CN102042372B - Multi-speed transmission - Google Patents

Multi-speed transmission Download PDF

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Publication number
CN102042372B
CN102042372B CN2011100211333A CN201110021133A CN102042372B CN 102042372 B CN102042372 B CN 102042372B CN 2011100211333 A CN2011100211333 A CN 2011100211333A CN 201110021133 A CN201110021133 A CN 201110021133A CN 102042372 B CN102042372 B CN 102042372B
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CN
China
Prior art keywords
gear
planetary gear
gear set
fixed axis
planet carrier
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CN2011100211333A
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Chinese (zh)
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CN102042372A (en
Inventor
黄庆培
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GUANGZHOU KELIYUAN ELECTROMECHANICAL TECHNOLOGY Co Ltd
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GUANGZHOU KELIYUAN ELECTROMECHANICAL TECHNOLOGY Co Ltd
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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
    • 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
    • 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
    • F16H2200/203—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
    • 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
    • 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

Multiple-speed gear-box
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.
" 8-speed transmission " of " 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, CN101392817, CN101392819 etc. comprises 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 technical problem that the present invention provides a kind of multiple-speed gear-box to 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; Said first and second planetary gear set are arranged on the axis of input shaft;
The said first and second fixed axis gear groups have separately driving wheel, follower respectively; The follower of the driving wheel of the said 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 said first fixed axis gear group and the second fixed axis gear group interconnects, and its coupling shaft constitutes countershaft;
The sun gear of said second planetary gear set, planet carrier are connected with said input shaft, output block respectively;
The driving wheel of the gear ring of said first planetary gear set and the said first fixed axis gear group interconnects, and the follower of the gear ring of said second planetary gear set and the said second fixed axis gear group interconnects;
Selectively be connected both between the sun gear that said first clutch gear-changing component is serially connected in said first planetary gear set and the said input shaft; Selectively be connected both between the sun gear that said second clutch gear-changing component is serially connected in said first planetary gear set and the planet carrier of said second planetary gear set; Selectively be connected both between the planet carrier that said three-clutch gear-changing component is serially connected in said first planetary gear set and the said input shaft;
Said 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 said first planetary gear set and the gear ring of said second planetary gear set, the rotating ratio of the gear ring of the planet carrier of said first planetary gear set and said second planetary gear set equals 1 when said four clutches gear-changing component combines; Scheme two; Speed changer comprises that also driving wheel, follower are arranged in the 3rd fixed axis gear group on input shaft, the layshaft axis; Said four clutches gear-changing component is serially connected between the gear ring of planet carrier and said second planetary gear set of said first planetary gear set and selectively is in transmission connection both through on the route that is in transmission connection of countershaft; The planet carrier of said first planetary gear set that the driven wheel that said " through the route that is in transmission connection of countershaft " is the driven wheel through said the 3rd fixed axis gear group, said countershaft, the said second fixed axis gear group forms is to the drive path of the gear ring of said second planetary gear set; Between the driving wheel of said four clutches gear-changing component or the planet carrier that is serially connected in said first planetary gear set and said the 3rd fixed axis gear group and the follower of said the 3rd fixed axis gear group be connected with countershaft; Between the follower that perhaps is serially connected in said the 3rd fixed axis gear group and the countershaft and the planet carrier of said first planetary gear set be connected with the driving wheel of said the 3rd fixed axis gear group; When said four clutches gear-changing component combines; The rotating ratio of the gear ring of the planet carrier of said first planetary gear set and said 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;
Said the 5th clutch shift element perhaps is serially connected between the planet carrier and said housing of said first planetary gear set; Perhaps in such scheme two; The 5th clutch shift series of elements is connected between the follower and said 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 said first planetary gear set;
In addition; Can also comprise overrunning clutch; Said overrunning clutch or be serially connected in the two ends that between the planet carrier and said housing of said first planetary gear set, perhaps are attempted by said the 5th clutch shift element; Its effect is to allow the planet carrier of said first planetary gear set to the identical sense of rotation rotation of said input shaft, and locking does not allow the planet carrier of said first planetary gear set to the opposite sense of rotation rotation of said 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 following:
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 said first planetary gear set and said second planetary gear set
9: the route that is in transmission connection between the planet carrier of said 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:Like Fig. 1, said 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 said 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 said first planetary gear set 10 and the gear ring 23 of said second planetary gear set 20 respectively;
The follower 32 of the said 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 said second planetary gear set 20, planet carrier 22 are connected with said input shaft 1, output block 2 respectively;
Selectively be connected both between the sun gear 11 that said first clutch gear-changing component 61 is serially connected in said first planetary gear set 10 and the said input shaft 1; Selectively be connected both between the sun gear 11 that said second clutch gear-changing component 62 is serially connected in said first planetary gear set 10 and the planet carrier 22 of said second planetary gear set 20; Selectively be connected both between the planet carrier 12 that said three-clutch gear-changing component 63 is serially connected in said first planetary gear set 10 and the said input shaft 1;
Selectively be connected both between the planet carrier 12 that said four clutches gear-changing component 64 is serially connected in said first planetary gear set 10 and the gear ring 23 of said second planetary gear set 20;
Said the 5th clutch shift element 65 is serially connected in the planet carrier 12 of selectively braking said first planetary gear set 10 between planet carrier 12 and the said housing 5 of said first planetary gear set 10.
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:
Figure 426983DEST_PATH_IMAGE001
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 said first planetary gear set 10 to rotate to input shaft 1 identical sense of rotation; Locking does not allow planet carrier 12 to the opposite sense of rotation rotation of input shaft 1, like this when automobile when urban road goes, first, second of low speed grade can combine 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 combine the 5th clutch shift element 65, and engine braking capable of using improves the safety of descent run.
Embodiment two:Like Fig. 2; Be with embodiment one the main distinction: increased by the 3rd fixed axis gear group 50; Its driving wheel 51 is arranged on the axis of input shaft 1 and countershaft 3 with follower 52; Four clutches gear-changing component 64 is not directly to be serially connected between the gear ring 23 of planet carrier 12 and second planetary gear set 20 of first planetary gear set 10; Be in transmission connection on the route 8 of gear ring 23 of second planetary gear set 20 through the 3rd fixed axis gear group 50, countershaft 3, the second fixed axis gear group 40 but be serially connected in planet carrier 12; What Fig. 2 showed 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, and 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 combines; 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:
Figure 631568DEST_PATH_IMAGE002
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 said housing 5, its effect is identical with embodiment one.

Claims (4)

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: said first and second planetary gear set (10,20) are single pinion type planetary gear set; And separately sun gear (11,21), planet carrier (12,22), gear ring (13,23) are arranged respectively, and be arranged on the axis of input shaft (1);
The said 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 said 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 said 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 said second planetary gear set (20), planet carrier (22) are connected with said input shaft (1), output block (2) respectively;
The gear ring (13) of said first planetary gear set (10) interconnects with the driving wheel (31) of the said first fixed axis gear group (30); The gear ring (23) of said second planetary gear set (20) interconnects with the follower (42) of the said second fixed axis gear group (40);
Selectively be connected both between the sun gear (11) that said first clutch gear-changing component (61) is serially connected in said first planetary gear set (10) and the said input shaft (1); Selectively be connected both between the sun gear (11) that said second clutch gear-changing component (62) is serially connected in said first planetary gear set (10) and the planet carrier (22) of said second planetary gear set (20); Selectively be connected both between the planet carrier (12) that said three-clutch gear-changing component (63) is serially connected in said first planetary gear set (10) and the said input shaft (1);
Selectively be connected both between the planet carrier (12) that said four clutches gear-changing component (64) is serially connected in said first planetary gear set (10) and the gear ring (23) of said second planetary gear set (20);
Said the 5th clutch shift element (65) is serially connected in the planet carrier (12) of selectively braking said first planetary gear set (10) between planet carrier (12) and the said housing (5) of said first planetary gear set (10).
2. multiple-speed gear-box according to claim 1 also comprises overrunning clutch (71); It is characterized in that: said overrunning clutch (71) is serially connected between the planet carrier (12) and said housing (5) of said first planetary gear set (10); Allow the planet carrier (12) of said first planetary gear set (10) to rotate in the same way with said input shaft (1), locking does not allow the planet carrier (12) of said first planetary gear set (10) to the opposite sense of rotation rotation of said input shaft (1).
3. multiple-speed gear-box comprises input shaft (1), output block (2), countershaft (3), housing (5), first and second planetary gear set (10,20), first, second and the 3rd fixed axis gear group (30,40,50), first to the 5th clutch shift element (61,62,63,64,65); It is characterized in that: said first and second planetary gear set (10,20) are single pinion type planetary gear set; And separately sun gear (11,21), planet carrier (12,22), gear ring (13,23) are arranged respectively, and be arranged on the axis of input shaft (1);
Said first, second is outer gearing type gear train with the 3rd fixed axis gear group (30,40,50); And separately driving wheel (31,41,51), follower (32,42,52) are arranged respectively; The driving wheel (51) of the follower (42) of the driving wheel (31) of the said first fixed axis gear group (30), the second fixed axis gear group (40) and the 3rd fixed axis gear group (50) is arranged on the axis of input shaft (1); The driving wheel (41) of the follower (32) of the said first fixed axis gear group (30) and the second fixed axis gear group (40) interconnects; Its coupling shaft constitutes countershaft (3), and the follower (52) of said the 3rd fixed axis gear group (50) is arranged on the axis of countershaft (3);
The sun gear (21) of said second planetary gear set (20), planet carrier (22) are connected with said input shaft (1), output block (2) respectively;
The gear ring (13) of said first planetary gear set (10) interconnects with the driving wheel (31) of the said first fixed axis gear group (30); The gear ring (23) of said second planetary gear set (20) interconnects with the follower (42) of the said second fixed axis gear group (40); The planet carrier (12) of said first planetary gear set (10) interconnects with the driving wheel (51) of said the 3rd fixed axis gear group (50);
Selectively be connected both between the sun gear (11) that said first clutch gear-changing component (61) is serially connected in said first planetary gear set (10) and the said input shaft (1); Selectively be connected both between the sun gear (11) that said second clutch gear-changing component (62) is serially connected in said first planetary gear set (10) and the planet carrier (22) of said second planetary gear set (20); Selectively be connected both between the planet carrier (12) that said three-clutch gear-changing component (63) is serially connected in said first planetary gear set (10) and the said input shaft (1);
Said four clutches gear-changing component (64) be serially connected in said the 3rd fixed axis gear group (50) follower (52) and said countershaft (3) thus between through said the 3rd fixed axis gear group (50), said countershaft (3) and the said second fixed axis gear group (40) selectively the be in transmission connection planet carrier (12) of said first planetary gear set (10) and the gear ring (23) of said second planetary gear set (20);
Said the 5th clutch shift element (65) be serially connected in said the 3rd fixed axis gear group (50) follower (52) and said housing (5) thus between selectively brake the planet carrier (12) of said first planetary gear set (10).
4. multiple-speed gear-box according to claim 3 also comprises overrunning clutch (71); It is characterized in that: said overrunning clutch (71) or be serially connected in the two ends that between the planet carrier (12) and said housing (5) of said first planetary gear set (10), perhaps are attempted by said the 5th clutch shift element (65); Allow the planet carrier (12) of said first planetary gear set (10) to rotate in the same way with said input shaft (1), locking does not allow the planet carrier (12) of said first planetary gear set (10) to the opposite sense of rotation rotation of said input shaft (1).
CN2011100211333A 2011-01-07 2011-01-18 Multi-speed transmission Expired - Fee Related CN102042372B (en)

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CN102042372B (en) * 2011-01-07 2012-10-24 广州科立源机电科技有限公司 Multi-speed transmission
CN102797809B (en) * 2012-08-31 2013-08-14 哈尔滨东安汽车发动机制造有限公司 Planetary gear type 6-speed automatic speed changer
KR101329008B1 (en) * 2012-11-05 2013-11-12 현대자동차주식회사 Planetary gear train of automatic transmission for vehicles
CN105972166B (en) * 2016-06-20 2018-11-06 裕克施乐塑料制品（太仓）有限公司 It is a kind of can self shifter planetary gear type speed change gear
CN112392926B (en) * 2020-12-08 2022-05-10 徐工集团工程机械股份有限公司 Multi-stage planet carrier, multi-stage planet combination structure and multi-gear planet mechanism

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