CN202165552U - Eight-speed automatic transmission - Google Patents

Eight-speed automatic transmission Download PDF

Info

Publication number
CN202165552U
CN202165552U CN 201120227865 CN201120227865U CN202165552U CN 202165552 U CN202165552 U CN 202165552U CN 201120227865 CN201120227865 CN 201120227865 CN 201120227865 U CN201120227865 U CN 201120227865U CN 202165552 U CN202165552 U CN 202165552U
Authority
CN
China
Prior art keywords
clutch
gear
hub
planetary system
output gear
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.)
Expired - Fee Related
Application number
CN 201120227865
Other languages
Chinese (zh)
Inventor
樊晓磊
徐海山
王克
白永生
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Great Wall Motor Co Ltd
Original Assignee
Great Wall Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Great Wall Motor Co Ltd filed Critical Great Wall Motor Co Ltd
Priority to CN 201120227865 priority Critical patent/CN202165552U/en
Application granted granted Critical
Publication of CN202165552U publication Critical patent/CN202165552U/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
    • 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
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight 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
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one 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
    • F16H2200/2023—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set using a Ravigneaux set with 4 connections
    • 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
    • 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

Landscapes

  • Structure Of Transmissions (AREA)

Abstract

The utility model discloses an eight-speed automatic transmission which comprises a Rarigneavx planetary system structure without a one-way clutch (that is, a conventional integral structure followed a Rarigneavx planetary system structure without a one-way clutch), a small output gear 8, a big output shaft loose change gear 23, a first additional clutch 11 and a second additional clutch. In the eight-speed automatic transmission, based on the conventional GWM (Great Wall Motors) 4AT (Four-speed Automatic Transmission) Rarigneavx planetary system structure, a Rarigneavx planetary system structure without a one-way clutch is formed after the one-way clutch is removed, and a pair of gears and two additional clutches are additionally arranged in the Rarigneavx planetary system structure without a one-way clutch, then the eight-speed automatic transmission has eight forward gears and one reverse gear, so that the dynamic property of an automobile is achieved to the utmost extent, and the fuel economy and the automobile driving property are improved to the utmost extent. The utility model has a simple and compact structure, saves space, can plays the dynamic property of the automobile, the fuel economy and the automobile driving property to the utmost extent, is applicable to various vehicles with front-engine, front-wheel drive layouts and transversally-arranged power assemblies, and is used as an eight-speed transmission.

Description

The 8AT automatic transmission
Technical field
The utility model relates to a kind of transmission for vehicles, and specifically a kind of have a 8AT automatic transmission.
Background technique
Present vehicular automatic transmission; Mainly contain hydraulic mechanical type automatic transmission (AT), mechanical continuously-variable transmission (CVT) and electric control mechanical type automatic speed variator several kinds of forms such as (AMT), however undeniable be that the comprehensive advantage of reliability, serviceability, travelling comfort on traditional AT structure remains the other technologies short time and can't catch up with.8AT even 9AT are just expedited the emergence of under such background; Even if its volume is huge many than 4AT, 5AT; But have more nearly one times ultimate attainment smooth-going and outstanding power performance that gear brought, the bumper harvests of economic performance, make ancient AT gearbox still enjoy favor.
4AT automatic transmission gear is less, can not give full play to engine power performance, and fuel consume is higher.Like GWM 4AT La Weina planetary system structure; Can be according to riving condition and driver's driving habits; Opening speed according to closure comes the choose reasonable shifting points between economical and power type gear shifting characteristic curve; Fully to satisfy driver's individual character requirement, have simple and compact for structure, the characteristics of saving the space.But GWM 4AT has only 4 forward gears, and its adjacent gear ratios differs bigger, and shift process has slight impact.
Summary of the invention
The technical problem that the utility model will solve; Providing a kind of 8AT automatic transmission, is on the basis of existing GWM 4AT La Weina planetary system structure, has increased a pair of gear when removing overrunning clutch; And increase by two clutches, thereby 8 forward gears and a gear reversing function have been realized.The utility model is simple and compact for structure, saves the space, can bring into play the power performance of automobile to greatest extent and improve fuel economy and vehicle drive property.
For solving the problems of the technologies described above, the technological scheme that the utility model adopted is:
A kind of 8AT automatic transmission; It comprises overrunning clutch La Weina planetary system structure, little output gear, big output shaft continuously-meshing gear, first extra clutch, second extra clutch, and wherein the outer hub of first and second extra clutch adopts spline to be connected with the planetary ring gear that goes overrunning clutch La Weina planetary system structure; The interior hub of first extra clutch and the big output gear splined of removing overrunning clutch La Weina planetary system; Spline is connected between the interior hub of little output gear and second extra clutch; Little output gear radially is connected through sliding bearing with the big output gear that removes overrunning clutch La Weina planetary system, and little output gear is connected hub diameter to connecting through sliding bearing with the first clutch that removes overrunning clutch La Weina planetary system.
More than be the basic structure of the utility model; Be on the basis of existing GWM 4AT La Weina planetary system structure, to remove overrunning clutch formation to go overrunning clutch La Weina planetary system structure; And increase a pair of gear and two additional clutches going overrunning clutch to draw to maintain structure to suffer; Reverse gear thereby had 8 advance gear and one, can bring into play the power performance of automobile to greatest extent, improve fuel economy and vehicle drive property to greatest extent.
As specializing of the utility model structure; Said automatic transmission comprises input shaft; First to three-clutch, first and second extra clutch, first and second break, remove short planet wheel and long planet wheel, double planet wheel rows of mixing and the output gear of the double planet wheel rows of mixing of overrunning clutch La Weina planetary system structure; Also comprise little output gear and big output shaft continuously-meshing gear
A right certainly extremely left side is followed successively by the connection hub that is connected with fluid torque converter, oil pump, second clutch, first clutch, second clutch, the interior hub of first clutch, little output gear, big output gear, first extra clutch, second extra clutch, removes overrunning clutch La Weina planetary system structure, first break, second break, three-clutch on the input shaft;
Input shaft is connected with transformer turbine, the outer hub spline of three-clutch; The hub of input shaft and second clutch, first clutch connects firmly, go overrunning clutch La Weina planetary system preceding sun gear, go the rear sun gear of overrunning clutch La Weina planetary system to be connected with input shaft through sliding bearing (lining); The interior hub of first clutch is connected with preceding sun gear spline; The connection hub of second clutch is connected with the planet carrier spline that removes overrunning clutch La Weina planetary system; Whether second clutch control planet carrier is power input part, and whether sun gear is power input part before the first clutch control; The interior hub of the hub and second break connects firmly in rear sun gear and the three-clutch, and whether three-clutch control rear sun gear is power input part, and whether second break control rear sun gear rotates; The planetary ring gear that removes overrunning clutch La Weina planetary system adopts spline to be connected with the outer hub of first and second extra clutch, the big output gear that removes overrunning clutch La Weina planetary system and little output gear respectively with first, second extra clutch in the hub spline be connected; The hub outer ring of big output gear be fixed in the two-row ball bearing inner ring interference fit on the housing, little output gear radially adopts sliding bearing to be connected with output gear greatly, little output gear is connected hub in radially connecting with sliding bearing with second clutch.
Matching relationship between above-mentioned member is: preceding sun gear often meshes with short planet wheel; Short planet wheel often meshes with long planet wheel; Often mesh with duration planet wheel and rear sun gear, long planet wheel and planetary ring gear often mesh, and long planet wheel shaft is fixed on the planet carrier with short planet wheel shaft; Big output gear often meshes with little output shaft constant mesh gear, and little output gear often meshes with big output shaft continuously-meshing gear, little output shaft constant mesh gear, greatly the output shaft constant mesh gear (spline is connected with output shaft.
Owing to adopted above-mentioned technological scheme; The utility model compared with prior art; The technological progress that is obtained is: this 8 gear transmission is on the basis of existing GWM 4AT La Weina planetary system structure, to increase a pair of gear, and increases by two clutches and realize that 8 forward gears and one reverses gear, and on the basis of original 4AT, increases by four gears that advance; Reduced the speed changer longitudinal size greatly, arranged for car load and practiced thrift very large space; Each gear adopts three control unit controls, and most shift processes only need two control unit actions to accomplish, and its shift process is smooth-going.The utility model is simple and compact for structure, saves the space, can bring into play the power performance of automobile to greatest extent and improve fuel economy and vehicle drive property.The utility model is applicable to that various preposition forerunners, power assembly are horizontal vehicle, as 8 gear speed change gears.
The utility model below will combine Figure of description and specific embodiment to do further explain.
Description of drawings
Fig. 1 is the utility model embodiment's an overall structure schematic representation;
Fig. 2 is the radial position relationship schematic representation of middle input shaft embodiment illustrated in fig. 1, jack shaft and differential mechanism.
Among the figure: 2-input shaft, 3-turbine, 5-pump impeller, 6-first clutch, 7-second clutch; The connection hub of 8-second clutch, 9-little output gear, 10-big output gear, 11-the first extra clutch, 12-the second extra clutch; 13-the first break, 14-planet carrier, 15-the second break, 16-the three-clutch, 17-preceding sun gear; 18-short planet wheel, 19-rear sun gear, 20-long planet wheel, 21-planetary ring gear, 22-little output shaft continuously-meshing gear; 23-big output shaft continuously-meshing gear, 24-output shaft, 25-differential mechanism, the interior hub of 26-first clutch.
Embodiment
Embodiment
Shown in Figure 1 is a kind of 8AT automatic transmission, and it comprises overrunning clutch La Weina planetary system structure (the promptly existing overall structure that connects after dimension Na planetary system structure is removed overrunning clutch), little output gear 9, big output shaft continuously-meshing gear 23, first extra clutch 11, second extra clutch 12.Wherein:
The outer hub of first and second extra clutch 11,12 adopts spline to be connected with the planetary ring gear that goes overrunning clutch La Weina planetary system structure 21; The interior hub of first extra clutch 11 and big output gear 10 splined of removing overrunning clutch La Weina planetary system; Spline is connected between the interior hub of little output gear 9 and second extra clutch 12; Little output gear 9 radially is connected through sliding bearing with the big output gear 10 that removes overrunning clutch La Weina planetary system, and little output gear 9 radially connects through sliding bearing with the hub 8 that is connected of the first clutch that removes overrunning clutch La Weina planetary system.Particularly:
Automatic transmission comprises input shaft 2; First to the short planet wheel 18 of three- clutch 6,7 and 16, first and second extra clutch 11 and 12, first and second break 13 and 15, double planet wheel rows of mixing and long planet wheel 20, output gear 9 and 10, also comprises little output shaft continuously-meshing gear 22 and big output shaft continuously-meshing gear 23.
On the input shaft 2 from the right interior hub 26 that is followed successively by the connection hub 8 that is connected with fluid torque converter, oil pump, second clutch 7, first clutch 6, second clutch 7, second clutch 7 to a left side, little output gear 9, big output gear 10, first extra clutch 11, second extra clutch 12, remove overrunning clutch La Weina planetary system structure, first break 13, second break 15, three-clutch 16.
Input shaft 2 is connected with transformer turbine 3, the outer hub spline of three-clutch (16); Input shaft 2 connects firmly with the hub of second clutch 7, first clutch 6, go overrunning clutch La Weina planetary system preceding sun gear 17, go the rear sun gear 19 of overrunning clutch La Weina planetary system to be connected with input shaft 2 through sliding bearing (lining); The interior hub 26 of first clutch 6 is connected with preceding sun gear 17 splines; The connection hub 8 of second clutch 7 clutches is connected with planet carrier 14 splines that remove overrunning clutch La Weina planetary system; Whether second clutch 7 control planet carriers 14 are power input part, and whether sun gear 17 is power input part before first clutch 6 controls; The interior hub of the hub and second break 15 connects firmly in rear sun gear 19 and the three-clutch 16, and whether three-clutch 16 control rear sun gears 19 are power input part, and whether second break, 15 control rear sun gears 19 rotate; Go the planetary ring gear 21 of overrunning clutch La Weina planetary system to adopt spline to be connected, go the big output gear 10 of overrunning clutch La Weina planetary system to be connected with the interior hub spline of first, second extra clutch 11,12 respectively with little output gear 9 with the outer hub of first, second extra clutch 11,12; The hub outer ring of big output gear 10 be fixed in the two-row ball bearing inner ring interference fit on the housing; Little output gear 9 radially adopts sliding bearing to be connected with big output gear 10, and little output gear 9 is connected hub 8 in radially connecting with sliding bearing with second clutch 7.
Matching relationship between above-mentioned member is: preceding sun gear 17 often meshes with short planet wheel 18; Short planet wheel 18 often meshes with long planet wheel 20; Often mesh with duration planet wheel 20 and rear sun gear 19; Long planet wheel 20 often meshes with planetary ring gear 21, and long planet wheel shaft is fixed on the planet carrier 14 with short planet wheel shaft; Big output gear 10 often mesh with little output shaft constant mesh gear 22, and little output gear 9 often meshes with big output shaft continuously-meshing gear 23, and little output shaft constant mesh gear 22, output shaft constant mesh gear 23 is connected with output shaft 24 splines greatly.
The radial position relationship of input shaft 2, output shaft 24, differential mechanism 25 is with reference to figure 2.
Present embodiment respectively to keep off power transmission process following:
[D1 retaining]
First clutch 6, second extra clutch 12, first break 13 combine; This moment, planet carrier 14 was fixed.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Sun gear 17 before passing to by first clutch 6 again; Preceding sun gear 17 is passed to short planet wheel 18; Short planet wheel 18 is passed to long planet wheel 20; Long planet wheel 20 is passed to planetary ring gear 21, and planetary ring gear 21 is passed to little output shaft continuously-meshing gear 22, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Rear sun gear 19, big output gear 10 rotate freely, not transmitting torque.
[D2 retaining]
First clutch 6, second extra clutch 12, second break 15 combine; This moment, rear sun gear 19 was fixed.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Sun gear 17 before passing to by first clutch 6 again; Preceding sun gear 17 is passed to short planet wheel 18; Short planet wheel 18 is passed to long planet wheel 20 and planet carrier 14; Long planet wheel 20 is passed to planetary ring gear 21 with planet carrier 14, and planetary ring gear 21 is passed to little output shaft continuously-meshing gear 22, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Big output gear 10 rotates freely, not transmitting torque.
[D3 retaining]
First clutch 6, first extra clutch 11, first break 13 combine; This moment, planet carrier 14 was fixed.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Sun gear 17 before passing to by first clutch 6 again; Preceding sun gear 17 is passed to short planet wheel 18, and short planet wheel 18 is passed to long planet wheel 20, and long planet wheel 20 is passed to planetary ring gear 21; Planetary ring gear 21 is passed to big output gear 10, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Rear sun gear 19, little output shaft continuously-meshing gear 22 rotate freely, not transmitting torque.
[D4 retaining]
Second clutch 7, first clutch 6, second extra clutch 12 combine; This moment, planet row locking was an one.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Pass to planet carrier 14 and preceding sun gear 17 by first and second clutch 6,7 again; Preceding sun gear 17 is passed to short planet wheel 18; Short planet wheel 18 is passed to long planet wheel 20; Long planet wheel 20 is passed to planetary ring gear 21, and planetary ring gear 21 is passed to little output shaft continuously-meshing gear 22, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Rear sun gear 19, big output gear 10 rotate freely, not transmitting torque.
[D5 retaining]
Second clutch 7, second extra clutch 12, second break 15 combine; This moment, rear sun gear 19 was fixed.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Pass to planet carrier 14 by second clutch 7 again, planet carrier 14 is passed to long planet wheel 20, and long planet wheel 20 is passed to planetary ring gear 21, and planetary ring gear 21 is passed to little output shaft continuously-meshing gear 22, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Preceding sun gear 17, short planet wheel 18 and big output gear 10 rotate freely, not transmitting torque.
[D6 retaining]
First clutch 6, first extra clutch 11, second break 15 combine; This moment, rear sun gear 19 was fixed.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Sun gear 17 before passing to by first clutch 6 again; Preceding sun gear 17 is passed to short planet wheel 18; Short planet wheel 18 is passed to long planet wheel 20 and planet carrier 14; Long planet wheel 20 is passed to planetary ring gear 21 with planet carrier 14, passes to big output gear 10 again, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Little output shaft continuously-meshing gear 22 rotates freely.
[D7 retaining]
Second clutch 7, first clutch 6, first extra clutch 13 combine; This moment, planet row locking was an one.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Pass to planet carrier 14 by first and second clutch 6 and 7 again, pass to planetary ring gear 21, pass to big output gear 10 again by long planet wheel 20, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Rear sun gear 19, little output shaft continuously-meshing gear 22 rotate freely, not transmitting torque.
[D8 retaining]
Second clutch 7, first extra clutch 11, second break 15 combine; This moment, rear sun gear 19 was fixed.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Pass to planet carrier 14 by second clutch 7 again, planet carrier 14 is passed to long planet wheel 20, and long planet wheel 20 is passed to planetary ring gear 21 with planet carrier 14, and planetary ring gear 21 is passed to big output gear 10, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Preceding sun gear 17, short planet wheel 18 and little output shaft continuously-meshing gear 22 rotate freely, not transmitting torque.
[reversing gear]
Second extra clutch 12, three-clutch 15, first break 13 combine; This moment, planet carrier 14 was fixed.
Power is passed to the pump impeller 5 of fluid torque converter by motor, and pump impeller 5 is passed to turbine 3 through fluid power, and turbine 3 is passed to input shaft 2 through spline; Pass to rear sun gear 19 by second extra clutch 12 again; Rear sun gear 19 is passed to long planet wheel 20; Long planet wheel 20 is passed to planetary ring gear 21, and planetary ring gear 21 is passed to little output shaft continuously-meshing gear 22, through output shaft 24 and differential mechanism 25 the most at last power pass on the semiaxis.
Preceding sun gear 17, short planet wheel 18 and big output gear 10 rotate freely, not transmitting torque.

Claims (2)

1. 8AT automatic transmission, It is characterized in that:It comprises overrunning clutch La Weina planetary system structure, little output gear (9), big output shaft continuously-meshing gear (23), first extra clutch (11), second extra clutch (12), and wherein the outer hub of first and second extra clutch (11,12) adopts spline to be connected with the planetary ring gear (21) that goes overrunning clutch La Weina planetary system structure; The interior hub of first extra clutch (11) and big output gear (10) splined of removing overrunning clutch La Weina planetary system; Spline is connected between the interior hub of little output gear (9) and second extra clutch (12); Little output gear (9) radially is connected through sliding bearing with the big output gear (10) that removes overrunning clutch La Weina planetary system, and little output gear (9) radially connects through sliding bearing with the hub (8) that is connected of the first clutch that removes overrunning clutch La Weina planetary system.
2. 8AT automatic transmission according to claim 1, It is characterized in that:Said automatic transmission comprises input shaft (2); First to three-clutch (6,7,16), first and second extra clutch (11,12), first and second break (13,15), the short planet wheel (18) that removes the double planet wheel rows of mixing of overrunning clutch La Weina planetary system structure, long planet wheel (20), output gear (9,10), also comprises little output shaft continuously-meshing gear (22) and big output shaft continuously-meshing gear (23);
Input shaft (2) is gone up from right being followed successively by to a left side and is connected with fluid torque converter; Oil pump; Second clutch (7); First clutch (6); The connection hub (8) of second clutch (7); The interior hub (26) of first clutch (7); Little output gear (9); Big output gear (10); First extra clutch (11); Second extra clutch (12); Go overrunning clutch La Weina planetary system structure; First break (13); Second break (15); Three-clutch (16);
Input shaft (2) is connected with transformer turbine (3), the outer hub spline of three-clutch (16); The hub of input shaft (2) and second clutch (7), first clutch (6) connects firmly, go overrunning clutch La Weina planetary system preceding sun gear (17), go the rear sun gear (19) of overrunning clutch La Weina planetary system to be connected with input shaft (2) through sliding bearing; The interior hub (26) of first clutch (6) is connected with preceding sun gear (17) spline, and the connection hub (8) of second clutch (7) is connected with the planet carrier that removes overrunning clutch La Weina planetary system (14) spline; Rear sun gear (19) connects firmly with the interior hub of interior hub of three-clutch (16) and second break (15); Go the planetary ring gear (21) of overrunning clutch La Weina planetary system to adopt spline to be connected, go the big output gear (10) of overrunning clutch La Weina planetary system to be connected with the interior hub spline of first and second extra clutch (11,12) respectively with little output gear (9) with the outer hub of first, second extra clutch (11,12); The hub outer ring of big output gear (10) be fixed in the two-row ball bearing inner ring interference fit on the housing; Little output gear (9) radially adopts sliding bearing to be connected with big output gear (10), and little output gear (9) is connected hub (8) in radially connecting with sliding bearing with second clutch (7).
CN 201120227865 2011-06-30 2011-06-30 Eight-speed automatic transmission Expired - Fee Related CN202165552U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN 201120227865 CN202165552U (en) 2011-06-30 2011-06-30 Eight-speed automatic transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN 201120227865 CN202165552U (en) 2011-06-30 2011-06-30 Eight-speed automatic transmission

Publications (1)

Publication Number Publication Date
CN202165552U true CN202165552U (en) 2012-03-14

Family

ID=45801378

Family Applications (1)

Application Number Title Priority Date Filing Date
CN 201120227865 Expired - Fee Related CN202165552U (en) 2011-06-30 2011-06-30 Eight-speed automatic transmission

Country Status (1)

Country Link
CN (1) CN202165552U (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102817974A (en) * 2012-08-24 2012-12-12 北京理工大学 Eight-gear planetary automatic speed changer
CN102954156A (en) * 2012-11-20 2013-03-06 长城汽车股份有限公司 Automatic speed changer and car applying same
US9488263B2 (en) 2014-08-15 2016-11-08 Caterpillar Inc. Modular arrangement for hydromechanical transmission
CN109017266A (en) * 2018-07-24 2018-12-18 浙江吉利控股集团有限公司 Hybrid gearbox and the automobile for using the speed changer

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102817974A (en) * 2012-08-24 2012-12-12 北京理工大学 Eight-gear planetary automatic speed changer
CN102817974B (en) * 2012-08-24 2015-03-11 北京理工大学 Eight-gear planetary automatic speed changer
CN102954156A (en) * 2012-11-20 2013-03-06 长城汽车股份有限公司 Automatic speed changer and car applying same
CN102954156B (en) * 2012-11-20 2015-08-19 长城汽车股份有限公司 Automatic transmission and apply its automobile
US9488263B2 (en) 2014-08-15 2016-11-08 Caterpillar Inc. Modular arrangement for hydromechanical transmission
CN109017266A (en) * 2018-07-24 2018-12-18 浙江吉利控股集团有限公司 Hybrid gearbox and the automobile for using the speed changer

Similar Documents

Publication Publication Date Title
CN202165536U (en) Automatic transmission with six forward gears and reverse gear
US20100269613A1 (en) Multi-clutch transmission having dual front-positioned gears and method of operating the same
CN211059305U (en) Two keep off derailleur gearshift
CN106438906A (en) Conical band type automobile continuously variable transmission
CN202165552U (en) Eight-speed automatic transmission
CN106917850A (en) Eight speed automatic transmissions
CN202188084U (en) 6AT transmission
CN210390751U (en) Hybrid power speed change mechanism, hybrid power system and vehicle with hybrid power system
JP5693509B2 (en) Automatic transmission for vehicles
CN202165553U (en) Automatic transmission with eight forward gears and one reverse gear
JP5780983B2 (en) Automatic transmission for vehicles
KR100836107B1 (en) A 8th-speed power train of an automatic transmission for car
US9556936B2 (en) Planetary gear train of automatic transmission for vehicle
CN102628495A (en) Six-gear planet automatic gearbox
CN109578533B (en) Three-gear electric assembly and speed ratio determination method thereof
CN101446332B (en) Planetary gearbox with multi-gear power gear shifting
KR100836106B1 (en) A 8th-speed power train of an automatic transmission for car
CN201359059Y (en) Multi-gear power shift planetary gearbox
CN202674221U (en) Six-gear planetary type hydrodynamic drive device
KR101775263B1 (en) Power transmission device for automobiles
CN201858316U (en) 8AT (Automatic Transmission) gear transmission system
KR101775264B1 (en) Power transmission device for automobiles
CN201359060Y (en) Multi-gear power shift planetary gearbox
CN101629618B (en) Multi-gear combined type transmission with prepositioned auxiliary box
CN209892699U (en) Double planetary gear set type two-speed electric drive transmission

Legal Events

Date Code Title Description
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20120314

Termination date: 20170630