WO2014069721A1 - 자동 변속기의 파워 트레인 - Google Patents
자동 변속기의 파워 트레인 Download PDFInfo
- Publication number
- WO2014069721A1 WO2014069721A1 PCT/KR2013/001248 KR2013001248W WO2014069721A1 WO 2014069721 A1 WO2014069721 A1 WO 2014069721A1 KR 2013001248 W KR2013001248 W KR 2013001248W WO 2014069721 A1 WO2014069721 A1 WO 2014069721A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- planetary gear
- power train
- automatic transmission
- rotating element
- clutch
- Prior art date
Links
Images
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
-
- 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
- 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
- F16H3/663—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another with conveying rotary motion between axially spaced orbital gears, e.g. RAVIGNEAUX
-
- 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
- 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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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
- F16H2200/2002—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
- F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set
-
- 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
- F16H2200/2048—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with seven engaging means
-
- 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
- F16H2200/2079—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches
- F16H2200/2082—Transmissions using gears with orbital motion using freewheel type mechanisms, e.g. freewheel clutches one freewheel mechanisms
Definitions
- the present invention relates to a power train of an automatic transmission, and more particularly, comprising seven rotary elements with two planetary gearsets including an input and an output, and three rotary elements with four clutches and three brakes. It is related to the power train of the automatic transmission, which is selected and tightened to enable 9 forward and 1 reverse gears.
- the automatic transmission in which the gear is automatically shifted according to the traveling speed is to remove the clutch and automatically obtain the optimum torque conversion.
- a torque converter and a planetary gear are used.
- the present invention has been made in view of this point, by using the two planetary gear set to configure the seven rotary elements, and by using the four clutch and the three brakes to select the three rotary elements by fastening, 9 forward and Its purpose is to provide a power train for an automatic transmission that is capable of forming a reverse stage.
- the power train of the automatic transmission according to the present invention for achieving this object includes three rotary elements that are continuously rotated, the outer first rotary element 110 is always connected to the input shaft (IN), A first planetary gear set 100 configured such that the second rotary element 120 and the third rotary element 130 are interrupted by the brakes B1 and B2 and the clutches C1 and C2, respectively; And first to fourth rotary elements 210 to 240 that are rotationally connected, wherein the first rotary element 210 is connected to the input shaft IN through the clutch C3 and the second rotary element 220 is connected to the input shaft IN.
- the third rotary element 230 is interrupted by the brake (B3) and the clutch (C4), the fourth rotary element 240 is mediated by the clutch (C1, C2) It characterized in that it comprises a; second planetary gear set 200 connected to.
- the first planetary gear set 100 may be a single pinion planetary gear or a double pinion planetary gear.
- the second planetary gear set 200 is a combination of two planetary planetary planetary gear, Simpson planetary gear, two-simple planetary gear, or laminated planetary gear.
- the power train of the automatic transmission of the present invention by reducing the number of elements of the automatic transmission required to implement the 9 forward and 1 reverse, the weight, cost and number of parts can be reduced, as well as the compact structure, and the mountability is improved. It can improve the performance and efficiency of the automatic transmission due to the multi-stage.
- FIG. 1 is a schematic view showing the configuration of a power train according to a first embodiment of the present invention.
- Figure 4 is a schematic diagram showing the configuration of a power train according to a second embodiment of the present invention.
- FIG. 5 is a graph showing speed diagrams of a power train according to Embodiment 2 of the present invention.
- FIG. 6 is a graph showing speed diagrams for the first to third speed shifts of the power train according to Embodiment 2 of the present invention.
- FIG. 7 is a schematic view showing the configuration of a power train according to Embodiment 3 of the present invention.
- FIG. 8 is a schematic view showing the configuration of a power train according to Embodiment 4 of the present invention.
- the present invention consists of seven rotating elements using two planetary gear sets, and three of the rotating elements are selectively fastened by three brakes and four brakes so that the 9 forward and 1 reverse stages are performed. It was made possible.
- any one of the planetary gearsets may use a single pinion planetary gear or a double pinion planetary gear
- the other planetary gearset may be a combination of two planetary gear planetary gears, a Simpson planetary gear, a two-simple planetary gear, or A laminated planetary gear can be used.
- the power train according to the first embodiment of the present invention comprises a first planetary gear set 100 and the second planetary gear set 200.
- the first and second planetary gear sets 100 and 200 are selectively connected and interrupted by three brakes B1 to B3 and four clutches C1 to C4.
- first to third rotary elements 110 to 130 are driven to be engaged with each other.
- first first rotary element 110 is always connected to the input shaft IN. do.
- the "outer side" may be a planetary gear sun gear as the component having the fastest rotation speed.
- the second rotation element 120 and the third rotation element 130 are interrupted by the transmission and power of the power by the brake (B1, B2) and the clutch (C1, C2), respectively.
- the second rotating element 120 and the third rotating element 130 may be a carrier and a ring gear of the planetary gear.
- the second planetary gear set 200 includes first to fourth rotating elements 210 to 240.
- the outer first rotating element 210 is directly connected to the input shaft IN via the clutch C3.
- the fourth rotating element 240 which is another outer side, is connected to the first planetary gear set 100 through the clutches C1 and C2.
- a second rotating element 220 and a third rotating element 230 are installed at an inner side between these outer sides.
- the second rotating element 220 is directly connected to the output shaft OUT.
- the third rotary element 230 is selectively interrupted in power by the brake B3 and the clutch C4.
- the power train according to the present invention made as described above is operated by the clutches C1 to C4 and the brakes B1 to B3 as shown in Table 1 below.
- the gear shift state of the stage is shown.
- the speed diagram shifted by the restraint of the clutches C1 to C4 and the brakes B1 to B3 is as shown in FIG. 3.
- the present invention can be seen that the shift state of the 9 forward and 1 reverse.
- the change in the speed diagram is indicated by a thick line, and the gear shifting of the 9 forward and 1 reverse stages is performed by the operation of the clutches C1 to C4 and the brakes B1 to B3 in the speed diagram.
- the second planetary gear set has been described only in the case of a laminated planetary gear, the same effect can be obtained even if the application of the Labyrinth planetary gear, Simpson planetary gear or two-simple planetary gear.
- the one-way clutch OWC is further added to the inner rotary element constituting the first planetary gearset 100, that is, the second rotary element 120. It is made up.
- the one-way clutch as shown in the following [Table 2], it is preferable to be able to restrain the starting slip, etc. by allowing the second rotary element 120 to be constrained in the first stage. .
- FIG. 5 shows speed diagrams obtained as the respective clutches C1 to C4, the brakes B1 to B3 and the one-way clutch OWC operate as shown in Table 2 above.
- Example 2 as in [Table 1] and [Table 2], it is performed in the same manner as in Example 1 except for the case of the first gear shifting speed three shifts. Therefore, the speed diagram of the shift stage different from the first embodiment is shown in FIG.
- a single pinion planetary gear 100 ′ is applied in place of the first planetary gearset as a planetary gearset, and a stacked type is substituted for the second planetary gearset.
- the example in which the planetary gear 200 'is applied is shown.
- the single pinion planetary gear 100 ′ is a single planetary gear and includes three rotating elements, that is, a sun gear S1, a ring gear R1, and a carrier Ca1.
- the sun gear S1 is connected to the input shaft IN.
- the ring gear R1 and the carrier Ca1 are constrained to be powered and shut off by the brakes B1 and B2 and the clutches C1 and C2, respectively.
- the brakes B1 and B2 and the clutches C1 and C2 restrain the ring gear R1 and the carrier Ca1 such that the same operation as in the first embodiment can be achieved.
- the stacked planetary gear 200 ′ has a structure in which a pair of single planetary gears are stacked, and has four rotating elements. That is, since the planetary gear is substantially a pair, it is composed of six rotating elements. Among them, one pair of carriers Ca2 and Ca3 rotates at the same time, and the ring-sun gear RS composed of any one ring gear and the sun gear operates simultaneously. Done.
- the carrier is a component for fixing a plurality of planetary gears.
- the ring sun gear R-S is selectively powered by the clutch C3 from the input shaft IN.
- the pair of carriers Ca2 and Ca3 are configured to rotate together as described above, and the output shaft OUT is connected, and the carriers Ca2 and Ca3 are engaged with the ring sun gear R-S to rotate.
- a ring gear R2 is engaged with the carrier Ca2.
- the ring gear R2 transmits and cuts off power by the brake B3 and the clutch C4.
- the clutch C4 is configured such that the ring gear R2 transmits and cuts power from the input shaft IN. It works.
- the sun gear S2 is meshed with the other carrier Ca3. At this time, the sun gear S2 receives power through the clutches C1 and C2 of the single pinion planetary gear 100 'described above.
- the power train of the third embodiment thus constructed is substantially the same as the configuration of the above-described first embodiment, so that the shifting of the forward 9 gears and the reverse 1 gears is possible even in the speed diagram.
- the power train according to the fourth embodiment of the present invention uses a double pinion planetary gear 100 "and a laminated planetary gear 200 'as shown in Fig. 8.
- the structure of the laminated planetary gear 200' is described above. Since it is the same as Example 3, the detailed description is abbreviate
- the double pinion planetary gear 100 "includes a carrier C, a sun gear S1, and a ring gear R.
- the sun gear S1 has the same configuration as in the third embodiment, here it is. The detailed description is omitted.
- the ring gear R is configured in the same manner as in the above-described third embodiment, but is further provided with a one-way clutch OWC to prevent slippage when starting.
- the carrier C is formed in a pair, and is selectively interrupted by the clutch C1 as in the third embodiment, and outputs the output to the stacked planetary gear 200 '. Since the carrier C has the same configuration as the above-described embodiment except that the carrier C is configured in pairs, detailed description thereof will be omitted here.
- the present invention configures seven rotating elements through two planetary gear sets, and operates three rotating elements using three brakes and four clutches, so that the multishifting of the 9 forward and 1 reverse stages is performed. It becomes possible.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
단수 | CLUTCH | BRAKE | |||||
C1 | C2 | C3 | C4 | B1 | B2 | B3 | |
1 | ○ | ○ | ○ | ||||
2 | ○ | ○ | ○ | ||||
3 | ○ | ○ | ○ | ||||
4 | ● | ◆ | ○ | ● | ◆ | ||
5 | ○ | ○ | ○ | ||||
6 | ○ | ○ | ○ | ||||
7 | ○ | ○ | ○ | ||||
8 | ● | ◆ | ○ | ● | ◆ | ||
9 | ○ | ○ | ○ | ||||
R | ○ | ○ | ○ | ||||
◆와 ●는 같은 모양끼리 체결하여 변속단이 형성됨 |
단수 | CLUTCH | BRAKE | ||||||
C1 | C2 | C3 | C4 | B1 | B2 | B3 | OWC | |
1 | ○ | ○ | ○ | ○ | ||||
2 | ○ | ○ | ○ | |||||
3 | ○ | ○ | ○ | |||||
4 | ● | ◆ | ○ | ● | ◆ | |||
5 | ○ | ○ | ○ | |||||
6 | ○ | ○ | ○ | |||||
7 | ○ | ○ | ○ | |||||
8 | ● | ◆ | ○ | ● | ◆ | |||
9 | ○ | ○ | ○ | |||||
R | ○ | ○ | ○ | |||||
◆와 ●는 같은 모양끼리 체결하여 변속단이 형성됨 |
Claims (5)
- 연속해서 회전연결되는 3개의 회전요소를 포함하되, 외측의 제1회전요소(110)가 입력축(IN)에 항시 연결되고, 제2회전요소(120)와 제3회전요소(130)가 각각 브레이크(B1,B2)와 클러치(C1,C2)에 의해 단속되도록 구성된 제1유성기어셋(100); 및회전연결되는 제1 내지 제4회전요소(210~240)를 포함하되, 외측의 제1회전요소(210)가 클러치(C3)를 통해 입력축(IN)에 연결되며, 제2회전요소(220)가 출력축(OUT)에 항시 연결되고, 제3회전요소(230)가 브레이크(B3)와 클러치(C4)에 의해 단속되며, 제4회전요소(240)가 상기 클러치(C1,C2)를 매개로 연결된 제2유성기어셋(200);을 포함하는 것을 특징으로 하는 자동 변속기의 파워 트레인.
- 제 1 항에 있어서,상기 제1유성기어셋(100)은 싱글 또는 더블 피니언 유성기어이고,상기 제2유성기어셋(200)은, 2개의 유성기어가 조합된 라비뉴 유성기어·투심플 유성기어·심프슨 유성기어 또는 적층형 유성기어인 것을 특징으로 하는 자동 변속기의 파워 트레인.
- 제 3 항에 있어서,내측의 회전요소(120,130) 중에서 적어도 하나에는 원웨이 클러치(OWC)와 연결된 것을 특징으로 하는 자동 변속기의 파워 트레인.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201380056775.4A CN104755809B (zh) | 2012-10-31 | 2013-02-18 | 自动变速器的动力传动系统 |
US14/439,588 US9714692B2 (en) | 2012-10-31 | 2013-02-18 | Power train of automatic transmission |
DE112013005219.9T DE112013005219T5 (de) | 2012-10-31 | 2013-02-18 | Antriebsstrang eines Automatikgetriebes |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
KR10-2012-0122123 | 2012-10-31 | ||
KR1020120122123A KR101334519B1 (ko) | 2012-10-31 | 2012-10-31 | 자동 변속기의 파워 트레인 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2014069721A1 true WO2014069721A1 (ko) | 2014-05-08 |
Family
ID=49858784
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/KR2013/001248 WO2014069721A1 (ko) | 2012-10-31 | 2013-02-18 | 자동 변속기의 파워 트레인 |
Country Status (5)
Country | Link |
---|---|
US (1) | US9714692B2 (ko) |
KR (1) | KR101334519B1 (ko) |
CN (1) | CN104755809B (ko) |
DE (1) | DE112013005219T5 (ko) |
WO (1) | WO2014069721A1 (ko) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013225202B4 (de) * | 2013-12-06 | 2019-01-10 | Zf Friedrichshafen Ag | Getriebe für ein Kraftfahrzeug |
DE102017204548A1 (de) * | 2017-03-20 | 2018-09-20 | Zf Friedrichshafen Ag | Getriebe für ein Kraftfahrzeug |
KR102398888B1 (ko) * | 2017-07-12 | 2022-05-18 | 현대자동차주식회사 | 다단 변속기 |
EP4056872A1 (en) * | 2021-03-12 | 2022-09-14 | Volvo Truck Corporation | A transmission for a vehicle |
Citations (5)
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JPH10311386A (ja) * | 1997-05-08 | 1998-11-24 | Jatco Corp | 自動変速機用歯車変速装置 |
KR100644482B1 (ko) * | 2005-02-03 | 2006-11-10 | 현대자동차주식회사 | 차량용 자동변속기의 6속 파워 트레인 |
JP2008286294A (ja) * | 2007-05-17 | 2008-11-27 | Honda Motor Co Ltd | 変速装置 |
KR20080105540A (ko) * | 2007-05-31 | 2008-12-04 | 현대 파워텍 주식회사 | 자동 변속기의 4속 파워 트레인 |
JP2009174643A (ja) * | 2008-01-24 | 2009-08-06 | Honda Motor Co Ltd | 自動変速機 |
Family Cites Families (9)
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US7442145B2 (en) * | 2006-06-02 | 2008-10-28 | Gm Global Technology Operations, Inc. | Multi-Speed transmissions with a long pinion |
GB2440347B (en) * | 2006-07-27 | 2011-02-23 | Ford Global Tech Llc | An automatic transmission for motor vehicles |
KR100867695B1 (ko) * | 2006-12-13 | 2008-11-10 | 현대자동차주식회사 | 자동변속기의 7속 파워트레인 |
KR100916774B1 (ko) * | 2007-11-02 | 2009-09-14 | 현대자동차주식회사 | 자동변속기의 파워 트레인 |
US8251849B2 (en) * | 2008-12-19 | 2012-08-28 | GM Global Technology Operations LLC | Clutching method and mechanism for electrically variable transmissions |
DE102010042656B4 (de) * | 2010-10-20 | 2022-06-23 | Zf Friedrichshafen Ag | Lastschaltbares Getriebe |
US8419585B2 (en) * | 2011-01-05 | 2013-04-16 | GM Global Technology Operations LLC | Multi-speed transmission having stacked planetary gear sets |
US8343007B2 (en) * | 2011-01-31 | 2013-01-01 | GM Global Technology Operations LLC | Compact multi-speed automatic transmission |
US9689470B2 (en) * | 2014-03-21 | 2017-06-27 | GM Global Technology Operations LLC | Multi-speed transmission |
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2012
- 2012-10-31 KR KR1020120122123A patent/KR101334519B1/ko active IP Right Grant
-
2013
- 2013-02-18 DE DE112013005219.9T patent/DE112013005219T5/de not_active Withdrawn
- 2013-02-18 CN CN201380056775.4A patent/CN104755809B/zh not_active Expired - Fee Related
- 2013-02-18 WO PCT/KR2013/001248 patent/WO2014069721A1/ko active Application Filing
- 2013-02-18 US US14/439,588 patent/US9714692B2/en active Active
Patent Citations (5)
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JPH10311386A (ja) * | 1997-05-08 | 1998-11-24 | Jatco Corp | 自動変速機用歯車変速装置 |
KR100644482B1 (ko) * | 2005-02-03 | 2006-11-10 | 현대자동차주식회사 | 차량용 자동변속기의 6속 파워 트레인 |
JP2008286294A (ja) * | 2007-05-17 | 2008-11-27 | Honda Motor Co Ltd | 変速装置 |
KR20080105540A (ko) * | 2007-05-31 | 2008-12-04 | 현대 파워텍 주식회사 | 자동 변속기의 4속 파워 트레인 |
JP2009174643A (ja) * | 2008-01-24 | 2009-08-06 | Honda Motor Co Ltd | 自動変速機 |
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CN104755809A (zh) | 2015-07-01 |
US9714692B2 (en) | 2017-07-25 |
CN104755809B (zh) | 2018-04-24 |
US20150276021A1 (en) | 2015-10-01 |
KR101334519B1 (ko) | 2013-11-28 |
DE112013005219T5 (de) | 2015-08-06 |
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