CN103821886A - Automatic speed change gear - Google Patents
Automatic speed change gear Download PDFInfo
- Publication number
- CN103821886A CN103821886A CN201410096952.8A CN201410096952A CN103821886A CN 103821886 A CN103821886 A CN 103821886A CN 201410096952 A CN201410096952 A CN 201410096952A CN 103821886 A CN103821886 A CN 103821886A
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- Prior art keywords
- gear
- clutch
- transmission
- ring
- train
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- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H47/00—Combinations of mechanical gearing with fluid clutches or fluid gearing
- F16H47/06—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type
- F16H47/08—Combinations of mechanical gearing with fluid clutches or fluid gearing the fluid gearing being of the hydrokinetic type the mechanical gearing being of the type with members having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides an automatic speed change gear. The automatic speed change gear comprises an automatic speed change clutch, a brake, a one-way coupler and a torque converter with a lock-up clutch, and the unique clutches, the unique brake and unique distribution achieve a plurality of forward speed ranges and reverse driving. The speed change gear is extremely compact in structure and light in weight. The speed change gear is compact, and can smoothly achieve a plurality of gear ratios. For example, reverse acting force of a gear set can be used for sending torque converter turbine torque in a reverse driving state through a plurality of structure transmission ratios in a middle rotating speed range in one-way connection.
Description
Technical field
The present invention relates to a kind of vehicular automatic transmission, relate in particular to a kind of automatic transmission with many forward gears.
Background technique
Existing motor vehicle, its multiple speed automatic transmission has many shortcomings, for example complex structure, cost is high, and Heavy Weight is simultaneously smooth and easy not in speed-change process.Self-shifting clutch of the present invention, the unique arrangement of break and unidirectional coupling realizes multiple forward speed ranges and reverse direction actuation.Speed changer has extremely compact structure, and it is lightweight.Speed changer is in having compactedness, speed changer can smooth-goingly be realized multiple gear ratio, for example, provide the reaction force of gear train by the structure within the scope of the intermediate speed in unidirectional connection, the first and second speed transmission ratios, also can, in the time of reverse direction actuation state, be used for sending torque converter turbine moment of torsion.
Torsion path between reverse direction actuation state in motor and planetary pinion is by reverse friction clutch and cylinder or drum, the surface that it provides the friction plate of a middle clamping strap and reverse friction clutch to engage, the shell using like this or rotary drum have saved an extra assembly for multiple use.This motor transmission ground disconnects from wheel, and therefore will hinder vehicle movement, thereby has avoided in the time of unexpected unexpected variation of acceleration, and what operated by driver changes to enabled condition in reverse scope.
Summary of the invention
The object of the present invention is to provide a kind of gearshift to be more prone to, power distribution is more reasonable, and pause and transition in rhythm or melody sense is less, has the vehicular automatic transmission of advantage simultaneously on spatial volume.
Automatic transmission of the present invention has: input shaft, output shaft, fixed component; There is the torque-converters of the impeller that can be drivingly coupled to vehicle power source, torque-converters comprises a lock-up clutch, be positioned at fluid torque converter and impeller housing, the moment of torsion outlet side of lock-up clutch has damper and the turbine between impeller and turbine quill, and this turbine is connected to described impeller and can drives and is connected on input shaft;
Planetary gear set, it comprises the first, the second and third planet train of gearings, each train of gearings has sun gear, gear ring, planetary pinion, and the planet carrier of rotatably support planetary pinion,
Clutch device, brake gear.
Preferably, clutch device comprises: the friction type first clutch device optionally engaging, for selectively the sun gear of described the first and second planetary gear set being engaged with described input device; The friction type second clutch device optionally engaging, for selectively connecting described the second planetary gear set and inside engaged gear, described the first planetary gear set is connected with described input device;
Brake gear comprises: the exercisable friction stopping device of the first selectivity, for prevent described gear ring the first planetary gear set rotation and set up the first velocity ratio in described transmission with described first clutch device; The friction stopping device of the second selectively actuatable, for prevent described the second planetary gear set gear ring rotation and cooperate and described first clutch device, transmit to set up described in one second velocity ratio; The exercisable friction stopping device of the 3rd selectivity, the 3rd velocity ratio that is used for the rotation of the gear ring that prevents described third planet gear train and cooperate to set up with described first clutch device is in described transmission, the first and second clutch device cooperate in transmitting procedure to set up four velocity ratios, described second clutch device and described the 3rd braking device match, to form the 5th velocity ratio in described transmission, described second clutch device and described the second braking device match, setting up the 6th velocity ratio in described transmission and; Described the first brake gear and described the 3rd braking device match, to set up a reverse velocity ratio in described transmission.
Preferably, first clutch device has an inner race and first group of clutch element between described inner race and described internal surface, spaced angle is around described axle, and described internal surface contacts with described inner race, connects inner ring and rotates with the first sense of rotation for driving.
Preferably, the inner ring that the outer ring of each braking device is all prevented from the overrunning clutch of the mission case of rotation is for good and all fixedly attached to gear ring, and its outer ring is connected to parts of forward clutch; Joint and one-way brake roller type surmount joint and conventionally have an external cam, and this cam has the surface of an inclination transmission and connects, surmount joint by according to inner ring with respect to the roller of rotation of outer race discharged by inner ring.
Preferably, described the first braking device comprises:
The first break of the torque transmission paths between described the first epicyclic train and the inside engaged gear of fixed component;
The connection set that one-way driver between the 1st unidirectional arranged in series and the first gear part described the first break and the gear ring of fixed component is connected;
Be arranged in second brake the connection set that is parallel to described the first braking and the 1st unidirectional array.
Preferably, second brake, it is located at the torque transmission paths between the first gear part and the carrier of sun gear of the second epicyclic train and described fixed component;
The connection set that the second hypervelocity tandem arrangement is connected for the one-way driver between the first epicyclic train and the sun gear of the second epicyclic train and the carrier of described fixed component with the 3rd break.
Preferably, described the 3rd braking device comprises:
The 3rd break, it is located at the torque transmission paths between the carrier of gear ring of fixed component and described the second epicyclic train and described third planet train of gearings;
And the 3rd connection set of connecting of the one-way driver exceeding the speed limit between the second epicyclic train and gear ring and the carrier of described fixed component of third planet train of gearings of the 3rd break that is arranged in parallel.
Beneficial effect:
Vehicular automatic transmission in the present invention, has overcome deficiency of the prior art, has the automatic transmission of better damping effect, and it is structurally compacter, can reduce the volume of speed changer, smooth-goingly realizes many grades of speed changes.In addition the torque-converters in speed changer provided by the invention has a lock-up clutch, lock-up clutch also has damper, its beneficial effect is to make the speed changer of this vehicle more smooth-going, its friction clutch of speed changer provided by the invention, break have multi-selection well in structural configuration simultaneously, it realizes better output in dynamic Control, make Multi-stage transmission more smooth-going, good structure makes it have better compactedness simultaneously.
Accompanying drawing explanation
Fig. 1 is the mechanical structure schematic diagram for the speed changer preferred embodiment of motor vehicle of the present invention.
Fig. 2 is the mechanical structure schematic diagram for another preferred embodiment of speed changer of motor vehicle of the present invention.
Embodiment
First with reference to Fig. 1,2, one is connected to the hydraulic moment variator 10 of explosive motor, it comprises blade turbomachine 16, with a cultrate stator 18, the impeller 12 being connected with bent axle 14, the mobile loop of annular fluid that impeller and turbine wheel limit, thus, the stator 18 that impeller is connected to turbo machine is rotatably supported on a fixing stator sleeve axle 20, with an overrun brake 70, in case the direction rotation impeller contrary with sense of rotation in fastening, even if in the opposite direction voltuntary movement allows.
Torque converter assembly comprises that a lock-up clutch 24 is positioned at fluid torque converter impeller housing 25.The moment of torsion outlet side of lock-up clutch 24 comprises that a damper 26 is positioned at impeller and turbine shaft, and this is between transmission input shaft 28, in the time that clutch 24 is engaged, and described turbine wheel and mechanical connection; In the time that clutch 24 departs from, they are connected and mechanically disconnect, and the fluid of vibration damper absorption band lock-up clutch is for oil feed pump assembly 30 from output to the relevant transition torque ripple of engagement of fluid torque converter.
Planetary pinion comprises first, second and third planet epicyclic train 32, 34, with 36, the first epicyclic train 32 comprises sun gear 38, gear ring 40, carrier 42 and planetary pinion 44, the supporting sun gear 38 being engaged by bracket 30 and gear ring 40, the second epicyclic train 34 comprises sun gear 46, gear ring 48, carrier 50 and planetary pinion 52, be rotatably supported in sun gear 46 and gear ring 48 that bearing 50 engages, third planet train of gearings 36 comprises sun gear 54, gear ring 56, sun gear 54 and the gear ring 46 of carrier 58 and engagement rotate the planetary pinion 60 that is bearing in freely slide rack 58.
Sun gear 38 is driven to be connected by the input shaft 28 of parts 62 continuously, and clutch 64 connects and discharges, input shaft and sun gear 54; Clutch 66 connects and discharges, input shaft and carrier 50.
Sun gear 46 is mutually can be connected with support 42 with driving, and their keep not rotating, and operation by break 68 discharges.Break 70 keeps not rotating, and discharges the alternately gear 40 of the first planet epicyclic train 32 of ring.The second epicyclic train 34 of carrier 50 is driven to be connected to third planet train of gearings 36 continuously, and the gear ring 56 of method by member 72, to the 3rd friction brake 74, its hold prevent rotation, and alternately carrier 50 of release, an excessive connector 78 in gear ring 56 and seat ring 76, other ethnic 80 connectors 78 are fixed and prevent the case of transmission 82 of rotation, it provides moment of torsion reaction thereon, by break 68, on 70,74 fixed components that provide, and be kept locking measure by this axle 20.
The gear ring 48 of the carrier 58 of the second epicyclic train and described third planet train of gearings can drive and be connected to each other, and they are also connected to output shaft 84, it can drive and to be connected to the vehicle that is delivered to driving wheel by the running shaft of its difference power actuation mechanism.
When first velocity ratio in transmission operation, forward clutch 64 is engaged the driver with connector 78, and keeping gear ring 56 facing to the rotation at mission case 82, the first velocity ratio is to result from third planet train of gearings 36 and output is taken at carrier 58, this driver output shaft 84.
In low scope, break 74 engages and replaces, and the moment of torsion reaction providing by connector 78, for meeting drive condition during this period, so by remaining against rotation gear ring 56, when engine braking, can use and manually slide in low scope.
That engages by maintenance upgrades to result forward clutch 64 and the engage brake 68 of second speed ratio.By this way, the sun gear 54 of third planet train of gearings 36 is connected to input shaft 28.The maintenance of the second gear part 34 of gear ring 48 is by housing 82, and rotation in output is to take at carrier 58 and output shaft 84.
Change high-grade to from second speed than described the 3rd gear ratio need to brake 68 and brake application device 70 throw off, keep the forward clutch applying simultaneously.The gear 38 of the sun the first epicyclic train 32 is directly driven from input shaft 28, and sun gear 40 keeps not rotating, therefore, the sun gear 54 of the third planet train of gearings that the speed of carrier 42 and sun gear 46 is set up, by driving from input shaft 28 clutches 64.Therefore, the speed of gear ring 48, carrier 58 and output shaft 84 are determined.
The 4th forward velocity ratio is by keeping forward clutch 64 while engaging, applying clutch 62, and discharge other friction element.Sun gear 38, bracket 50, and sun gear 54 is driven in the rotating speed of input shaft 28 by parts 62.
When the 5th speed ratio, produce clutch 66 and break 70 engages, and another friction element is thrown off.This action drives the speed of sun gear 38 at input shaft 28, keep fixing to prevent that case of transmission 82 is by the sun gear 40 of break 70, and the speed of setting up carrier 42 and gear ring 46 carriers 50 also drives the rotating speed at the input shaft of the operation by clutch 66, therefore, gear ring 48, the rotating speed of carrier 58 and output shaft 84 and moment of torsion output are to establish.
The result of the 6th forward velocity ratio, when clutch 66 is employed, break 68 engages, and another friction element is thrown off.This operation drives the second gear part to pass through the carrier 50 of the speed of clutch 66 at input shaft 28, keeps gear ring 46 these retarders fixedly to prevent that rotation is by the operation of break 68, and definite engaging gear 48, rotating speed and the torque of carrier 50 and output shaft 84.
By engage brake 70 and 74, and discharge the result of other friction element reverse direction actuation.This action keeps gear ring 40 facing to rotating on case of transmission, drives the rotating speed of sun gear 38 at input shaft 28, and the speed of the output of setting up.The first epicyclic train 32, bracket 42, and the carrier 50 of gear ring 46, the second epicyclic trains 34 is clamped in shell 82 by the operational rotation of break 74, therefore, and gear ring 48, bracket 58, sets up speed and torque and output shaft 84.
Torque-converters comprises a lock-up clutch, is positioned at fluid torque converter and impeller housing.The moment of torsion outlet side of lock-up clutch has the damper between impeller and turbine quill, thereby makes the engagement of lock-up clutch not be accompanied by the ear-piercing torque ripple due to transition.
Inner ring unidirectional or overrun brake is directly connected to carrier and drum; The inner ring that the outer ring of break is prevented from the overrunning clutch of the mission case of rotation is for good and all fixedly attached to gear ring, and its outer ring is connected to a key element of forward clutch.Joint and one-way brake roller type surmount joint conventionally have an external cam have an inclination surperficial transmission be connected, and by according to inner ring with respect to the roller of rotational speed of outer race discharged by inner ring.A friction disk brake, keeps carrier to prevent rotation break engagement release vehicle when being connected to described housing, in the time throwing off.
The element miscellaneous part clutch that the inner ring of unidirectional coupling is also connected to clutch is connected on drum.
Friction element is the friction element in clutch and the brake disks of the multiple friction disks of having of the hydraulic actuating type that is rotatably supported on the friction disk between a member and first friction member of second group in friction element, when being applied on another member of friction element, hydraulic pressure arranges and rotatably support, this dish is brought to transmitting torque between mutual rubbing contact and the parts of friction element, be reduced when the size of hydraulic pressure offers friction element, spring disengagement dish and friction element are thereafter cannot transfer of torque.
Low/reverse gear brake band optionally engages bulging low-medium speed manually and reverse direction actuation condition.Clamping strap, by Hydrauservo System, drives the clamping strap that this contract is corresponding become with each drum and discharge this participation when corresponding servo emptying.
It is 6.64 that entirety between the first forward gear ratio and the 6th forward gear velocity ratio is propagated.In other words, output shaft and minimum advance than torque be the moment of torsion of 6.64 times of overdrive ratio, by changing no matter tooth is the both sides' of sun gear and/or gear ring the number of teeth, minimum forward velocity ratio can increase or reduce, and can not affect other ratio in any transmission, but, variation at forward ratio will affect whole gear range, if for example wish the motive force that higher low ratio causes vehicle to increase, low ratio can increase stepping between the first and second gears than also increasing.
Peak torque in this planetary gear set delivery system, therefore, (final transmission epicyclic train) will be designed to the Maximum Torque of transmission system in its downstream to only have gear train and transmission device, this allows to use the input in similar diameter shaft, as axle and clutch, cross tie part between geared parts separately, general permission will remain on bottom line in total radian size of transmission.
The fluid-operated friction torque transfer unit of the clutch using and the preferred routine of break or CD or belt, similarly, described unidirectional device is traditional parts, no matter is preferably roller or wedge block type, and transmitting torque is freely overflowed in one direction in another direction.
Although described in detail for implementing optimal mode of the present invention, the technician who is familiar with field involved in the present invention will be appreciated that within the scope of the appended claims for putting into practice various substituting design and implementation example of the present invention.
Claims (7)
1. a vehicular automatic transmission, this automatic transmission has: input shaft, output shaft, fixed component; There is the torque-converters of the impeller that can be drivingly coupled to vehicle power source, torque-converters comprises a lock-up clutch, be positioned at fluid torque converter and impeller housing, the moment of torsion outlet side of lock-up clutch has damper and the turbine between impeller and turbine quill, and this turbine is connected to described impeller and can drives and is connected on input shaft;
Planetary gear set, it comprises the first, the second and third planet train of gearings, each train of gearings has sun gear, gear ring, planetary pinion, and the planet carrier of rotatably support planetary pinion, clutch device, brake gear.
2. automatic transmission as claimed in claim 1, is characterized in that: clutch device comprises: the friction type first clutch device optionally engaging, for selectively the sun gear of described the first and second planetary gear set being engaged with described input device; The friction type second clutch device optionally engaging, for selectively connecting described the second planetary gear set and inside engaged gear, described the first planetary gear set is connected with described input device;
Brake gear comprises: the exercisable friction stopping device of the first selectivity, for prevent described gear ring the first planetary gear set rotation and set up the first velocity ratio in described transmission with described first clutch device; The friction stopping device of the second selectively actuatable, for prevent described the second planetary gear set gear ring rotation and cooperate and described first clutch device, transmit to set up described in one second velocity ratio; The exercisable friction stopping device of the 3rd selectivity, the 3rd velocity ratio that is used for the rotation of the gear ring that prevents described third planet gear train and cooperate to set up with described first clutch device is in described transmission, the first and second clutch device cooperate in transmitting procedure to set up four velocity ratios, described second clutch device and described the 3rd braking device match, to form the 5th velocity ratio in described transmission, described second clutch device and described the second braking device match, setting up the 6th velocity ratio in described transmission and; Described the first brake gear and described the 3rd braking device match, to set up a reverse velocity ratio in described transmission.
3. automatic transmission as claimed in claim 1 or 2, it is characterized in that: first clutch device has an inner race and first group of clutch element between described inner race and described internal surface, spaced angle is around described axle, described internal surface contacts with described inner race, connects inner ring and rotates with the first sense of rotation for driving.
4. the automatic transmission as described in one of claim 1-3, is characterized in that:
The inner ring that the outer ring of each braking device is all prevented from the overrunning clutch of the mission case of rotation is for good and all fixedly attached to gear ring, and its outer ring is connected to parts of forward clutch; Joint and one-way brake roller type surmount joint and conventionally have an external cam, and this cam has the surface of an inclination transmission and connects, surmount joint by according to inner ring with respect to the roller of rotation of outer race discharged by inner ring.
5. the automatic transmission as described in one of claim 1-4, is characterized in that: described the first braking device comprises:
The first break of the torque transmission paths between described the first epicyclic train and the inside engaged gear of fixed component;
The connection set that one-way driver between the 1st unidirectional arranged in series and the first gear part described the first break and the gear ring of fixed component is connected; Be arranged in second brake the connection set that is parallel to described the first braking and the 1st unidirectional array.
6. according to the automatic transmission one of claim 1-5 Suo Shu, it is characterized in that: described the second braking device comprises:
Second brake, it is located at the torque transmission paths between the first gear part and the carrier of sun gear of the second epicyclic train and described fixed component;
The connection set that the second hypervelocity tandem arrangement is connected for the one-way driver between the first epicyclic train and the sun gear of the second epicyclic train and the carrier of described fixed component with the 3rd break.
7. the automatic transmission as described in one of claim 1-6, is characterized in that: described the 3rd braking device comprises:
The 3rd break, it is located at the torque transmission paths between the carrier of gear ring of fixed component and described the second epicyclic train and described third planet train of gearings;
And the 3rd connection set of connecting of the one-way driver exceeding the speed limit between the second epicyclic train and gear ring and the carrier of described fixed component of third planet train of gearings of the 3rd break that is arranged in parallel.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410096952.8A CN103821886A (en) | 2014-03-18 | 2014-03-18 | Automatic speed change gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410096952.8A CN103821886A (en) | 2014-03-18 | 2014-03-18 | Automatic speed change gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN103821886A true CN103821886A (en) | 2014-05-28 |
Family
ID=50757103
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201410096952.8A Withdrawn CN103821886A (en) | 2014-03-18 | 2014-03-18 | Automatic speed change gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN103821886A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104110471A (en) * | 2014-06-25 | 2014-10-22 | 盛瑞传动股份有限公司 | Automatic transmission |
| CN106884938A (en) * | 2017-01-25 | 2017-06-23 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
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| US5435792A (en) * | 1994-03-28 | 1995-07-25 | Ford Motor Company | Multiple-speed automatic transmission for motor vehicles |
| JP2012097777A (en) * | 2010-10-29 | 2012-05-24 | Honda Motor Co Ltd | Automatic transmission |
| US20120322604A1 (en) * | 2009-05-01 | 2012-12-20 | GM Global Technology Operations LLC | Automatic transmission gear and clutch arrangement |
| CN102927222A (en) * | 2012-10-29 | 2013-02-13 | 长城汽车股份有限公司 | Automatic transmission |
| CN103216586A (en) * | 2012-01-18 | 2013-07-24 | 丰田自动车株式会社 | Vehicular automatic transmission |
| CN103307230A (en) * | 2012-03-13 | 2013-09-18 | 本田技研工业株式会社 | Automatic transmission |
| CN103322139A (en) * | 2012-03-19 | 2013-09-25 | 本田技研工业株式会社 | Automatic transmission |
| JP2013204663A (en) * | 2012-03-28 | 2013-10-07 | Honda Motor Co Ltd | Automatic transmission |
| CN103527733A (en) * | 2012-06-14 | 2014-01-22 | 通用汽车环球科技运作有限责任公司 | Automatic transmission gear and clutch arrangement |
| CN103807384A (en) * | 2014-02-20 | 2014-05-21 | 丽水桉阳生物科技有限公司 | Automatic gearbox |
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2014
- 2014-03-18 CN CN201410096952.8A patent/CN103821886A/en not_active Withdrawn
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5435792A (en) * | 1994-03-28 | 1995-07-25 | Ford Motor Company | Multiple-speed automatic transmission for motor vehicles |
| US20120322604A1 (en) * | 2009-05-01 | 2012-12-20 | GM Global Technology Operations LLC | Automatic transmission gear and clutch arrangement |
| JP2012097777A (en) * | 2010-10-29 | 2012-05-24 | Honda Motor Co Ltd | Automatic transmission |
| CN103216586A (en) * | 2012-01-18 | 2013-07-24 | 丰田自动车株式会社 | Vehicular automatic transmission |
| CN103307230A (en) * | 2012-03-13 | 2013-09-18 | 本田技研工业株式会社 | Automatic transmission |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104110471A (en) * | 2014-06-25 | 2014-10-22 | 盛瑞传动股份有限公司 | Automatic transmission |
| CN104110471B (en) * | 2014-06-25 | 2016-04-27 | 盛瑞传动股份有限公司 | Automatic transmission |
| CN106884938A (en) * | 2017-01-25 | 2017-06-23 | 广州汽车集团股份有限公司 | Automatic transmission and vehicle |
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Application publication date: 20140528 |