EP2959183A1 - Multi-stage planetary transmission - Google Patents
Multi-stage planetary transmissionInfo
- Publication number
- EP2959183A1 EP2959183A1 EP14701079.7A EP14701079A EP2959183A1 EP 2959183 A1 EP2959183 A1 EP 2959183A1 EP 14701079 A EP14701079 A EP 14701079A EP 2959183 A1 EP2959183 A1 EP 2959183A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- designed
- switching element
- clutch
- gear
- shaft
- 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.)
- Withdrawn
Links
- 230000005540 biological transmission Effects 0.000 title claims abstract description 54
- 230000008878 coupling Effects 0.000 description 10
- 238000010168 coupling process Methods 0.000 description 10
- 238000005859 coupling reaction Methods 0.000 description 10
- 238000010276 construction Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000009434 installation Methods 0.000 description 2
- 210000000078 claw Anatomy 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 239000006247 magnetic powder Substances 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
Classifications
-
- 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
-
- 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
- F16H3/666—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with compound planetary gear units, e.g. two intermeshing orbital gears
-
- 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
- F16H2003/442—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion comprising two or more sets of orbital gears arranged in a single plane
-
- 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
- F16H2003/445—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion without permanent connection between the input and the set of orbital gears
-
- 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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
-
- 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
-
- 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
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
Definitions
- the present invention relates to a planetary multi-speed transmission for a vehicle according to the closer defined in the preamble of claim 1.
- a power-shiftable multi-speed transmission is known.
- the drive shaft is connected via a torsional vibration damper fixed to a first shaft of a first shaft train.
- a parallel arranged second shaft strand includes, among others, designated as the shaft two output shaft.
- the two wave strands are connected to each other via three spur gear stages.
- On the first shaft train is a first three-shaft planetary gear.
- On the second shaft train are a second planetary gear and a third planetary gear.
- the multi-speed transmission thus comprises ten shafts, which communicate with each other via three spur gears and three planetary gears. To switch the eight forward gears and the one reverse gear five switching elements are necessary.
- the envisaged switching elements are hydraulically actuated.
- the switching elements are to be arranged easily accessible from the outside.
- a front-transverse installation of the transmission in a vehicle only a limited axial space is available.
- the present invention is based on the object to provide a multi-speed transmission with the highest possible number of gear ratios and good accessibility of the switching elements at the same time good gear efficiency and the lowest possible axial space requirement.
- a powershiftable multi-speed planetary gear or a multi-speed planetary gear for a vehicle is proposed with a housing, wherein the drive or the drive shaft and the output or the output shaft are arranged axially parallel to each other for a preferred front transverse installation.
- the multistage transmission according to the invention comprises only nine shafts, three planetary gear sets and only six shift elements in order to realize at least nine forward gears and one reverse gear can. Furthermore, preferably only two machine elements are provided for coupling drive and output.
- the good accessibility of the switching elements can be realized, inter alia, on the one hand by the use of brakes as switching elements and on the other hand by the use of couplings as switching elements, which are preferably positioned on outer shafts preferably on the drive and the output in the multi-step transmission according to the invention. Due to the low construction costs result in an advantageous manner low production costs and low weight of the multi-speed transmission according to the invention.
- at least one spur gear or the like is used as a machine element for coupling or for torque transmission between the drive and output, which realizes the necessary translation to the output differential.
- Preferably, only two machine elements or spur gears are provided. However, other machine elements for power transmission such as chains, belts or the like may be used.
- the planetary gear sets are arranged in the order of the first planetary gear set, second planetary gear set and third planetary gear set when viewed in the axial direction, wherein preferably two of the planetary gear sets are designed as minus planetary gear sets and at least one of the planetary gear sets as plus planetary gear set.
- a minus planetary gear set is known to be rotatably mounted on the planet gear planetary gears, which mesh with the sun gear and the ring gear of this planetary gear, so that the ring gear rotates with held planet carrier and rotating sun in the direction opposite to Sonnenradcardraum.
- a plus planetary gear set is known to be rotatably mounted on its planet gear and meshing with each other inner and outer planetary gears, the sun gear of this planetary mesh with the inner planet gears and the ring gear of this planetary gear with the outer planetary gears, so that the ring gear with held planet carrier and rotating sun gear in the direction of Clarradfilraum same direction turns.
- a plurality of planetary gear sets are arranged radially one above the other.
- the ring gear of the inner planetary gear and the sun gear of the outer planetary gear set may be designed as a component.
- the ring gear of the inner planetary gear set have an inner toothing and an outer toothing, wherein
- the interleaved planetary gear sets are arranged substantially in an axial plane, so that in an advantageous manner axial construction space is saved.
- a hydrodynamic torque converter or a hydrodynamic coupling can be used in the multistage transmission according to the invention. It is also conceivable that an additional starting clutch or an integrated starting clutch or starting brake be used. It is also possible that an electric machine or another power / power source is arranged on at least one of the shafts. In addition, a freewheel to the housing or to another shaft can be arranged on at least one of the waves.
- nine forward gears and at least one reverse gear can be switched via the switching elements provided.
- the switching elements provided.
- switching element is to be understood as meaning a switchable connection between two elements of the transmission, wherein the torque to be transmitted between these two elements is transmitted by means of frictional connection or frictional engagement or by means of positive locking. If both elements of the switchable connection are rotatable, then the switching element is referred to as a coupling and if only one of the two elements of the switchable connection rotates, the switching element is referred to as a brake.
- the geometric position or sequence of the individual switching elements is freely selectable, as long as it allows the bindability of the elements. In this way, individual elements can be moved arbitrarily in their position.
- a plurality of wheel sets can also be arranged radially one above the other, ie nested.
- Embodiments of a force-locking switching element are multi-plate clutches or brakes, band brakes, cone clutches or brakes, electromagnetic clutches, magnetic powder clutches and electro-rheological coupling.
- Embodiments of a positive switching element are jaw clutches or brakes and gear couplings.
- both friction and form-locking switching elements can generally be used.
- the second shifting element designed as a clutch and the fourth shifting element designed as a clutch can be designed as claw shifting elements, whereby clear consumption advantages are achieved.
- Figure 1 is a schematic view of a first embodiment of a multi-speed transmission according to the invention
- Figure 2 is a schematic view of a second embodiment of the multi-speed transmission.
- Figure 3 is a circuit diagram for the various embodiments of the multi-speed transmission.
- FIGS. 1 and 2 an embodiment variant of the multi-speed transmission according to the invention in planetary construction, for example as an automatic transmission or automatic transmission, is shown by way of example for a vehicle.
- the multistage transmission comprises a housing 1 1, which is indicated only schematically, with a first shaft 1 as the drive An and a second shaft 2 arranged parallel to the axis as the output Ab and further seven shafts 3, 4, 5, 6, 7, 8, 9. Furthermore, a first planetary gearset RS1, a second planetary gearset RS2 and a third planetary gearset set RS3 provided.
- a clutch first switching element K1 designed as a clutch second switching element K2, designed as a clutch third switching element K3, designed as a clutch fourth switching element K4, designed as a brake fifth switching element B1 and designed as a brake sixth Switching element B2 provided.
- two arbitrary machine elements are preferably provided, which in the case of the embodiment variants are designed by way of example as first spur gear stage ST1 and as second spur gear stage ST2.
- the first spur gear ST1 comprises a fixed gear 12, which is connected to the fifth shaft 5, and a idler gear 13 meshing with the fixed gear 12, which transmits via the ninth shaft 9 and the fourth shifting element K 4 the second wave is connectable.
- the second spur gear ST2 comprises a fixed gear 14, which is connected via the sixth shaft 6 to the ring gear HR3 of the third planetary gear set RS3, and a stationary gear 15 with the fixed gear 15, which is connected to the second shaft 2.
- the first spur gear ST1 a idler gear 12A, which is connected via the ninth shaft 9 with the fourth switching element K4, and a fixed gear 13A, which is connected to the second shaft 2.
- connection possibilities between the provided shafts 1, 2, 3, 4, 5, 6, 7, 8, 9, the planned three planetary gear sets RS1, RS2, RS3, the intended housing 1 1 and the provided switching elements K1, K2, K3, K4, B1, B2 and the proposed spur gears ST1, ST2 is by the term -verbindbar- to understand that the elements described are releasably connected, for example via a switching element, so that the connection is closed when activated switching element and open when not activated switching element.
- the detachable connection can be realized in addition to the switching element via at least one further element, such as a shaft or the like.
- the first shaft 1 as drive An with the sun SR2 of the second planetary RS2, with the sun SR1 of the first planetary RS1, with the planet PT2 of the second planetary RS2, with the planet PT1 of the first planetary RS1 and releasably connected or connectable to the first machine element or to the first spur gear ST1.
- the second shaft as output Ab is connected or detachably connected or connectable to the first machine element or to the first spur gear ST1 and to the second machine element or the second spur gear ST2.
- the second shaft 2 is connected to the fixed gear 15 of the second spur gear ST2. Furthermore, the second shaft 2 is connectable or detachably connected via the fourth shifting element K4 designed as a clutch and via the ninth shaft 9 to the idler gear 13 of the first spur gear stage.
- the second shaft 2 is in each case directly connected to the fixed gear 13A of the first spur gear ST1 and to the fixed gear 15 of the second spur gear ST2.
- the idler gear 12 A of the first spur gear is releasably connected or connectable to the first shaft 1 via the ninth shaft 9 and via the fourth switching element K4 designed as a clutch and the fifth shaft 5 and via the third shifting element K3 designed as a clutch.
- the first spur gear ST1 can be connected via the ninth shaft 9 and via the fourth shifting element K4 designed as a clutch and via the fifth shaft 5 to the planet carrier PT1 of the first planetary gearset RS1.
- the fourth switching element K4 designed as a clutch, which connects the first spur gear stage or the first spur gear pair ST1 to the output shaft or to the second shaft 2, respectively, on the other spur gear side, ie to the side of the transmission input shaft or gearbox . of the first wave 1 possessing.
- the first shaft 1 via the first switching element K1 designed as a clutch and via the third shaft 3 with the sun gear SR2 of the second planetary gear set RS2, the sun gear SR2 of the second planetary gear set RS2 via the third shaft. 3 and via the executed as a brake sixth switching element B2 to the housing 1 1 is connectable.
- the first shaft 1 can be connected via the second switching element K2 designed as a clutch and via the fourth shaft 4 both to the sun gear SR1 of the first planetary gearset RS1 and to the planetary gearset PT2 of the second planetary gearset RS2, the sun gear SR1 of the first planetary gearset RS1 and the Planetenradträ- carrier PT2 of the second planetary gearset RS2 via the fourth shaft 4 are connected to each other.
- the first shaft 1 can be connected via the third switching element K3 designed as a clutch and via the fifth shaft 5 both to the fixed gear 12 of the first spur gear ST1 and to the planet carrier PT1 of the first planetary gearset RS1.
- the fixed gear 14 of the second spur gear ST2 is connected via the sixth shaft 6 to the ring gear HR3 of the third planetary gearset RS3. Furthermore, the ring gear HR1 of the first planetary gear set RS1 is connected via the seventh shaft 7 to the planet carrier PT3 of the third planetary gearset RS3.
- the first planetary gearset RS1 and the third planetary gearset RS3 are each designed as a minus planetary gearset and the second planetary gearset RS2 as a plus planetary gearset. Furthermore, the second planetary gear set RS2 and the third planetary gear set RS3 are arranged radially one above the other in an axial plane nested.
- the second planetary gear set RS2 radially inward and the third planetary gearset RS3 is arranged radially outward in the radially nested wheelsets, wherein the two nested wheelsets RS2, RS3 via the same time as the sun gear of the third Planetenradsat- zes RS3 acting ring gear HR2 of the second planetary gearset RS2 are interconnected.
- the ring gear HR2 of the second planetary gear set RS2 can be connected to the housing 11 via the eighth shaft 8 and via the fifth shifting element B1 designed as a brake.
- FIG. 3 shows a circuit diagram or a switching matrix for the two equivalent transmission variants according to FIGS. 1 and 2.
- switching elements K1, K2, K3, K4, B1, B2 are tabulated to realize the various gear ratios, each gear ratio is a ratio i and indicated between different gear ratios of the respective gear jump ⁇ .
- further additional shift combinations are indicated as alternative fourth forward gears M1, M2, M3.
- a value of about i 0 -3.450
- the second shifting element K2 designed as a clutch, the fourth shifting element K4 designed as a clutch and the fifth shifting element B1 designed as a brake are closed in order to realize the first forward gear G1.
- the second shifting element K2 designed as a clutch, the fourth shifting element K4 designed as a clutch and the sixth shifting element B2 designed as a brake are closed.
- the first switching element K1 designed as a clutch, the second shifting element K2 designed as a clutch and the fourth shifting element K4 designed as a clutch are closed.
- the second shifting element K2 designed as a clutch, the third shifting element K3 designed as a clutch and the fourth shifting element K4 designed as a clutch are closed.
- the first shifting element K1 designed as a clutch, the second shifting element K2 designed as a clutch and the third shifting element K3 designed as a clutch are closed.
- the second shifting element K2 designed as a clutch, the third shifting element K3 designed as a clutch and the sixth shifting element B2 designed as a brake are closed.
- the seventh forward gear G7 the second shifting element K2 designed as a clutch, the third shifting element K3 designed as a clutch and the fifth shifting element B1 designed as a brake are closed.
- the third shifting element K3 designed as a clutch, the fifth shifting element B1 designed as a brake and the sixth shifting element B2 designed as a brake are closed.
- the ninth forward gear G9 designed as a clutch first switching element K1, designed as a clutch third switching element K3 and executed as a brake fifth switching element B1 are closed.
- the reverse gear R the first shifting element K1 designed as a clutch, the fourth shifting element K4 designed as a clutch and the fifth shifting element B1 designed as a brake are closed.
- the third shifting element K3 designed as a clutch the fourth shifting element K4 designed as a clutch and the fifth shifting element B1 designed as a brake are closed.
- the alternative fourth forward gear M2 are designed as a clutch third switching element K3, as Clutch executed fourth switching element K4 and executed as a brake sixth switching element B2 closed.
- the first shifting element K1 designed as a clutch the third shifting element K3 designed as a clutch and the fourth shifting element K4 designed as a clutch are closed.
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013202895.4A DE102013202895A1 (en) | 2013-02-22 | 2013-02-22 | Multi-speed transmission in planetary construction |
PCT/EP2014/051162 WO2014127940A1 (en) | 2013-02-22 | 2014-01-22 | Multi-stage planetary transmission |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2959183A1 true EP2959183A1 (en) | 2015-12-30 |
Family
ID=49999957
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP14701079.7A Withdrawn EP2959183A1 (en) | 2013-02-22 | 2014-01-22 | Multi-stage planetary transmission |
Country Status (5)
Country | Link |
---|---|
US (1) | US9581223B2 (en) |
EP (1) | EP2959183A1 (en) |
CN (1) | CN105026794B (en) |
DE (1) | DE102013202895A1 (en) |
WO (1) | WO2014127940A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6061099B2 (en) * | 2014-01-28 | 2017-01-18 | マツダ株式会社 | Automatic transmission |
SE538187C2 (en) | 2014-03-20 | 2016-03-29 | Scania Cv Ab | A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code |
SE539661C2 (en) | 2014-03-20 | 2017-10-24 | Scania Cv Ab | Method for starting an internal combustion engine of a hybrid drive line, vehicles with such an internal combustion engine, computer programs for starting such an internal combustion engine, and a computer program product comprising program code |
SE539028C2 (en) | 2014-03-20 | 2017-03-21 | Scania Cv Ab | Procedure for driving a vehicle with a hybrid drivetrain, vehicles with such a hybrid drivetrain, computer programs for controlling a vehicle's driving, and a computer software product comprising program code |
SE539662C2 (en) | 2014-03-20 | 2017-10-24 | Scania Cv Ab | Method of starting an internal combustion engine in a hybrid drive line, vehicles with such a hybrid drive line, computer programs for starting an internal combustion engine, and a computer program product including program code |
SE540693C2 (en) * | 2014-03-20 | 2018-10-09 | Scania Cv Ab | A method for controlling a hybrid driver, vehicles with such a hybrid driver, computer programs for controlling such a hybrid driver, and a computer software product comprising program code |
DE102014216465A1 (en) * | 2014-08-20 | 2016-02-25 | Bayerische Motoren Werke Aktiengesellschaft | hybrid transmission |
DE102018218183A1 (en) * | 2018-10-24 | 2020-04-30 | Robert Bosch Gmbh | Power shiftable multi-speed transmission |
DE102019204909B4 (en) * | 2019-04-05 | 2022-10-20 | Zf Friedrichshafen Ag | Transmission, transmission assembly and drive train |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6617175B1 (en) * | 2002-05-08 | 2003-09-09 | Advanced Technology Materials, Inc. | Infrared thermopile detector system for semiconductor process monitoring and control |
US7025692B2 (en) * | 2004-02-05 | 2006-04-11 | Callaway Golf Company | Multiple material golf club head |
US6994649B2 (en) * | 2004-03-24 | 2006-02-07 | General Motors Corporation | Wide ratio transmissions having three gear sets and a stationary planetary member |
US7059994B2 (en) * | 2004-05-10 | 2006-06-13 | General Motors Corporation | Wide ratio transmissions with a fixed interconnecting member and a stationary planetary member |
US7153232B2 (en) * | 2004-07-28 | 2006-12-26 | General Motors Corporation | Planetary transmissions having a stationary member and an input member |
DE102007014150A1 (en) | 2007-03-23 | 2008-09-25 | EGS Entwicklungsgesellschaft für Getriebesysteme mbH | Power-shiftable multi-speed transmission |
CN101265958B (en) * | 2007-06-07 | 2010-11-17 | 黄庆培 | Multiple-speed gear-box |
US8113977B2 (en) * | 2007-10-12 | 2012-02-14 | GM Global Technology Operations LLC | Eight and nine speed automatic transmissions |
US8353803B2 (en) * | 2008-08-07 | 2013-01-15 | Honda Motor Co., Ltd. | Automatic transmission |
JP5138500B2 (en) | 2008-08-07 | 2013-02-06 | 本田技研工業株式会社 | Automatic transmission |
JP4757327B2 (en) * | 2009-06-04 | 2011-08-24 | 本田技研工業株式会社 | Automatic transmission |
JP5184456B2 (en) * | 2009-07-10 | 2013-04-17 | 本田技研工業株式会社 | Automatic transmission |
JP5087746B2 (en) * | 2010-06-15 | 2012-12-05 | ジヤトコ株式会社 | Automatic transmission |
US8277355B2 (en) * | 2010-07-07 | 2012-10-02 | GM Global Technology Operations LLC | Multi-speed transmission having stacked planetary gear sets |
JP2012127398A (en) * | 2010-12-14 | 2012-07-05 | Honda Motor Co Ltd | Automatic transmission |
JP2012127399A (en) * | 2010-12-14 | 2012-07-05 | Honda Motor Co Ltd | Automatic transmission |
US8343007B2 (en) | 2011-01-31 | 2013-01-01 | GM Global Technology Operations LLC | Compact multi-speed automatic transmission |
-
2013
- 2013-02-22 DE DE102013202895.4A patent/DE102013202895A1/en not_active Withdrawn
-
2014
- 2014-01-22 CN CN201480009896.8A patent/CN105026794B/en not_active Expired - Fee Related
- 2014-01-22 WO PCT/EP2014/051162 patent/WO2014127940A1/en active Application Filing
- 2014-01-22 EP EP14701079.7A patent/EP2959183A1/en not_active Withdrawn
- 2014-01-22 US US14/769,625 patent/US9581223B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
CN105026794A (en) | 2015-11-04 |
US20160131227A1 (en) | 2016-05-12 |
WO2014127940A1 (en) | 2014-08-28 |
US9581223B2 (en) | 2017-02-28 |
CN105026794B (en) | 2018-05-22 |
DE102013202895A1 (en) | 2014-08-28 |
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