gear assembly |
JP2019027435A (ja) * | 2017-07-31 | 2019-02-21 | ボーグワーナー インコーポレーテッド | e−位相器クッション止め部 |
CN111219223A (zh) | 2018-11-26 | 2020-06-02 | 博格华纳公司 | 电致动可变凸轮轴正时设备控制器 |
US11942829B2 (en) | 2022-07-26 | 2024-03-26 | Borgwarner Inc. | Bonded rotor plate |
US11940030B1 (en) * | 2022-10-24 | 2024-03-26 | Borgwarner Inc. | Torque-limiting torsion gimbal |
Citations (5)
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US20040206322A1 (en) * | 2003-04-03 | 2004-10-21 | Jens Meintschel | Device for the relative angular adjustment of a camshaft with respect to a drive wheel |
US20050103299A1 (en) * | 2002-07-11 | 2005-05-19 | Ina-Schaeffler Kg | Electrically driven camshaft |
US20060236965A1 (en) * | 2005-04-23 | 2006-10-26 | Schaeffler Kg | Camshaft adjustment device for an internal combustion engine |
US20080210182A1 (en) * | 2004-02-25 | 2008-09-04 | Schaeffler Kg | Electric Camshaft Adjuster |
EP2295741A1 (fr) * | 2009-08-31 | 2011-03-16 | Delphi Technologies, Inc. | Dispositif de commande de soupape doté d'un déphaseur à came variable |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AT409030B (de) * | 2000-03-09 | 2002-05-27 | Tcg Unitech Ag | Vorrichtung zur verstellung einer nockenwelle |
WO2005015011A1 (fr) * | 2003-08-12 | 2005-02-17 | Nabtesco Corporation | Reducteur de vitesse destine a etre utilise dans un actionneur de gouverne de lacet pour un appareil de generation de puissance eolienne, procede d'actionnement de gouverne de lacet et appareil pour appareil de generation de puissance eolienne utilisant le reducteur de vitesse |
-
2013
- 2013-11-21 WO PCT/US2013/071202 patent/WO2014092963A1/fr active Application Filing
- 2013-11-21 US US14/649,982 patent/US20150315939A1/en not_active Abandoned
- 2013-11-21 JP JP2015546500A patent/JP2015537158A/ja active Pending
- 2013-11-21 CN CN201380062453.0A patent/CN104822909A/zh active Pending
- 2013-11-21 DE DE112013005415.9T patent/DE112013005415T5/de not_active Withdrawn
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20050103299A1 (en) * | 2002-07-11 | 2005-05-19 | Ina-Schaeffler Kg | Electrically driven camshaft |
US20040206322A1 (en) * | 2003-04-03 | 2004-10-21 | Jens Meintschel | Device for the relative angular adjustment of a camshaft with respect to a drive wheel |
US20080210182A1 (en) * | 2004-02-25 | 2008-09-04 | Schaeffler Kg | Electric Camshaft Adjuster |
US20060236965A1 (en) * | 2005-04-23 | 2006-10-26 | Schaeffler Kg | Camshaft adjustment device for an internal combustion engine |
EP2295741A1 (fr) * | 2009-08-31 | 2011-03-16 | Delphi Technologies, Inc. | Dispositif de commande de soupape doté d'un déphaseur à came variable |
Cited By (26)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN106460588A (zh) * | 2014-06-25 | 2017-02-22 | 博格华纳公司 | 凸轮轴相位器系统以及用于其的锁定相位器 |
CN106460588B (zh) * | 2014-06-25 | 2019-03-01 | 博格华纳公司 | 凸轮轴相位器系统以及用于其的锁定相位器 |
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 |
DE112015002518B4 (de) * | 2014-06-25 | 2017-11-16 | Borgwarner Inc. | Nockenwellenverstellersysteme und zugehörige Versteller mit Verriegelung |
US9771839B2 (en) | 2014-06-25 | 2017-09-26 | Borgwarner Inc. | Camshaft phaser systems and locking phasers for the same |
CN105275524A (zh) * | 2014-07-22 | 2016-01-27 | 株式会社电装 | 阀定时控制设备 |
CN105275524B (zh) * | 2014-07-22 | 2018-12-25 | 株式会社电装 | 阀定时控制设备 |
WO2016044044A1 (fr) * | 2014-09-17 | 2016-03-24 | Borgwarner Inc. | Déphaseur d'arbre à cames variable de moteur à train planétaire |
CN107075983B (zh) * | 2014-09-17 | 2018-12-04 | 博格华纳公司 | 具有行星齿轮组的发动机可变凸轮轴正时相位器 |
US9810109B2 (en) | 2014-09-17 | 2017-11-07 | Borgwarner Inc. | Engine variable camshaft timing phaser with planetary gear set |
CN107075983A (zh) * | 2014-09-17 | 2017-08-18 | 博格华纳公司 | 具有行星齿轮组的发动机可变凸轮轴正时相位器 |
DE102016206623A1 (de) | 2015-05-05 | 2016-11-10 | Borgwarner Inc. | Axial versetzt vorgespannter spielfreier planetenantrieb für e-phasenverschiebungsvorrichtung |
US10233999B2 (en) | 2015-05-05 | 2019-03-19 | Borgwarner, Inc. | Off-axis-loaded anti-backlash planetary drive for e-phaser |
CN106195215A (zh) * | 2015-05-29 | 2016-12-07 | 博格华纳公司 | 具有带有弹簧柔度和速度依赖性的带偏心销的分离式环架 |
US9664254B2 (en) | 2015-05-29 | 2017-05-30 | Borgwarner Inc. | Split ring carrier with eccentric pin with spring compliance and speed dependence |
JP2016223439A (ja) * | 2015-05-29 | 2016-12-28 | ボーグワーナー インコーポレーテッド | ばね荷重遊星ギアアセンブリ |
DE102016209191A1 (de) | 2015-05-29 | 2016-12-01 | Borgwarner Inc. | Elastisch nachgiebiger und drehzahlabhängiger geteilter Hohlradträger mit Exzenterstift |
DE102016209023A1 (de) | 2015-05-29 | 2016-12-01 | Borg Warner Inc. | Federbelastete Planetenanordnung |
US10344825B2 (en) | 2015-05-29 | 2019-07-09 | Borgwarner Inc. | Spring loaded plant gear assembly |
CN107923272A (zh) * | 2015-07-30 | 2018-04-17 | 博格华纳公司 | 用于电动相位器的行星齿轮的行程止动件 |
JP2018523774A (ja) * | 2015-07-30 | 2018-08-23 | ボーグワーナー インコーポレーテッド | 電動位相可変器の遊星ギア用移動止め部 |
WO2017019585A1 (fr) * | 2015-07-30 | 2017-02-02 | Borgwarner Inc. | Butée de déplacement pour engrenages planétaires d'un dispositif de mise en phase électrique |
WO2017202971A1 (fr) * | 2016-05-27 | 2017-11-30 | Sonceboz Automotive Sa | Dephaseur d'arbre a cames electrique a arbre unique |
FR3051835A1 (fr) * | 2016-05-27 | 2017-12-01 | Sonceboz Automotive Sa | Dephaseur d'arbre a cames electrique a arbre unique |
DE102017120810A1 (de) | 2016-09-13 | 2018-03-15 | Borgwarner Inc. | Nachgiebiger planetenradträger |
US10408096B2 (en) | 2017-03-16 | 2019-09-10 | Borgwarner Inc. | Engine variable camshaft timing phaser with planetary gear set |
Also Published As
Publication number | Publication date |
---|---|
JP2015537158A (ja) | 2015-12-24 |
CN104822909A (zh) | 2015-08-05 |
DE112013005415T5 (de) | 2015-07-30 |
US20150315939A1 (en) | 2015-11-05 |
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