CN104822909A - Split ring gear planetary cam phaser - Google Patents
Split ring gear planetary cam phaser Download PDFInfo
- Publication number
- CN104822909A CN104822909A CN201380062453.0A CN201380062453A CN104822909A CN 104822909 A CN104822909 A CN 104822909A CN 201380062453 A CN201380062453 A CN 201380062453A CN 104822909 A CN104822909 A CN 104822909A
- Authority
- CN
- China
- Prior art keywords
- ring gear
- gear
- side ring
- planetary
- outlet side
- 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.)
- Pending
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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
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- 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
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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
Invention field
The present invention relates to a kind of for dynamic conditioning camshaft relative to the phase angle of engine crankshaft or rotation relationship to improve the planetary gear set of explosive motor fuel efficiency.
background
There is many different devices to realize this phase modulation of engine cam in current production.Such as, U.S. Patent Application Publication No. 2010/0064997 is seen; U.S. Patent Application Publication No. 2004/0206322; U.S. Patent number 7,506,623; U.S. Patent number 7,047,923; U.S. Patent number 6,971,352; U.S. Patent number 6,138,622; U.S. Patent number 6,129,061; U.S. Patent number 5,680,836; U.S. Patent number 5,361,736; U.S. Patent number 5,327,859; U.S. Patent number 4,850,427; And German patent DE 4110195.Although each in these devices seems to be suitable for performing expectation function, have been found that these devices have high overall cost and/or high frictional loss.Make us desirably providing a kind of and there is lower frictional loss and the lower cam phaser of overall cost.
general introduction
Disclose a kind of for the cam phaser of dynamic conditioning explosive motor camshaft relative to the rotation relationship of engine crankshaft.This cam phaser can comprise an epicyclic gear system, the sun gear that this epicyclic gear system has a driving side ring gear driven by sprocket wheel and Infinite Cyclic side power transmission member by this engine crankshaft, multiple planetary pinion and are positioned at center.This cam phaser also comprises an outlet side ring gear, and this outlet side ring gear is concentric and be connected on this camshaft with this sun gear.Compared with this driving side ring gear, this outlet side ring gear can have the tooth (be greater than or be less than) of varying number, and the multiple that this value corresponds to planetary pinion quantity provides tooth to aim at planetary joint place each in these planetary pinions.
This driving side ring gear radially can be guided by this outlet side ring gear.Motor can be connected on this sun gear for relative to this sun gear of these planet gear drives.This electronic function rotates to maintain a constant phase position with the speed equal with this driving side ring gear, and this electromotor velocity can cause cam phase to change function from an equivalent change occurs.This driving side ring gear, this outlet side ring gear, the plurality of planetary pinion and this sun gear define a Planetary Gear Transmission and connect, this Planetary Gear Transmission connects the velocity ratio with a high numerical value, thus allows under the driving torque demand relatively low to this motor, realize the adjustment of accurate phase angle.This driving side ring gear and outlet side ring gear define a ring gear be separated.These planetary pinions can be supported by the first carrier board and the second carrier board, and these carrier boards are axially guided for the plurality of planetary pinion is fastening in the axial direction by this driving side ring gear and outlet side ring gear.
A kind ofly can comprise an epicyclic gear system for dynamic conditioning explosive motor camshaft relative to the cam phaser of the rotation relationship of engine crankshaft, this epicyclic gear system has a ring gear be separated, and the ring gear of this separation comprises the driving side ring gear and an outlet side ring gear that can be connected for rotating together with this camshaft that need to be driven by sprocket wheel and an Infinite Cyclic side power transmission member by this engine crankshaft.This epicyclic gear system can have the ring gear be separated with this and be in a sun gear of concentric position and joggle(d) joint and be combined in multiple planetary pinions between ring gear that this sun gear is separated with this.
Time compared with driving side ring gear, this outlet side ring gear can have the tooth (be greater than or be less than) of varying number, and the multiple that this value corresponds to planetary pinion quantity provides tooth to aim at planetary joint place each in these planetary pinions.This driving side ring gear is radially guided by this outlet side ring gear.Motor can be connected on this sun gear for relative to this sun gear of these planet gear drives.This electronic function rotates to maintain a constant phase position with the speed equal with this driving side ring gear, and wherein this electromotor velocity can cause cam phase to change function from an equivalent change to occur.This driving side ring gear, this outlet side ring gear, the plurality of planetary pinion and this sun gear define a Planetary Gear Transmission and connect, this Planetary Gear Transmission connects the velocity ratio with a high numerical value, thus allows under the driving torque demand that this motor is relatively low, realize the adjustment of accurate phase angle.These planetary pinions can be supported by the first carrier board and the second carrier board, and these carrier boards are axially guided for the plurality of planetary pinion is fastening in the axial direction by this driving side ring gear and outlet side ring gear.
A kind of for assemble and dynamic conditioning explosive motor camshaft can comprise relative to the method for the rotation relationship of engine crankshaft: to assemble an epicyclic gear system, this epicyclic gear system has a ring gear be separated, the ring gear of this separation comprises the driving side ring gear and an outlet side ring gear that can connect for rotating together with this camshaft that need to be driven by sprocket wheel by this engine crankshaft, and this sprocket wheel engages with an Infinite Cyclic side power transmission member; The sun gear of this epicyclic gear system is placed in the concentric position place of the ring gear be separated with this; Multiple planetary pinion is engaged by engagement and is bonded between ring gear that this sun gear is separated with this; And this outlet side ring gear is provided, time compared with driving side ring gear, this outlet side ring gear has the tooth (be greater than or be less than) of varying number, and the multiple that this value corresponds to planetary pinion quantity provides tooth to aim at planetary joint place each in these planetary pinions.
This epicyclic gear system assembly can rotate to make frictional loss minimum as a unit together with this sprocket wheel.The electronic function be connected on this sun gear drives with the speed equal with this driving side ring gear to maintain a constant phase position or the speed that can be not equal to this driving side ring gear with one drives to produce a phase change function.
For those of ordinary skills when reading the explanation for putting into practice the optimal mode that the present invention considers in conjunction with the following drawings, other application of the present invention will become clear.
brief description of drawings
Explanation herein have references to accompanying drawing, wherein runs through these views and refers to similar part with similar reference number, and in the accompanying drawings:
Fig. 1 is the perspective view of a cam phaser, wherein this cam phaser end plate is removed, the figure shows one and be placed in inner planetary gear set, this planetary gear set has the ring gear be separated, the sun gear of an arranged concentric and a multiple planetary pinion, and these planetary pinion joggle(d) joints are combined between the ring gear that this sun gear is separated with this; And
Fig. 2 is the cross sectional view of the cam phaser of Fig. 1, wherein when compared with driving side ring gear, this outlet side ring gear has the tooth (be greater than or be less than) of varying number, and the multiple that this value corresponds to planetary pinion quantity provides tooth to aim at planetary joint place each in these planetary pinions.
describe in detail
Referring now to Fig. 1 to Fig. 2, illustrate a ring gear planetary convex phase discriminator 10 be separated.This cam phaser 10 can comprise a planetary gear set 12, this planetary gear set is with the sun gear 14 of a center arrangement, multiple identical planetary pinion 16a, 16b, 16c and a ring gear 18 be separated, and the ring gear of this separation is limited by two ring gears (i.e. a driving side ring gear 18a and outlet side ring gear 18b).These two ring gears 18a, 18b have the tooth of varying number separately relative to each other, and wherein the difference of number of teeth amount equals the multiple of the quantity of planetary pinion 16a, 16b, 16c in this planetary gear set 12.The wheel tooth of these two ring gears 18a, 18b can modified profile to allow these ring gears 18a, 18b correctly to engage with these planetary pinions 16a, 16b, 16c.These planetary pinions 16a, 16b, 16c can keep being in fixing relation each other by planetary support 20a, a 20b.By a timing chain (not shown), an engine crankshaft (not shown) can be joined on a ring gear 18a in these two ring gears rotatably by a sprocket wheel 22, and this engine crankshaft 24 can join another ring gear 18b in these two ring gears rotatably to.A motor 26 can engage with the sun gear 14 of this planetary gear set 12 rotatably.Because these two ring gears 18a, 18b as one man rotate, when this sun gear 14 by this motor 26 to rotate with any one identical speed in these ring gears 18a, 18b time to maintain a constant cam phase position.When this sun gear 14 by this motor 26 with the speed driving different from these ring gears 18a, 18b time, ring gear speed slightly different relative to another ring gear can cause cam phase conversion function.The ratio of a very high numerical value can be obtained in this way and this camshaft can from this bent axle relative to increasing the nominal rotation relationship of this camshaft 24 or reducing phase place.
This cam phaser 10 can be used to the rotation relationship of this camshaft 24 of dynamic conditioning relative to this engine crankshaft to improve the fuel efficiency of motor.This cam phaser 10 is compared than previously known device and is achieved this cam phase modulation function with lower frictional loss and lower holistic cost.The adjustment of this cam phase angle utilizes this planetary gear set 12 to realize, this planetary gear set provides ratio (the unrestriced mode by way of example of a high numerical value, such as in the configuration shown about 57: 1), can accurately adjust this cam phase angle in the relatively low driving torque of this adjustment motor 26 like this.
When this engine running and this cam phase by adjustment time, this whole cam phaser 10 assembly is as a finite element rotation, and this makes frictional loss minimum.When motor operate and this cam phase by adjustment time, this adjustment motor 26 can drive with the speed equal with this camshaft to maintain a constant cam phase position.When this motor is when operating and this cam phase needs to adjust, this adjustment motor 26 can drive with the rotational speed of the ring gear 18 being not equal to this separation to cause cam phase conversion function in advance or direction of retreat.
The timing chain driven by engine crankshaft can engage with the tooth of a sprocket wheel 22.Unrestriced mode by way of example, shown and in the configuration illustrated, number of teeth amount on this engine crank sprocket wheel can be ten nine (19) and number of teeth amount on this sprocket wheel 22 can be 38 (38), and this produces a ratio and this sprocket wheel 22 can be driven with the half of this engine crank speed.Go out as demonstrated, this planetary gear set 12 assembly can have a single sun gear 14 and three planetary pinions 16a, 16b, 16c, and these planetary pinions can be in transmission meshing relation with this sun gear 14.Two ring gear 18a, 18bs of separating concentric with this sun gear 14 can be there are.This sprocket wheel 22 can have the ring gear tooth of the driving side ring gear 18a be formed on internal diameter and radially can be guided by this outlet side ring gear 18b.Number of teeth amount on this driving side ring gear 18a can be greater than or less than the number of teeth amount on this outlet side ring gear 18b, and wherein the difference of number of teeth amount is the multiple of the quantity of planetary pinion 16a, 16b, 16c.In this way, there is tooth and aim in each planetary engaging position place in these three planetary pinions 16a, 16b, 16c.
Unrestriced mode by way of example, shown and in the configuration illustrated, this driving side ring gear 18a can have 70 (70) individual internal tooths and this outlet side ring gear 18b can have 67 (67) individual teeth.Unrestriced mode by way of example, shown and in the configuration illustrated this sun gear can have 26 (26) individual teeth, and these planetary pinions 16a, 16b, 16c can have 21 (21) individual teeth separately.This arrangement causes the velocity ratio that a ring gear is very high relative to another ring gear.If this driving side ring gear 18a keeps static, this sun gear 14 can rotate 57.55 times and rotate a circle to cause this outlet side ring gear 18b.Therefore, cam phase change once can require this sun gear 14 relative to this sprocket wheel 22 almost 60 (60) spend relatively to rotate.Those of ordinary skill in the art should recognize that this disclosure invention can realize different velocity ratios and therefore the invention is not restricted to the particular configuration in this displaying and discussion.
This outlet side ring gear 18b can be rotatably secured on an end plate 28, unrestriced mode by way of example, and this end plate can be secured on this camshaft 24 by a bolt 36.This outlet side ring gear 18b and this end plate 28 can be connected with each other and act on this camshaft 24 as one in this way, and this entirety can securely guide for rotating to this engine cylinder-body without the need to extra guide features.This sprocket wheel 22 is low with the relative velocity of the driving side ring gear 18a be connected to this outlet side ring gear 18b and a simple steel to steel or lining are enough to these parts relative to each other correctly radially to be located.Another end plate (not shown in Fig. 1 to Fig. 2) can be provided axially to locate the driving side ring gear 18a of this sprocket wheel 22 and this connection.
These three planetary pinions 16a, 16b, 16c can carry out ring circumferentially and radially locate, unrestriced mode by way of example by these two carryings half portion 20a, 20b, and these two carrying half portion can be secured to one another by three bolts 30a, 30b, 30c.We believe, these planetary pinions 16a, 16b, 16c can be come radially by pitch wheel tooth and ring is located circumferentially, will reduce the cost of this assembly further by omitting these two carrying half portion.We believe further, and these planetary pinions 16a, 16b, 16c can be positioned axially between by being disposed between these two isolated end plates (being similar to the end plate 28 shown), if these carryings half portion 20a, 20b do not exist.Because these all gears 14,16a, 16b, 16c, 18a, 18b only rotate relative to each other in the phase modulation process of camshaft, noise problem should not be produced.These gears 14,16a, 16b, 16c, 18a, 18b can be all the spur gears that can not produce axial load parts.
A transposition motor 26 can be attached on this device case (not shown), and wherein an output shaft 38 of this motor 26 is secured on this sun gear 14.As long as this motor 26 is to rotate with the identical speed of this sprocket wheel 22, cam phase modulation would not occur.The speed increasing or reduce this motor 26 will cause transposition or the phase modulation function of this planetary gear set 12.A sensor 32 can be used as the feedback of a motor controller 34, to measure the current location of a sprocket wheel 22 relative to this camshaft 24, to determine to need in any position to make which adjustment (if existence) in time to realize optimum engine efficiency.
Although the present invention has combined the most practical and preferred embodiment considered at present and has been illustrated, should be appreciated that and the invention is not restricted to these disclosed embodiments, and the different amendment that the spirit and scope being intended to be encompassed in claims on the contrary comprise and equivalent arrangement, to this scope should give most broad sense explanation in case contain as law all these type of amendment and the equivalent structures of being allowed.
Claims (15)
1. a camshaft (24) for dynamic conditioning explosive motor relative in a kind of cam phaser (10) of the rotation relationship of an engine crankshaft, this cam phaser (10) comprises an epicyclic gear system (12), this epicyclic gear system has the driving side ring gear (18a) driven by an Infinite Cyclic side power transmission member by this engine crankshaft, a multiple planetary pinion (16a, 16b, 16c) and a sun gear (14) being positioned at center, improvement comprises:
And the outlet side ring gear (18b) that is connected to this camshaft (24) on concentric with this sun gear (14), compared with this driving side ring gear (18a), this outlet side ring gear (18b) has the tooth of varying number, this value corresponds to planetary pinion (16a, 16b, 16c) multiple of quantity is with at these planetary pinions (16a, 16b, 16c) in each planetary joint place provide tooth to aim at.
2. improve as claimed in claim 1, comprise further:
This driving side ring gear (18a) is radially guided by this outlet side ring gear (18b).
3. improve as claimed in claim 1, comprise further:
One is connected to the motor (26) on this sun gear (14), this motor is used for these planetary pinions (16a relatively, 16b, 16c) this sun gear (14) is driven, wherein this motor (26) rotates to maintain a constant phase position with the speed equal with this driving side ring gear (18a), and this electromotor velocity can cause cam phase to change function from the change that equals this driving side ring gear (18a) value occurs.
4. improve as claimed in claim 1, wherein this driving side ring gear (18a), this outlet side ring gear (18b), the plurality of planetary pinion (16a, 16b, 16c) and this sun gear (14) define Planetary Gear Transmission and connect, this Planetary Gear Transmission connects the velocity ratio with a high numerical value, thus allows under relatively low driving torque demand, realize the adjustment of accurate phase angle.
5. improve as claimed in claim 1, comprise further:
The first carrier board axially guided by this driving side ring gear (18a) and the second carrier board (20a, 20b) and for fastening the plurality of planetary pinion (16a in the axial direction, 16b, 16c) outlet side ring gear (18b).
6. one kind for the cam phaser (10) of dynamic conditioning explosive motor camshaft (24) relative to the rotation relationship of engine crankshaft, and this cam phaser (10) comprising:
An epicyclic gear system (12), this epicyclic gear system has a ring gear (18) be separated, the ring gear of this separation comprises a driving side ring gear (18a) needing to be driven by an Infinite Cyclic side power transmission member by this engine crankshaft, an outlet side ring gear (18b) that can connect for rotating together with this camshaft (24), this epicyclic gear system (12) has the sun gear (14) of the arranged concentric of a ring gear be separated with this (18), and joggle(d) joint is combined in the multiple planetary pinion (16a between ring gear (18) that this sun gear (14) is separated with this, 16b, 16c).
7. cam phaser (10) as claimed in claim 6, comprises further:
Compared with this driving side ring gear (18a), this outlet side ring gear (18b) has the tooth of varying number, this value corresponds to planetary pinion (16a, 16b, 16c) multiple of quantity is with at these planetary pinions (16a, 16b, 16c) in each planetary joint place provide tooth to aim at.
8. cam phaser (10) as claimed in claim 6, comprises further:
This driving side ring gear (18a) is radially guided by this outlet side ring gear (18b).
9. cam phaser (10) as claimed in claim 6, comprises further:
One is connected to the motor (26) on this sun gear (14), this motor is used for these planetary pinions (16a relatively, 16b, 16c) this sun gear (14) is driven, wherein this motor (26) rotates to maintain a constant phase position with the speed equal with the ring gear that this is separated (18), and this electromotor velocity can cause cam phase to change function from an equivalent change occurs.
10. cam phaser (10) as claimed in claim 6, wherein this driving side ring gear (18a), this outlet side ring gear (18b), the plurality of planetary pinion (16a, 16b, 16c) and this sun gear (14) define Planetary Gear Transmission and connect, this Planetary Gear Transmission connects the velocity ratio with a high numerical value, thus allows under relatively low driving torque demand, realize the adjustment of accurate phase angle.
11. cam phasers (10) as claimed in claim 6, comprise further:
The first carrier board axially guided by this driving side ring gear (18a) and the second carrier board (20a, 20b) and for fastening the plurality of planetary pinion (16a in the axial direction, 16b, 16c) outlet side ring gear (18b).
12. 1 kinds for assemble and a camshaft (24) of dynamic conditioning explosive motor relative to the method for the rotation relationship of engine crankshaft, the method comprises:
Assemble an epicyclic gear system (12), this epicyclic gear system has a ring gear (18) be separated, the ring gear of this separation comprises the driving side ring gear (18a) and an outlet side ring gear (18b) that can connect for rotating together with this camshaft (24) that need to be driven by a sprocket wheel (22) by this engine crankshaft, and this sprocket wheel engages with an Infinite Cyclic side power transmission member;
By ring gear (18) arranged concentric of a sun gear (14) of this epicyclic gear system (12) relative to this separation;
Engaged by engagement and multiple planetary pinion (16a, 16b, 16c) be bonded between ring gear (18) that this sun gear (14) is separated with this; And
This outlet side ring gear (18b) is provided, wherein compared with this driving side ring gear (18a), this outlet side ring gear has the tooth of varying number, this value corresponds to planetary pinion (16a, 16b, 16c) multiple of quantity provides tooth to aim at planetary joint place each in these planetary pinions (16a, 16b, 16c).
13. methods as claimed in claim 12, comprise further:
This epicyclic gear system (12) assembly is made to rotate to make frictional loss minimum together with this sprocket wheel (22) as a unit.
14. methods as claimed in claim 12, comprise further:
The motor (26) be connected on this sun gear (14) is driven, with the phase position remained unchanged with the speed identical with the ring gear that this is separated (18).
15. methods as claimed in claim 12, comprise further:
The motor (26) be connected on this sun gear (14) is driven, to adjust a phase position with the ring gear be separated with this (18) unequal speed.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US201261735513P | 2012-12-10 | 2012-12-10 | |
| US61/735513 | 2012-12-10 | ||
| PCT/US2013/071202 WO2014092963A1 (en) | 2012-12-10 | 2013-11-21 | Split ring gear planetary cam phaser |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN104822909A true CN104822909A (en) | 2015-08-05 |
Family
ID=50934818
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201380062453.0A Pending CN104822909A (en) | 2012-12-10 | 2013-11-21 | Split ring gear planetary cam phaser |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20150315939A1 (en) |
| JP (1) | JP2015537158A (en) |
| CN (1) | CN104822909A (en) |
| DE (1) | DE112013005415T5 (en) |
| WO (1) | WO2014092963A1 (en) |
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| CN109322720A (en) * | 2017-07-31 | 2019-02-12 | 博格华纳公司 | Automatically controlled phaser snubber or stopper bushing |
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| CN106460588B (en) * | 2014-06-25 | 2019-03-01 | 博格华纳公司 | Camshaft phaser system and locking phase device for it |
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| JP2016211541A (en) | 2015-05-05 | 2016-12-15 | ボーグワーナー インコーポレーテッド | Off-axis-loaded anti-backlash planetary drive for e-phaser |
| 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 |
| US9664254B2 (en) | 2015-05-29 | 2017-05-30 | Borgwarner Inc. | Split ring carrier with eccentric pin with spring compliance and speed dependence |
| 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 |
| FR3051835B1 (en) * | 2016-05-27 | 2018-05-11 | Sonceboz Automotive Sa | DIRECT SHAFT ELECTRIC CAM SHAFT DEEPER |
| 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 |
| DE102017120810A1 (en) | 2016-09-13 | 2018-03-15 | Borgwarner Inc. | SUSTAINABLE PLANETARY WHEEL CARRIER |
| 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 |
| US10408096B2 (en) | 2017-03-16 | 2019-09-10 | Borgwarner Inc. | Engine variable camshaft timing phaser with planetary gear set |
| 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 |
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2013
- 2013-11-21 WO PCT/US2013/071202 patent/WO2014092963A1/en active Application Filing
- 2013-11-21 US US14/649,982 patent/US20150315939A1/en not_active Abandoned
- 2013-11-21 JP JP2015546500A patent/JP2015537158A/en active Pending
- 2013-11-21 DE DE112013005415.9T patent/DE112013005415T5/en not_active Withdrawn
- 2013-11-21 CN CN201380062453.0A patent/CN104822909A/en active Pending
Patent Citations (3)
| 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 |
| CN102705162A (en) * | 2003-08-12 | 2012-10-03 | 纳博特斯克株式会社 | Yaw drive method and device for wind power generator |
| US20060236965A1 (en) * | 2005-04-23 | 2006-10-26 | Schaeffler Kg | Camshaft adjustment device for an internal combustion engine |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109322720A (en) * | 2017-07-31 | 2019-02-12 | 博格华纳公司 | Automatically controlled phaser snubber or stopper bushing |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2015537158A (en) | 2015-12-24 |
| US20150315939A1 (en) | 2015-11-05 |
| WO2014092963A1 (en) | 2014-06-19 |
| DE112013005415T5 (en) | 2015-07-30 |
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| EXSB | Decision made by sipo to initiate substantive examination | ||
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Application publication date: 20150805 |
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| WD01 | Invention patent application deemed withdrawn after publication |