CN102042372A - Multi-speed transmission - Google Patents
Multi-speed transmission Download PDFInfo
- Publication number
- CN102042372A CN102042372A CN2011100211333A CN201110021133A CN102042372A CN 102042372 A CN102042372 A CN 102042372A CN 2011100211333 A CN2011100211333 A CN 2011100211333A CN 201110021133 A CN201110021133 A CN 201110021133A CN 102042372 A CN102042372 A CN 102042372A
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- China
- Prior art keywords
- gear
- planetary gear
- gear set
- fixed axis
- planet carrier
- Prior art date
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/04—Combinations of toothed gearings only
- F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
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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
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0056—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising seven forward speeds
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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
- F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two 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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- 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
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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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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention discloses a multi-speed transmission which is applicable to a front driving truck. The multi-speed transmission comprises an input shaft, an output component, an auxiliary shaft, two planetary gear sets, two stationary shaft gear sets and five engaging elements, wherein a driven gear of the first stationary shaft gear set and a driving gear of the second stationary shaft gear set are connected so as to form the auxiliary shaft; a sun gear and a planet carrier of the second planetary gear set are respectively connected with the input shaft and the output component; the gear rings of the first and second planetary gear sets are respectively connected with a driving gear of the first stationary shaft gear set and a driven gear of the second stationary shaft gear set; the first and third engaging elements are respectively connected in series between a sun gear of the first planetary gear set and the input shaft and between a and a planet carrier of the first planetary gear set and the input shaft; the second engaging element is connected in series between the sun gear of the first planetary gear set and the planet carrier of the second planetary gear set; the fourth engaging element is selectively or rotatably connected with the planet carrier of the first planetary gear set and the gear ring of the second planetary gear set; and the fifth engaging element optionally brakes the planet carrier of the first planetary gear set. The multi-speed transmission is provided with a seven-forward and one-astern stage gearshift.
Description
Technical field
The present invention relates to be used for the multiple-speed gear-box field of automobile, be specifically related to comprise the multistage automatic transmission of a plurality of planetary gear set and gear-changing component.
Background technique
Early stage three, level Four speed change that progressively the popularizing of Pyatyi, six grades of automatic transmission will replace gradually.Existing six grades of speed changers generally comprise three planetary gear set and five gear-changing components (clutch and break), seven or general minimum three planetary gear set and six gear-changing components of comprising of 8-speed transmission, perhaps four planetary gear set and five gear-changing components, as: Chinese patent publication number CN1860314, CN1531634, CN1650119, CN101191535, CN101846160A, CN101235879, CN101275644, CN101103212, CN101354072, CN101275631 etc.The planetary gear set of these speed changers, gear-changing component all are arranged on the same axis, and the axial length of speed changer is longer, are not suitable for the automobile of preposition forerunner, lateral arrangement speed changer, have hindered them and have been widely used.
" eight speed automatic transmission of band planetary gear system and counter shaft gear device " of " Powershift multistep transmission " of Chinese patent publication number CN101275630, CN101334094, " 8-speed transmission " of CN101392817, CN101392819 etc. comprise three planetary gear set, five gear-changing components and three fixed axis gear groups, the automobile that is used for preposition forerunner, lateral arrangement speed changer, but its volume weight is bigger." the AUTOMATIC TRANSMISSION " of U.S. Patent application US20100035718A1 comprises that two planetary gear set, two fixed axis gear groups, five gear-changing components can realize six grades of speed changes, or increase a gear-changing component and can realize eight grades of speed changes, its all planetary gear set and gear-changing component are arranged on the main shaft.
Summary of the invention
The invention provides the technical problem that a kind of multiple-speed gear-box will solve is: the speed changer that comprises two planetary gear set, five gear-changing components, two fixed axis gear groups has seven grades and advances and one-level reversing speed change, increase a fixed axis gear group on this basis, can improve the distribution of the speed change ratio of each gear, the layout of optimization clutch shift element, further shorten axial distance.With less elements, than short axial distance, realize more number of steps of speeds, help popularization and application on the automobile of preposition lateral arrangement speed changer.
Technological scheme of the present invention is: a kind of multiple-speed gear-box comprises input shaft, output block, countershaft, housing, be first and second planetary gear set of single pinion type, be the first and second fixed axis gear groups, first to the 5th clutch shift element of outer gearing type; Described first and second planetary gear set are arranged on the axis of input shaft;
The described first and second fixed axis gear groups have driving wheel, follower separately respectively, the follower of the driving wheel of the described first fixed axis gear group and the second fixed axis gear group is arranged on the axis of input shaft, the driving wheel of the follower of the described first fixed axis gear group and the second fixed axis gear group interconnects, and its coupling shaft constitutes countershaft;
The sun gear of described second planetary gear set, planet carrier are connected with described input shaft, output block respectively;
The driving wheel of the gear ring of described first planetary gear set and the described first fixed axis gear group interconnects, and the follower of the gear ring of described second planetary gear set and the described second fixed axis gear group interconnects;
Selectively be connected both between the sun gear that described first clutch gear-changing component is serially connected in described first planetary gear set and the described input shaft; Selectively be connected both between the sun gear that described second clutch gear-changing component is serially connected in described first planetary gear set and the planet carrier of described second planetary gear set; Selectively be connected both between the planet carrier that described three-clutch gear-changing component is serially connected in described first planetary gear set and the described input shaft;
Described four clutches gear-changing component has two kinds of plans of establishment: scheme one, selectively be connected both between the planet carrier that directly is serially connected in described first planetary gear set and the gear ring of described second planetary gear set, when described four clutches gear-changing component in conjunction with the time planet carrier of described first planetary gear set and described second planetary gear set the rotating ratio of gear ring equal 1; Scheme two, speed changer also comprises driving wheel, follower is arranged in input shaft, the 3rd fixed axis gear group on the layshaft axis, described four clutches gear-changing component is serially connected between the gear ring of the planet carrier of described first planetary gear set and described second planetary gear set and selectively is in transmission connection both through on the route that is in transmission connection of countershaft, described " through the route that is in transmission connection of countershaft " is the master by described the 3rd fixed axis gear group, follower, described countershaft, the master of the described second fixed axis gear group, the planet carrier of described first planetary gear set that follower forms is to the drive path of the gear ring of described second planetary gear set, between the driving wheel of described four clutches gear-changing component or the planet carrier that is serially connected in described first planetary gear set and described the 3rd fixed axis gear group and the follower of described the 3rd fixed axis gear group be connected with countershaft, between the follower that perhaps is serially connected in described the 3rd fixed axis gear group and the countershaft and the planet carrier of described first planetary gear set be connected with the driving wheel of described the 3rd fixed axis gear group, when described four clutches gear-changing component in conjunction with the time, the rotating ratio of the gear ring of the planet carrier of described first planetary gear set and described second planetary gear set can be not equal to 1, though scheme two is complicated a little, but can improve the distribution of the speed change ratio of each gear of speed changer, make between shelves better than (ratio between the adjacent gear gear ratio), the four clutches gear-changing component also can be arranged on the countershaft;
Described the 5th clutch shift element or be serially connected between the planet carrier and described housing of described first planetary gear set, perhaps in such scheme two, the 5th clutch shift element is serially connected between the follower and described housing of the 3rd fixed axis gear group, the planet carrier that the 3rd fixed axis gear group, the 5th clutch shift element form first planetary gear set is to the route that is in transmission connection between the housing, and the 5th clutch shift element is selectively braked the planet carrier of described first planetary gear set;
In addition, can also comprise overrunning clutch, described overrunning clutch or be serially connected in the planet carrier of described first planetary gear set and described housing between or be attempted by the two ends of described the 5th clutch shift element, its effect is to allow the planet carrier of described first planetary gear set to the identical sense of rotation rotation of described input shaft, and locking does not allow the planet carrier of described first planetary gear set to the opposite sense of rotation rotation of described input shaft.
Beneficial effect of the present invention is: existing multiple-speed gear-box is one group of key element of increase and decrease (as: planetary gear set or two fixed axis gear groups or a gear-changing component), two speed change levels of changeable usually; For example: general minimum two planetary gear set and five gear-changing components of comprising of existing level Four speed changer, and a kind of six grades of speed changers comprise three planetary gear set and five gear-changing components, perhaps comprise two planetary gear set, five gear-changing components and two fixed axis gear groups, the present invention has seven grades of speed changes of advancing by comparison.And for example: existing three planetary gear set, five gear-changing components of comprising are compared with the 8-speed transmission of three fixed axis gear groups, the few planetary gear set of the present invention, and have seven grades advance, one-level reversing speed change, higher cost performance is arranged.
Description of drawings
Fig. 1 is embodiment one a schematic diagram
Fig. 2 is embodiment two a schematic diagram
Description of reference numerals is as follows:
1: input shaft
2: output block
3: countershaft
5: housing
8: the route that is in transmission connection of process countershaft between the gear ring of the planet carrier of described first planetary gear set and described second planetary gear set
9: the route that is in transmission connection between the planet carrier of described first planetary gear set and the housing
10: the first planetary gear set
The sun gear of 11: the first planetary gear set
The planet carrier of 12: the first planetary gear set
The gear ring of 13: the first planetary gear set
20: the second planetary gear set
The sun gear of 21: the second planetary gear set
The planet carrier of 22: the second planetary gear set
The gear ring of 23: the second planetary gear set
30: the first fixed axis gear groups
The driving wheel of 31: the first fixed axis gear groups
The follower of 32: the first fixed axis gear groups
40: the second fixed axis gear groups
The driving wheel of 41: the second fixed axis gear groups
The follower of 42: the second fixed axis gear groups
50: the three fixed axis gear groups
The driving wheel of 51: the three fixed axis gear groups
The follower of 52: the three fixed axis gear groups
61 to 65: the first to the 5th clutch shift element
71: overrunning clutch.
Embodiment
Embodiment one:As Fig. 1, described first planetary gear set 10, second planetary gear set 20 are single pinion type planetary gear set, are arranged on the axis of input shaft 1;
The driving wheel 31 of the described first fixed axis gear group 30 and the follower 42 of the second fixed axis gear group 40 are arranged on the axis of input shaft 1, and are connected with the gear ring 13 of described first planetary gear set 10 and the gear ring 23 of described second planetary gear set 20 respectively;
The follower 32 of the described first fixed axis gear group 30 and the driving wheel 41 of the second fixed axis gear group 40 interconnect, and its coupling shaft constitutes countershaft 3;
The sun gear 21 of described second planetary gear set 20, planet carrier 22 are connected with described input shaft 1, output block 2 respectively;
Selectively be connected both between the sun gear 11 that described first clutch gear-changing component 61 is serially connected in described first planetary gear set 10 and the described input shaft 1; Selectively be connected both between the sun gear 11 that described second clutch gear-changing component 62 is serially connected in described first planetary gear set 10 and the planet carrier 22 of described second planetary gear set 20; Selectively be connected both between the planet carrier 12 that described three-clutch gear-changing component 63 is serially connected in described first planetary gear set 10 and the described input shaft 1;
Selectively be connected both between the planet carrier 12 that described four clutches gear-changing component 64 is serially connected in described first planetary gear set 10 and the gear ring 23 of described second planetary gear set 20;
Described the 5th clutch shift element 65 is serially connected in the planet carrier 12 of selectively braking described first planetary gear set 10 between the planet carrier 12 of described first planetary gear set 10 and the described housing 5.
If get gear ring 13, the gear ratio between the sun gear 11: the K of first planetary gear set 10
10The gear ring 23 of=1.909, second planetary gear set 20, the gear ratio between the sun gear 21: K
20The gear ratio of the driven wheel 31,32 of=2.048, the first fixed axis gear group 30 multiply by the gear ratio of the driven wheel 41,42 of the second fixed axis gear group 40:
Z
31/ Z
32* Z
41/ Z
42=1.555, the then marriage relation of each gear of speed changer and gear-changing component, gear ratio situation such as following table, " ● " expression clutch shift combination of elements in the table, blank expression separates:
In addition, all right also order is to clutch 71 at the two ends of the 5th clutch shift element 65, overrunning clutch 71 allows the planet carrier 12 of described first planetary gear set 10 to rotate to input shaft 1 identical sense of rotation, locking does not allow planet carrier 12 to rotate to input shaft 1 opposite sense of rotation, like this when automobile when urban road travels, first, second shelves of low speed can be in conjunction with the 5th clutch shift element 65, automobile slide when receiving throttle, do not produce engine braking, the pause and transition in rhythm or melody sense when eliminating low speed driving; And under the engine braking pattern, first, second shelves can utilize engine braking to improve the safety of descent run in conjunction with the 5th clutch shift element 65.
Embodiment two:As Fig. 2, be with embodiment one the main distinction: increased by the 3rd fixed axis gear group 50, its driving wheel 51 and follower 52 are arranged on the axis of input shaft 1 and countershaft 3, four clutches gear-changing component 64 is not directly to be serially connected between the gear ring 23 of the planet carrier 12 of first planetary gear set 10 and second planetary gear set 20, but be serially connected in planet carrier 12 through the 3rd fixed axis gear group 50, countershaft 3, the second fixed axis gear group 40 is in transmission connection on the route 8 that is in transmission connection of gear ring 23 of second planetary gear set 20, what Fig. 2 was shown is that four clutches gear-changing component 64 is serially connected between the follower 52 and countershaft 3 of the 3rd fixed axis gear group 50, planet carrier 12 is connected with the driving wheel 51 of the 3rd fixed axis gear group 50, like this when four clutches gear-changing component 64 in conjunction with the time, rotating ratio between planet carrier 12 and the gear ring 23 no longer equals one, and this point is different with embodiment one; The 5th clutch shift element 65 is also different with embodiment one, is to be serially connected between the follower 52 and housing 5 of the 3rd fixed axis gear group 50; Four, the 5th clutch shift element 64,65 is arranged on the axis of countershaft 3, helps optimizing each component placement, further shortens axial distance.
Get gear ring 13, the gear ratio between the sun gear 11: the K of first planetary gear set 10
10The gear ring 23 of=1.909, second planetary gear set 20, the gear ratio between the sun gear 21: K
20The gear ratio of the driven wheel 31,32 of=2.048, the first fixed axis gear group 30 multiply by the gear ratio of the driven wheel 41,42 of the second fixed axis gear group 40:
Z
31/ Z
32* Z
41/ Z
42The gear ratio of the driven wheel 51,52 of the=1.555, the 3rd fixed axis gear group 50 multiply by the gear ratio of the driven wheel 41,42 of the second fixed axis gear group 40: Z
51/ Z
52* Z
41/ Z
42=1.0526, the then marriage relation of each gear of speed changer and gear-changing component, gear ratio situation such as following table:
Contrast two embodiments, in first, second planetary gear set 10,20, under all identical situation of the tooth ratio of first, second fixed axis gear group 30,40, total ratio is also identical between two embodiments' shelves, but embodiment two has between better shelves than distributing.
Can increase the planet carrier 12 that is serially connected in first planetary gear set 10 and the overrunning clutch 71 between the described housing 5, its effect is identical with embodiment one.
Claims (3)
1. a multiple-speed gear-box comprises input shaft (1), output block (2), countershaft (3), housing (5), first and second planetary gear set (10,20), the first and second fixed axis gear groups (30,40), first to the 5th clutch shift element (61,62,63,64,65); It is characterized in that: described first and second planetary gear set (10,20) are single pinion type planetary gear set, and separately sun gear (11,21), gear carrier (12,22), gear ring (13,23) are arranged respectively, and be arranged on the axis of input shaft (1);
The described first and second fixed axis gear groups (30,40) are outer gearing type gear train, and separately driving wheel (31,41), follower (32,42) are arranged respectively, the follower (42) of the driving wheel (31) of the described first fixed axis gear group (30) and the second fixed axis gear group (40) is arranged on the axis of input shaft (1), the driving wheel (41) of the follower (32) of the described first fixed axis gear group (30) and the second fixed axis gear group (40) interconnects, and its coupling shaft constitutes countershaft (3);
The sun gear (21) of described second planetary gear set (20), planet carrier (22) are connected with described input shaft (1), output block (2) respectively;
The gear ring (13) of described first planetary gear set (10) interconnects with the driving wheel (31) of the described first fixed axis gear group (30); The gear ring (23) of described second planetary gear set (20) interconnects with the follower (42) of the described second fixed axis gear group (40);
Selectively be connected both between the sun gear (11) that described first clutch gear-changing component (61) is serially connected in described first planetary gear set (10) and the described input shaft (1); Selectively be connected both between the sun gear (11) that described second clutch gear-changing component (62) is serially connected in described first planetary gear set (10) and the planet carrier (22) of described second planetary gear set (20); Selectively be connected both between the planet carrier (12) that described three-clutch gear-changing component (63) is serially connected in described first planetary gear set (10) and the described input shaft (1);
Selectively be connected both between the gear ring (23) of described four clutches gear-changing component (64) or the planet carrier (12) that is serially connected in described first planetary gear set (10) and described second planetary gear set (20), perhaps be serially connected on the route that is in transmission connection (8) that passes through countershaft (3) between the two and selectively be in transmission connection both;
Described the 5th clutch shift element (65) or be serially connected in the planet carrier (12) of described first planetary gear set (10) and described housing (5) between or be serially connected in the planet carrier (12) of selectively braking described first planetary gear set (10) between the two the route that is in transmission connection (9).
2. multiple-speed gear-box according to claim 1 also comprises the 3rd fixed axis gear group (50); It is characterized in that: described the 3rd fixed axis gear group (50) is outer gearing type gear train, and its driving wheel (51) and follower (52) are arranged on the axis of described input shaft (1) and countershaft (3); The planet carrier (12) of described first planetary gear set (10) interconnects with the driving wheel (51) of described the 3rd fixed axis gear group (50), selectively be connected both, described the 3rd fixed axis gear group (50) between the follower (52) that described four clutches gear-changing component (64) is serially connected in described the 3rd fixed axis gear group (50) and the described countershaft (3), four clutches gear-changing component (64), the route that is in transmission connection (8) between the planet carrier (12) of countershaft (3) and the second fixed axis gear group (40) described first planetary gear set of formation (10) and the gear ring (23) of described second planetary gear set (20); Described the 5th clutch shift element (65) is serially connected between the follower (52) and described housing (5) of described the 3rd fixed axis gear group (50), the planet carrier (12) that described the 3rd fixed axis gear group (50), the 5th clutch shift element (65) constitute described first planetary gear set (10) is to the route that is in transmission connection (9) between the housing (5), and described the 5th clutch shift element (65) is selectively braked the planet carrier (12) of described first planetary gear set (10).
3. multiple-speed gear-box according to claim 1 and 2 also comprises overrunning clutch (71); It is characterized in that: described overrunning clutch (71) or be serially connected in the planet carrier (12) of described first planetary gear set (10) and described housing (5) between or be attempted by the two ends of described the 5th clutch shift element (65), allow the planet carrier (12) of described first planetary gear set (10) to rotate in the same way with described input shaft (1), locking does not allow the planet carrier (12) of described first planetary gear set (10) to the opposite sense of rotation rotation of described input shaft (1).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2011100211333A CN102042372B (en) | 2011-01-07 | 2011-01-18 | Multi-speed transmission |
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110003098.2 | 2011-01-07 | ||
| CN201110003098 | 2011-01-07 | ||
| CN2011100211333A CN102042372B (en) | 2011-01-07 | 2011-01-18 | Multi-speed transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN102042372A true CN102042372A (en) | 2011-05-04 |
| CN102042372B CN102042372B (en) | 2012-10-24 |
Family
ID=43908794
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2011100211333A Expired - Fee Related CN102042372B (en) | 2011-01-07 | 2011-01-18 | Multi-speed transmission |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN102042372B (en) |
| WO (1) | WO2012092749A1 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012092749A1 (en) * | 2011-01-07 | 2012-07-12 | Huang Qingpei | Multi-speed transmission |
| CN102797809A (en) * | 2012-08-31 | 2012-11-28 | 哈尔滨东安汽车发动机制造有限公司 | Planetary gear type 6-speed automatic speed changer |
| CN103807371A (en) * | 2012-11-05 | 2014-05-21 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN105972166A (en) * | 2016-06-20 | 2016-09-28 | 裕克施乐塑料制品（太仓）有限公司 | Planetary-gear-type speed variator capable of automatic gear shifting |
| CN112392926A (en) * | 2020-12-08 | 2021-02-23 | 徐工集团工程机械股份有限公司 | Multi-stage planet carrier, multi-stage planet combined structure and multi-gear planet mechanism |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007006449A1 (en) * | 2005-07-08 | 2007-01-18 | Zf Friedrichshafen Ag | Multi-speed gearbox |
| US20080015081A1 (en) * | 2006-07-06 | 2008-01-17 | Zf Friedrichshafen Ag | Multi-speed transmission |
| CN101424316A (en) * | 2007-11-01 | 2009-05-06 | 通用汽车环球科技运作公司 | Gear and clutch arrangement for multi-speed transmission |
| CN101655141A (en) * | 2009-09-21 | 2010-02-24 | 重庆青山工业有限责任公司 | Double-clutch transmission |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP3763296B2 (en) * | 2001-12-10 | 2006-04-05 | トヨタ自動車株式会社 | Automatic transmission |
| JP4039309B2 (en) * | 2002-05-27 | 2008-01-30 | トヨタ自動車株式会社 | Automatic transmission for vehicles |
| KR100610791B1 (en) * | 2004-09-01 | 2006-08-09 | 현대자동차주식회사 | A six-speed powertrain of an automatic transmission |
| KR100793878B1 (en) * | 2006-07-11 | 2008-01-15 | 현대자동차주식회사 | A six-speed power train of an automatic transmission for a vehicle |
| JP4757327B2 (en) * | 2009-06-04 | 2011-08-24 | 本田技研工業株式会社 | Automatic transmission |
| CN102042372B (en) * | 2011-01-07 | 2012-10-24 | 广州科立源机电科技有限公司 | Multi-speed transmission |
-
2011
- 2011-01-18 CN CN2011100211333A patent/CN102042372B/en not_active Expired - Fee Related
- 2011-06-03 WO PCT/CN2011/075263 patent/WO2012092749A1/en active Application Filing
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2007006449A1 (en) * | 2005-07-08 | 2007-01-18 | Zf Friedrichshafen Ag | Multi-speed gearbox |
| US20080015081A1 (en) * | 2006-07-06 | 2008-01-17 | Zf Friedrichshafen Ag | Multi-speed transmission |
| CN101424316A (en) * | 2007-11-01 | 2009-05-06 | 通用汽车环球科技运作公司 | Gear and clutch arrangement for multi-speed transmission |
| CN101655141A (en) * | 2009-09-21 | 2010-02-24 | 重庆青山工业有限责任公司 | Double-clutch transmission |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2012092749A1 (en) * | 2011-01-07 | 2012-07-12 | Huang Qingpei | Multi-speed transmission |
| CN102797809A (en) * | 2012-08-31 | 2012-11-28 | 哈尔滨东安汽车发动机制造有限公司 | Planetary gear type 6-speed automatic speed changer |
| CN103807371A (en) * | 2012-11-05 | 2014-05-21 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN103807371B (en) * | 2012-11-05 | 2018-04-27 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN105972166A (en) * | 2016-06-20 | 2016-09-28 | 裕克施乐塑料制品（太仓）有限公司 | Planetary-gear-type speed variator capable of automatic gear shifting |
| CN112392926A (en) * | 2020-12-08 | 2021-02-23 | 徐工集团工程机械股份有限公司 | Multi-stage planet carrier, multi-stage planet combined structure and multi-gear planet mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2012092749A1 (en) | 2012-07-12 |
| CN102042372B (en) | 2012-10-24 |
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