WO2014092963A1 - Split ring gear planetary cam phaser - Google Patents

Split ring gear planetary cam phaser Download PDF

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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
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.)
Ceased
Application number
PCT/US2013/071202
Other languages
French (fr)
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
Priority to DE112013005415.9T priority patent/DE112013005415T5/en
Priority to JP2015546500A priority patent/JP2015537158A/en
Priority to CN201380062453.0A priority patent/CN104822909A/en
Publication of WO2014092963A1 publication Critical patent/WO2014092963A1/en
Anticipated expiration legal-status Critical
Ceased 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 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.

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  • 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

A cam phaser (10) for dynamically adjusting a rotational relationship of a camshaft (24) of an internal combustion engine with respect to an engine crank shaft can include a planetary gear system (12) having a split ring gear (18) including a drive-side ring gear (18a) to be driven by the engine crank shaft through an endless loop power transmission member and an output- side ring gear (18b) connectable for rotation with the camshaft (24). A sun gear (14) can be located concentric with the split ring gear (18), and a number of planetary gears (16a, 16b, 16c) can be in meshing engagement between the sun gear (14) and the split ring gear (18). The output- side ring gear (18b) can have a different number of teeth (greater or lesser) than compared with the drive-side ring gear (18a) 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 (16a, 16b, 16c).

Description

SPLIT RING GEAR PLANETARY CAM PHASER
FIELD OF THE INVENTION
[0001] 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.
BACKGROUND
[0002] There are many different devices currently in production to achieve this phasing of the engine camshaft. For example, see U.S. Patent Application Publication No. 2010/0064997; U.S. Patent Application Publication No.
2004/0206322; U.S. Patent No. 7,506,623; U.S. Patent No. 7,047,923; U.S. Patent No. 6,971,352; U.S. Patent No. 6,138,622; U.S. Patent No. 6,129,061; U.S. Patent No. 5,680,836; U.S. Patent No. 5,361,736; U.S. Patent No. 5,327,859; U.S. Patent No. 4,850,427; and German Patent No. DE4110195. While each of these devices appear suitable to perform the intended function, it has been found that the devices have high overall cost and/or high frictional losses. It would desirable to provide a cam phaser with lower frictional losses and at a lower overall cost.
SUMMARY
[0003] A cam phaser is disclosed 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.
[0004] 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.
[0005] 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.
[0006] 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.
[0007] 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.
5 [0008] 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.
o [0009] Other applications of the present invention will become apparent to those skilled in the art when the following description of the best mode contemplated for practicing the invention is read in conjunction with the accompanying drawings.
BRIEF DESCRIPTION OF THE DRAWINGS
[0010] The description herein makes reference to the accompanying drawings 5 wherein like reference numerals refer to like parts throughout the several views, and wherein:
[0011] 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
0 engagement between the sun gear and the split ring gear; and [0012] 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.
DETAILED DESCRIPTION
[0013] Referring now to Figures 1-2, a split ring gear planetary cam phaser 10 is illustrated. 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. When the sun gear 14 can be rotated by the electric motor 26 at the same speed as either of the ring gears 18a, 18b, since both ring gears 18a, 18b rotate in unison, to maintain a constant cam phase position. When the sun gear 14 is driven at a different speed from the ring gears 18a, 18b 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.
[0014] 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.
[0015] When the engine is running and the cam phase is not being adjusted, the entire cam phaser 10 assembly rotates as a unit which minimizes frictional losses. When the engine is running and the cam phase is not being adjusted, the adjusting electric motor 26 can be driven at the same speed as the camshaft to maintain a constant cam phase position. When the engine is running and the cam phase needs to be adjusted, 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.
[0016] The timing chain which is driven by the engine crankshaft can be engaged with teeth of a sprocket 22. By way of example and not limitation, in the illustrated and described configuration, 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.
[0017] By way of example and not limitation, in the illustrated and described configuration, 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. By way of example and not limitation, 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. Therefore, 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.
[0018] 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. In this way 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.
[0019] 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. Since all of the 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.
[0020] 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.
[0021] While the invention has been described in connection with what is presently considered to be the most practical and preferred embodiment, it is to be understood that the invention is not to be limited to the disclosed embodiments but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims, which scope is to be accorded the broadest interpretation so as to encompass all such modifications and equivalent structures as is permitted under the law.

Claims

What is claimed is:
1. In a cam phaser (10) for dynamically adjusting a rotational relationship of a camshaft (24) of an internal combustion engine with respect to an engine crank shaft, the cam phaser (10) including a planetary gear system (12) having a drive-side ring gear (18a) driven by the engine crank shaft through an endless loop power transmission member, a number of planetary gears (16a, 16b, 16c), and a centrally located sun gear (14), the improvement comprising:
an output-side ring gear (18b) concentric with the sun gear (14) and connected to the camshaft (24), the output-side ring gear (18b) having a different number of teeth compared with the drive-side ring gear (18a) by a value
corresponding to a multiple of the number of planetary gears (16a, 16b, 16c) to provide tooth alignment at an engagement position of each of the planetary gears (16a, 16b, 16c).
2. The improvement of claim 1 further comprising:
the drive-side ring gear (18a) piloted radially by the output-side ring gear (18b).
3. The improvement of claim 1 further comprising:
an electric motor (26) connected to the sun gear (14) for driving the sun gear (14) in relation to the planetary gears (16a, 16b, 16c), wherein the electric motor (26) rotates at a speed equal to the drive-side ring gear (18a) to maintain a constant phase position, while variance of the electric motor speed from a value equal to the drive-side ring gear (18a) causes a cam phase change function to occur.
4. The improvement of claim 1, wherein the drive-side ring gear (18a), the output-side ring gear (18b), the number of planetary gears (16a, 16b, 16c), and the sun gear (14) define an epicyclic gear drive connection having a high numerical gear ratio allowing accurate phasing angle adjustment with a relatively low driving torque requirement.
5. The improvement of claim 1 further comprising:
first and second carrier plates (20a, 20b) axially piloted by the drive- side ring gear (18a) and the output-side ring gear (18b) for securing the number of 5 planetary gears (16a, 16b, 16c) in an axial direction.
6. A cam phaser (10) for dynamically adjusting a rotational relationship of a camshaft (24) of an internal combustion engine with respect to an engine crank shaft, the cam phaser (10) comprising:
a planetary gear system (12) having a split ring gear (18) including a drive-side ring gear (18a) to be driven by the engine crank shaft through an endless loop power transmission member and an output- side ring gear (18b) connectable for rotation with the camshaft (24), the planetary gear system (12) having a sun gear (14) located concentric with the split ring gear (18), and a number of planetary gears (16a, 16b, 16c) in meshing engagement between the sun gear (14) and the split ring gear (18).
7. The cam phaser (10) of claim 6 further comprising:
the output-side ring gear (18b) having a different number of teeth o compared with the drive-side ring gear (18a) by a value corresponding to a multiple of the number of planetary gears (16a, 16b, 16c) to provide tooth alignment at an engagement position of each of the planetary gears (16a, 16b, 16c).
8. The cam phaser (10) of claim 6 further comprising:
5 the drive-side ring gear (18a) piloted radially by the output-side ring gear (18b).
9. The cam phaser (10) of claim 6 further comprising:
an electric motor (26) connected to the sun gear (14) for driving the0 sun gear (14) in relation to the planetary gears (16a, 16b, 16c), wherein the electric motor (26) rotates at a speed equal to the split ring gear (18) to maintain a constant phase position and variance of the electric motor speed from an equal value causes a cam phase change function to occur.
10. The cam phaser (10) of claim 6, wherein the drive-side ring gear 5 (18a), the output-side ring gear (18b), the number of planetary gears (16a, 16b, 16c), and the sun gear (14) define an epicyclic gear drive connection having a high numerical gear ratio allowing accurate phasing angle adjustment with a relatively low driving torque requirement. 0
11. The cam phaser (10) of claim 6 further comprising:
first and second carrier plates (20a, 20b) axially piloted by the drive- side ring gear (18a) and the output-side ring gear (18b) for securing the number of planetary gears (16a, 16b, 16c) in an axial direction. 5 12. A method for assembling and dynamically adjusting a rotational relationship of a camshaft (24) of an internal combustion engine with respect to an engine crank shaft comprising:
assembling a planetary gear system (12) having a split ring gear (18) including a drive-side ring gear (18a) to be driven by the engine crank shaft through a o sprocket (22) engaging an endless loop power transmission member and an output- side ring gear (18b) connectable for rotation with the camshaft (24);
locating a sun gear (14) of the planetary gear system
(12) concentric with respect to the split ring gear (18);
engaging a number of planetary gears (16a, 16b, 16c) in meshing 5 engagement between the sun gear (14) and the split ring gear (18); and
providing the output- side ring gear (18b) with a different number of teeth compared with the drive-side ring gear (18a) by a value corresponding to a multiple of the number of planetary gears (16a, 16b, 16c) to provide tooth alignment at an engagement position of each of the planetary gears (16a, 16b, 16c).
0
13. The method of claim 12 further comprising: rotating the planetary gear system (12) assembly as a unit with the sprocket (22) to minimize frictional losses.
14. The method of claim 12 further comprising:
driving an electric motor (26) connected to the sun gear (14) at the same speed as the split ring gear (18) to maintain a constant phase position.
15. The method of claim 12 further comprising:
driving an electric motor (26) connected to the sun gear (14) at a speed not equal to the split ring gear (18) to adjust a phase position.
PCT/US2013/071202 2012-12-10 2013-11-21 Split ring gear planetary cam phaser Ceased WO2014092963A1 (en)

Priority Applications (4)

Application Number Priority Date Filing Date Title
US14/649,982 US20150315939A1 (en) 2012-12-10 2013-11-21 Split ring gear planetary cam phaser
DE112013005415.9T DE112013005415T5 (en) 2012-12-10 2013-11-21 Planetary camshaft phasing system with split ring gear
JP2015546500A JP2015537158A (en) 2012-12-10 2013-11-21 Split ring gear planetary cam phaser
CN201380062453.0A CN104822909A (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

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JP (1) JP2015537158A (en)
CN (1) CN104822909A (en)
DE (1) DE112013005415T5 (en)
WO (1) WO2014092963A1 (en)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015200190A1 (en) * 2014-06-25 2015-12-30 Borgwarner Inc. Camshaft phaser systems and locking phasers for the same
CN105275524A (en) * 2014-07-22 2016-01-27 株式会社电装 Valve timing control apparatus
WO2016044044A1 (en) * 2014-09-17 2016-03-24 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set
DE102016206623A1 (en) 2015-05-05 2016-11-10 Borgwarner Inc. AXIAL DELIVERS PRE-TENSIONED FREE PLAY PLANET DRIVE FOR E-PHASE SHIFTING DEVICE
DE102016209191A1 (en) 2015-05-29 2016-12-01 Borgwarner Inc. Elastic, flexible and speed-dependent split ring gear carrier with eccentric pin
DE102016209023A1 (en) 2015-05-29 2016-12-01 Borg Warner Inc. Spring loaded planetary arrangement
WO2017019585A1 (en) * 2015-07-30 2017-02-02 Borgwarner Inc. Travel stop for planetary gears of an electric phaser
WO2017202971A1 (en) * 2016-05-27 2017-11-30 Sonceboz Automotive Sa Electric camshaft phase-shifter with single shaft
DE102017120810A1 (en) 2016-09-13 2018-03-15 Borgwarner Inc. SUSTAINABLE PLANETARY WHEEL CARRIER
US10408096B2 (en) 2017-03-16 2019-09-10 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112015003581T5 (en) * 2014-09-04 2017-06-08 Borgwarner Inc. ADJUSTABLE VARIABLE MOTOR CAMSHAFT CONTROL WITH PLANETARY ARRANGEMENT
JP6874983B2 (en) * 2016-06-24 2021-05-19 株式会社Ｓｏｋｅｎ Decelerator
CN107559410B (en) 2016-06-30 2022-02-18 博格华纳公司 Planet carrier stop for split ring planetary transmission
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 (en) * 2017-07-31 2019-02-21 ボーグワーナー インコーポレーテッド e-Phaser cushion stop
CN111219223A (en) 2018-11-26 2020-06-02 博格华纳公司 Electrically actuated variable camshaft timing device controller
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)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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 (en) * 2009-08-31 2011-03-16 Delphi Technologies, Inc. Valve train with variable cam phaser

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT409030B (en) * 2000-03-09 2002-05-27 Tcg Unitech Ag DEVICE FOR ADJUSTING A CAMSHAFT
CN102705162B (en) * 2003-08-12 2014-10-22 纳博特斯克株式会社 Yaw drive device for wind power generator

Patent Citations (5)

* Cited by examiner, † Cited by third party
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 (en) * 2009-08-31 2011-03-16 Delphi Technologies, Inc. Valve train with variable cam phaser

Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE112015002518B4 (en) * 2014-06-25 2017-11-16 Borgwarner Inc. Camshaft adjuster systems and associated adjuster with lock
CN106460588B (en) * 2014-06-25 2019-03-01 博格华纳公司 Camshaft phaser system and lock phaser therefor
WO2015200190A1 (en) * 2014-06-25 2015-12-30 Borgwarner Inc. Camshaft phaser systems and locking phasers for the same
US9771839B2 (en) 2014-06-25 2017-09-26 Borgwarner Inc. Camshaft phaser systems and locking phasers for the same
CN106460588A (en) * 2014-06-25 2017-02-22 博格华纳公司 Camshaft phaser systems and locking phasers for the same
CN105275524A (en) * 2014-07-22 2016-01-27 株式会社电装 Valve timing control apparatus
CN105275524B (en) * 2014-07-22 2018-12-25 株式会社电装 Valve timing controls equipment
WO2016044044A1 (en) * 2014-09-17 2016-03-24 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set
CN107075983B (en) * 2014-09-17 2018-12-04 博格华纳公司 Engine variable camshaft timing phaser with planetary gear set
US9810109B2 (en) 2014-09-17 2017-11-07 Borgwarner Inc. Engine variable camshaft timing phaser with planetary gear set
CN107075983A (en) * 2014-09-17 2017-08-18 博格华纳公司 Engine variable camshaft timing phaser with planetary gearsets
DE102016206623A1 (en) 2015-05-05 2016-11-10 Borgwarner Inc. AXIAL DELIVERS PRE-TENSIONED FREE PLAY PLANET DRIVE FOR E-PHASE SHIFTING DEVICE
US10233999B2 (en) 2015-05-05 2019-03-19 Borgwarner, Inc. Off-axis-loaded anti-backlash planetary drive for e-phaser
CN106195215A (en) * 2015-05-29 2016-12-07 博格华纳公司 There is the separate type ring stand of the band cam pin with spring flexibility and speed dependence
US9664254B2 (en) 2015-05-29 2017-05-30 Borgwarner Inc. Split ring carrier with eccentric pin with spring compliance and speed dependence
US10344825B2 (en) 2015-05-29 2019-07-09 Borgwarner Inc. Spring loaded plant gear assembly
DE102016209191A1 (en) 2015-05-29 2016-12-01 Borgwarner Inc. Elastic, flexible and speed-dependent split ring gear carrier with eccentric pin
DE102016209023A1 (en) 2015-05-29 2016-12-01 Borg Warner Inc. Spring loaded planetary arrangement
JP2016223439A (en) * 2015-05-29 2016-12-28 ボーグワーナー インコーポレーテッド Spring loaded planet gear assembly
JP2017015251A (en) * 2015-05-29 2017-01-19 ボーグワーナー インコーポレーテッド Split ring carrier having eccentric pin with spring compliance and velocity dependency
JP2018523774A (en) * 2015-07-30 2018-08-23 ボーグワーナー インコーポレーテッド Detent part for planetary gear of electric phase shifter
CN107923272A (en) * 2015-07-30 2018-04-17 博格华纳公司 Travel stops for planetary gears of electric phasers
WO2017019585A1 (en) * 2015-07-30 2017-02-02 Borgwarner Inc. Travel stop for planetary gears of an electric phaser
FR3051835A1 (en) * 2016-05-27 2017-12-01 Sonceboz Automotive Sa DIRECT SHAFT ELECTRIC CAM SHAFT DEEPER
WO2017202971A1 (en) * 2016-05-27 2017-11-30 Sonceboz Automotive Sa Electric camshaft phase-shifter with single shaft
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CN104822909A (en) 2015-08-05

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