US20150315939A1 - Split ring gear planetary cam phaser - Google Patents

Split ring gear planetary cam phaser Download PDF

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Publication number
US20150315939A1
US20150315939A1 US14/649,982 US201314649982A US2015315939A1 US 20150315939 A1 US20150315939 A1 US 20150315939A1 US 201314649982 A US201314649982 A US 201314649982A US 2015315939 A1 US2015315939 A1 US 2015315939A1
Authority
US
United States
Prior art keywords
ring gear
side ring
gear
drive
planetary gears
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
US14/649,982
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English (en)
Inventor
Dan J. Showalter
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.)
BorgWarner Inc
Original Assignee
BorgWarner Inc
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 BorgWarner Inc filed Critical BorgWarner Inc
Priority to US14/649,982 priority Critical patent/US20150315939A1/en
Publication of US20150315939A1 publication Critical patent/US20150315939A1/en
Assigned to BORGWARNER INC. reassignment BORGWARNER INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: SHOWALTER, DAN J.
Abandoned 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
    • F01L1/352—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 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 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.
  • FIG. 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 engagement between the sun gear and the split ring gear; and
  • FIG. 2 is a cross sectional view of the cam phaser of FIG. 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 16 a, 16 b, 16 c, and a split ring gear 18 defined by two ring gears (i.e. a drive-side ring gear 18 a and an output-side ring gear 18 b ).
  • Each of the two ring gears 18 a, 18 b 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 16 a, 16 b, 16 c in the planetary gearset 12 .
  • the gear teeth of the two ring gears 18 a, 18 b can have modified profiles to allow the ring gears 18 a, 18 b to mesh properly with the planetary gears 16 a, 16 b , 16 c.
  • the planetary gears 16 a, 16 b, 16 c can be maintained in a fixed relationship to each other by a planetary carrier 20 a, 20 b.
  • An engine crankshaft (not shown) can be rotationally engaged through a timing chain (not shown) to one of the two ring gears 18 a through a sprocket 22 , and the engine camshaft 24 can be rotationally engaged to the other of the two ring gears 18 b.
  • An electric motor 26 can be rotationally engaged with the sun gear 14 of the planetary gearset 12 .
  • the sun gear 14 can be rotated by the electric motor 26 at the same speed as either of the ring gears 18 a, 18 b, since both ring gears 18 a, 18 b rotate in unison, to maintain a constant cam phase position.
  • the sun gear 14 is driven at a different speed from the ring gears 18 a, 18 b by the electric motor 26 , a slightly different speed of one ring gear to the other ring gear causes a cam phase shift function. In this way a very high numerical ratio can be obtained and the camshaft can be phased either plus or minus from the nominal rotational relationship of the crankshaft to the camshaft 24 .
  • 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 frictional 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 16 a, 16 b, 16 c, which can be in a driving meshing relationship with the sun gear 14 . There can be two separate ring gears 18 a, 18 b concentric with the sun gear 14 .
  • the sprocket 22 can have the ring gear teeth of the drive-side ring gear 18 a formed on an inner diameter and can be piloted radially by the output-side ring gear 18 b.
  • the number of teeth on the drive-side ring gear 18 a can be either greater or less than the number of teeth on the output-side ring gear 18 b, where the difference in number of teeth is a multiple of the number of planetary gears 16 a, 16 b, 16 c. In this way, there is tooth alignment at the engagement position of each of the three planetary gears 16 a, 16 b, 16 c.
  • the drive-side ring gear 18 a can have seventy (70) internal teeth and the output-side ring gear 18 b 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 16 a, 16 b, 16 c 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 18 a is held stationary, the sun gear 14 can turn 57.55 times to cause one revolution of the output-side ring gear 18 b .
  • 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 18 b 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 18 b 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 18 a to the output-side ring gear 18 b 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 FIGS. 1-2 ) can be provided to axially locate sprocket 22 and the connected drive-side ring gear 18 a.
  • the three planetary gears 16 a, 16 b, 16 c can be circumferentially and radially located in position by the two carrier halves 20 a, 20 b, which by way of example and not limitation, can be secured to each other by three bolts 30 a , 30 b, 30 c . It is believed that the planetary gears 16 a, 16 b, 16 c 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.
  • the planetary gears 16 a, 16 b, 16 c can be axially located by being interposed between two spaced apart end plates, similar to the illustrated end plate 28 , if the carrier halves 20 a, 20 b are not present. Since all of the gears 14 , 16 a, 16 b, 16 c, 18 a, 18 b only rotate relative to each other during the phasing of the camshaft, noise should not be a problem.
  • the gears 14 , 16 a, 16 b, 16 c, 18 a, 18 b can all be spur gears which produce no axial loading components.
  • An indexing electric motor 26 can be attached to the device housing (not shown) with an output shaft 38 of the electric motor 26 secured to the sun gear 14 . As long as the motor 26 runs at the same speed as the sprocket 22 cam phasing does not occur. Increasing or decreasing the speed of the motor 26 will cause the indexing or phasing function of the planetary gearset 12 .
  • 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)
US14/649,982 2012-12-10 2013-11-21 Split ring gear planetary cam phaser Abandoned US20150315939A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US14/649,982 US20150315939A1 (en) 2012-12-10 2013-11-21 Split ring gear planetary cam phaser

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US201261735513P 2012-12-10 2012-12-10
US14/649,982 US20150315939A1 (en) 2012-12-10 2013-11-21 Split ring gear planetary cam phaser
PCT/US2013/071202 WO2014092963A1 (fr) 2012-12-10 2013-11-21 Dispositif de mise en phase de came planétaire à couronne fendue

Publications (1)

Publication Number Publication Date
US20150315939A1 true US20150315939A1 (en) 2015-11-05

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ID=50934818

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/649,982 Abandoned US20150315939A1 (en) 2012-12-10 2013-11-21 Split ring gear planetary cam phaser

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)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9810109B2 (en) 2014-09-17 2017-11-07 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set
US9810108B2 (en) * 2014-09-04 2017-11-07 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear assembly
US20190010837A1 (en) * 2017-02-28 2019-01-10 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear assembly
US10190450B2 (en) * 2016-12-14 2019-01-29 GM Global Technology Operations LLC Camshaft deactivation system for an internal combustion engine
US10352419B2 (en) 2016-06-30 2019-07-16 Borgwarner Inc. Carrier stop for split ring planetary drive
US10408096B2 (en) 2017-03-16 2019-09-10 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set
US20190301313A1 (en) * 2016-05-27 2019-10-03 Sonceboz Automotive Sa Electric camshaft phase-shifter with single shaft
DE102019131704A1 (de) 2018-11-26 2020-05-28 Borgwarner Inc. Steuergerät für elektrisch-betätigte nockenwellenverstellvorrichtung
US20240039352A1 (en) * 2022-07-26 2024-02-01 Borgwarner Inc. Bonded rotor plate
US11940030B1 (en) * 2022-10-24 2024-03-26 Borgwarner Inc. Torque-limiting torsion gimbal

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9771839B2 (en) 2014-06-25 2017-09-26 Borgwarner Inc. Camshaft phaser systems and locking phasers for the same
JP5987868B2 (ja) * 2014-07-22 2016-09-07 株式会社デンソー バルブタイミング調整装置
JP2016211541A (ja) 2015-05-05 2016-12-15 ボーグワーナー インコーポレーテッド ｅフェイザー用の軸外負荷バックラッシュ防止遊星駆動
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
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
JP6874983B2 (ja) * 2016-06-24 2021-05-19 株式会社Ｓｏｋｅｎ 減速装置
DE102017120810A1 (de) 2016-09-13 2018-03-15 Borgwarner Inc. Nachgiebiger planetenradträger
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

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AT409030B (de) * 2000-03-09 2002-05-27 Tcg Unitech Ag Vorrichtung zur verstellung einer nockenwelle
US7089897B2 (en) * 2002-07-11 2006-08-15 Ina-Schaeffler Kg Electrically driven camshaft adjuster
DE10315151A1 (de) * 2003-04-03 2004-10-14 Daimlerchrysler Ag Vorrichtung zur relativen Winkelverstellung einer Nockenwelle gegenüber dem antreibenden Antriebsrad
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
DE102004009128A1 (de) * 2004-02-25 2005-09-15 Ina-Schaeffler Kg Elektrischer Nockenwellenversteller
DE102005018956A1 (de) * 2005-04-23 2006-11-23 Schaeffler Kg Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
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 (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9810108B2 (en) * 2014-09-04 2017-11-07 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear assembly
US9810109B2 (en) 2014-09-17 2017-11-07 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set
US20190301313A1 (en) * 2016-05-27 2019-10-03 Sonceboz Automotive Sa Electric camshaft phase-shifter with single shaft
US10352419B2 (en) 2016-06-30 2019-07-16 Borgwarner Inc. Carrier stop for split ring planetary drive
US10190450B2 (en) * 2016-12-14 2019-01-29 GM Global Technology Operations LLC Camshaft deactivation system for an internal combustion engine
US20190010837A1 (en) * 2017-02-28 2019-01-10 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear assembly
US10557385B2 (en) * 2017-02-28 2020-02-11 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear assembly
US10408096B2 (en) 2017-03-16 2019-09-10 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set
DE102019131704A1 (de) 2018-11-26 2020-05-28 Borgwarner Inc. Steuergerät für elektrisch-betätigte nockenwellenverstellvorrichtung
US20240039352A1 (en) * 2022-07-26 2024-02-01 Borgwarner Inc. Bonded rotor plate
DE102023119163A1 (de) 2022-07-26 2024-02-01 Borgwarner Inc. Geklebte rotorplatte
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

Also Published As

Publication number Publication date
JP2015537158A (ja) 2015-12-24
CN104822909A (zh) 2015-08-05
DE112013005415T5 (de) 2015-07-30
WO2014092963A1 (fr) 2014-06-19

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Legal Events

Date Code Title Description
AS Assignment

Owner name: BORGWARNER INC., MICHIGAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:SHOWALTER, DAN J.;REEL/FRAME:037757/0568

Effective date: 20121206

STCB Information on status: application discontinuation

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