CN105179615A - Improved nine-gear transmission - Google Patents
Improved nine-gear transmission Download PDFInfo
- Publication number
- CN105179615A CN105179615A CN201510424619.XA CN201510424619A CN105179615A CN 105179615 A CN105179615 A CN 105179615A CN 201510424619 A CN201510424619 A CN 201510424619A CN 105179615 A CN105179615 A CN 105179615A
- Authority
- CN
- China
- Prior art keywords
- gear
- planet
- coupling member
- transmission
- break
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/76—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides an improved nine-gear transmission. The improved nine-gear transmission mainly comprises an input shaft, an output shaft, planet gear rows, connecting components and torque transmission devices. All the components are arranged in a transmission shell. Each planet gear row comprises a sun gear, a planet carrier, a planet gear and a gear ring. Each torque transmission device comprises two clutches and four brakes, wherein the two clutches and the four brakes are selectively jointed, and then the sun gears, the planet carriers and the gear rings or one of the four connecting components rotate or are/is fixed; the torque transmission devices can be selectively jointed in a combining form of at least two torque transmission devices; and nine forward gear speed ratios and a reverse gear speed ratio are established between the input shaft and the output shaft, and nine forward gears include the five deceleration gears, one direct gear and the three overspeed gears. The transmission is compact in structure, low in weight and small in size, and is easily arranged on an automobile, and the speed ratio step change between the transmission ratios of all the gears of the transmission meet the requirements of the transmission.
Description
Technical field
The present invention relates to a kind of modified model nine shift transmission, belong to system of vehicle transmission technical field.
Background technique
Typical multi-speed transmission uses the combination of friction clutch, planetary gear system and fixed interconnection to realize multiple velocity ratio.The quantity of planetary gear set and physics are arranged usually by encapsulation, cost and desired speed ratio regulation.Although current speed changer achieves its expection object, universal along with automobile, people to new-type and improve speed changer configuration to need be in fact continual.
The improvement of described speed changer configuration is mainly set about from following two aspects, and one is performance, specifically comprises the angle of the scope of velocity ratio, responsiveness and flatness; Two is encapsulation, the size mainly reduced and weight, when gear is determined, the quantity realizing fixing component needed for gear is corresponding determines the performance therefore improvement of speed changer mainly being improved to speed changer, when speed changer composition component remains unchanged substantially, how to pass through the annexation improving each inter-module, to increase the attainable gear number of speed changer and velocity ratio parameter, become difficult point and the core of transmissions improved.Chinese invention application " eight shift transmissions " (application number: CN201410829472) and Chinese invention application " speed changer that CN201410826601-slewing range is wider " (application number: CN201110094929) all discloses a kind of eight shift transmissions be made up of four planetary gear train, six torque transmitters and four connector elements, above-mentioned two speed changers all realize eight forward gear speed ratios and the speed ratio that reverses gear, but there is the problem that gear is less, speed is smaller, transmission stability is lower.
Summary of the invention
The object of the present invention is to provide a kind of volume that can reduce retarder, lower the difficulty that controls and there is modified model nine shift transmission of wider transmission gear ratio scope.
Realizing the technological scheme that the object of the invention adopts is that a kind of modified model nine shift transmission, comprises gearbox case and be installed on the input shaft of gearbox case inside, output shaft, epicyclic gear train group, coupling member group and torque transmitter, described epicyclic gear train group comprises the first planet gear row installed successively from front to back, second epicyclic gear train, third planet gear row and fourth planet gear row, each epicyclic gear train is by sun gear, planet carrier, planet wheel and gear ring are formed, and described torque transmitter comprises first clutch, second clutch, first break, second brake, 3rd break and the 4th break, each break is all connected with the housing of gearbox case, it is characterized in that: described coupling member group comprises the first coupling member, second coupling member, 3rd coupling member and the 4th coupling member, wherein the first coupling member connects the gear ring of first planet gear row and the gear ring of the second epicyclic gear train, second coupling member connects the sun gear that the planet carrier of the second epicyclic gear train and third planet gear are arranged, the planet carrier that the gear ring of the 3rd coupling member connection third planet gear row and fourth planet gear are arranged, the gear ring that the planet carrier of the 4th coupling member connection third planet gear row and fourth planet gear are arranged,
The planet carrier that described first break and first planet gear are arranged is connected, and second brake is connected with the first coupling member, and the 3rd break is connected with the second coupling member, and the planet carrier that the 4th break and third planet gear are arranged is connected;
The sun gear of the sun gear that described input shaft and first planet gear are arranged and the second epicyclic gear train is all connected, the planet carrier that output shaft is arranged with fourth planet gear is connected, the sun gear that input shaft is arranged by first clutch and fourth planet gear is connected, and is connected with the 4th coupling member by second clutch.
As shown from the above technical solution, modified model nine shift transmission provided by the invention, realize speed changer nine forward gear speed ratios and the speed ratio that reverses gear by four epicyclic gear trains and six torque transmitters, the formation of the speed ratio of each gear obtains by engaging two torque transmitters; Wherein first clutch optionally engages to connect together with sun gear that input shaft and fourth planet gear arrange and rotates; Second clutch optionally engages to connect input shaft and rotates together with the 4th coupling member; First break optionally engages the planet carrier and the gearbox case that connect first planet gear row, and object is the rotation of the planet carrier in order to stop first planet gear to be arranged relative to gearbox case; Second brake optionally engages to connect the first coupling member and gearbox case, and object is to stop the first coupling member relative to the rotation of gearbox case; 3rd break optionally engages to connect the second coupling member and gearbox case, and object is to stop the second coupling member relative to the rotation of gearbox case; 4th break optionally engages to connect the 4th coupling member and gearbox case, and object is to stop the 4th coupling member relative to the rotation of gearbox case.
Two clutches and four breaks optionally engage, moving link (some in sun gear, planet carrier, gear ring or four coupling members) is rotated or fixes, and wherein torque transmitter optionally can engage can set up nine forward gear speed ratios and the speed ratio that reverses gear between described input shaft and output shaft with the combining form of at least two, nine forward gears comprise five gears that slow down, a direct gear and three overgears, are specially:
1) second brake and the 4th break engage, and realize the foundation of reversing gear, the velocity ratio reversed gear is-8;
2) the first break and the 4th break engage, and realize the foundation of a gear (slow down gear), the velocity ratio of a gear is 8;
3) first clutch and the 4th break engage, and realize the foundation of two gears (slow down gear), the velocity ratio of two gears is 4.5, and speed ratio step is 1.78;
4) first clutch and the first break engage, and realize the foundation of three gears (slow down gear), the velocity ratio of three gears is 3.06, and speed ratio step is 1.47.
5) first clutch and the 3rd break engage, and realize the foundation of four gears (slow down gear), the velocity ratio of four gears is 2.07, and speed ratio step is 1.41;
6) first clutch and second brake engage, and realize the foundation of five gears (slow down gear), the velocity ratio of five gears is 1.68, and speed ratio step is 1.29;
7) first clutch and second clutch engage, and realize the foundation of six gears (directly keeping off), and the velocity ratio of six gears is 1, and speed ratio step is 1.68;
8) second clutch and second brake engage, and realize the foundation of seven gears (overgear), and the velocity ratio of seven gears is 0.73, and speed ratio step is 1.37;
9) second clutch and the 3rd break engage, and realize the foundation of eight gears (overgear), and the velocity ratio of eight gears is 0.67, and speed ratio step is 1.09;
10) second clutch and the first break engage, and realize the foundation of nine gears (overgear), and the velocity ratio of nine gears is 0.62, and speed ratio step is 1.08.
Compared with prior art, beneficial effect of the present invention is:
1, modified model nine shift transmission provided by the invention adopts Gear Planet Transmission, and gear concentrates on centre, and its power can carry out transmission by several planet wheel, and the modulus of gear is little, compact structure, and lighter in weight is easily arranged on automobile;
2, decrease the number of torque-transfer members, nine shift transmissions only use only six torque-transfer members, reduce the volume of speed changer to a great extent;
3, the control of each gear only needs two basic change component (clutch or break), and the combination and the disconnection that need replacing a pair torque-transfer members when converting between adjacent gear, control simple;
4, this speed changer utilizes coupling member to be linked together by the component of different gear train, new transmission mechanism can be formed, the quantity of coupling member and the difference of position will cause the transmission mechanism difference in essence formed, this speed changer utilizes four coupling members, connecting mode empirical tests is feasible, and make the speed ratio step between the velocity ratio of each gear of this speed changer more meet the requirement of speed changer by the special parameter preferably obtained, the total slewing range of each gear can reach 12.9, than the slewing range 7.37 of classical ZF8 speed transmission and the slewing range 6.71 of Lexus LS460 speed changer wider,
5, the speed ratio step of three overgears is all less, is respectively 1.37,1.03 and 1.08, can steadily transmission, improves the power performance of automobile.
Accompanying drawing explanation
Fig. 1 is the structure diagram of modified model nine shift transmission provided by the invention.
Wherein, 1-input shaft, 2-output shaft, 3-gearbox case, 5-first coupling member, 6-second coupling member, 7-the 3rd coupling member, 8-the 4th coupling member, 11-first planet gear toothrow circle, 12-first planet gear seniority among brothers and sisters star-wheel, 13-first planet gear seniority among brothers and sisters carrier, 14-first planet gear row sun gear, 21-second epicyclic gear train gear ring, 22-second epicyclic gear train planet wheel, 23-second epicyclic gear train planet carrier, 24-second epicyclic gear train sun gear, 31-third planet gear toothrow circle, 32-third planet gear seniority among brothers and sisters star-wheel, 33-third planet gear seniority among brothers and sisters carrier, 34-third planet gear row sun gear, 41-fourth planet gear toothrow circle, 42-fourth planet gear seniority among brothers and sisters star-wheel, 43-fourth planet gear seniority among brothers and sisters carrier, 44-fourth planet gear row sun gear, C1-first clutch, C2-second clutch, B1-first break, B2-second brake, B3-the 3rd break, B4-the 4th break.
Embodiment
Illustrate in detail the present invention below in conjunction with drawings and Examples, content of the present invention is not limited to following examples.
Modified model nine shift transmission provided by the invention, its structure as shown in Figure 1, comprise gearbox case 3 and be installed on the input shaft 1 of gearbox case inside, output shaft 2, epicyclic gear train group, coupling member group and torque transmitter, described epicyclic gear train group comprises the first planet gear row installed successively from front to back, second epicyclic gear train, third planet gear row and fourth planet gear row, each epicyclic gear train is by sun gear (14, 24, 34 and 44), planet carrier (13, 23, 33 and 43), planet wheel (13, 23, 33 and 43) and gear ring (12, 22, 32 and 42) form, planet wheel wherein in epicyclic gear train and sun gear and gear ring are all intermeshed by gear pair, described torque transmitter comprises first clutch C1, second clutch C2, first break B1, second brake B2, 3rd break B3 and the 4th break B4, each break is all connected with the housing 3 of gearbox case,
Described coupling member group comprises the first coupling member 5, second coupling member 6, the 3rd coupling member 7 and the 4th coupling member 8, and wherein first planet gear toothrow circle 11 and the second epicyclic gear train gear ring 21 interconnect by the first coupling member 5; Second epicyclic gear train planet carrier 23 and third planet gear row sun gear 34 interconnect by the second coupling member 6; Third planet gear toothrow circle 31 and fourth planet gear seniority among brothers and sisters carrier 43 interconnect by the 3rd coupling member 7; Third planet gear seniority among brothers and sisters carrier 33 interconnects with fourth planet gear toothrow circle 41 by the 4th coupling member 8;
Described torque transmitter comprises first clutch C1, second clutch C2, the first break B1, second brake B2, the 3rd break B3 and the 4th break B4, first clutch C1 and input shaft 1 and fourth planet gear row sun gear 44 is interconnected; Input shaft 1 and the 4th coupling member 8 interconnect by second clutch C2; First planet gear seniority among brothers and sisters carrier 13 and case of transmission 3 interconnect by the first break B1; First coupling member 5 interconnects with case of transmission 3 by second brake B2; Second coupling member 6 and case of transmission 3 interconnect by the 3rd break B3; 4th coupling member 8 and case of transmission 3 interconnect by the 4th break B4;
The output terminal of described input shaft 1 arranges sun gear 14 with first planet gear all the time and the second epicyclic gear train sun gear 24 is connected, the input end of input shaft 1 is connected to the turbine of motor or torque-converters all the time, the input end of output shaft 2 is ranked carrier 43 with fourth planet gear all the time and is connected, and the output terminal of output shaft 2 is connected to next stage retarder.
Below the variable block principle of modified model nine shift transmission provided by the invention is introduced, this speed changer can realize nine forward gear speed ratios and the speed ratio that reverses gear, the formation of the speed ratio of each gear obtains by engaging two torque transmitters, introduces the working procedure of each gear below in detail:
The foundation of reversing gear, second brake B2 and the 4th break B4 engages.Specifically, second brake B2 is engaged to make the first coupling member 5 be connected with case of transmission 3, prevents the first coupling member 5 relative to the rotation of case of transmission 3.4th break B4 is engaged to make the 4th coupling member 8 be connected with case of transmission 3, prevents the 4th coupling member 8 relative to the rotation of case of transmission 3.Thus, between input shaft 1 and output shaft 2, set up the velocity ratio reversed gear.
The foundation of one gear (slow down gear), the first break B1 and the 4th break B4 is engaged.Specifically, the first break B1 is engaged to be connected with case of transmission 3 to make first planet gear rank carrier 13, prevents first planet gear to rank the rotation of carrier 13 relative to case of transmission 3.4th break B4 is engaged to make the 4th coupling member 8 be connected with case of transmission 3, prevents the 4th coupling member 8 relative to the rotation of case of transmission 3.Thus, between input shaft 1 and output shaft 2, establish the velocity ratio of a gear.
The foundation of two gears (slow down gear), first clutch C1 and the 4th break B4 is engaged.Specifically, first clutch C1 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and fourth planet gear row sun gear 44.4th break B4 is engaged to make the 4th coupling member 8 be connected with case of transmission 3, prevents the 4th coupling member 8 relative to the rotation of case of transmission 3.Result in formation of single planetary gear row transmission, between input shaft 1 and output shaft 2, establish the velocity ratio of two gears thus.
The foundation of three gears (slow down gear), first clutch C1 and the first break B1 is engaged.Specifically, first clutch C1 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and fourth planet gear row sun gear 44.First break B1 is engaged to be connected with case of transmission 3 to make first planet gear rank carrier 13, prevents first planet gear to rank the rotation of carrier 13 relative to case of transmission 3.Thus, between input shaft 1 and output shaft 2, establish the velocity ratio of three gears.
The foundation of four gears (slow down gear), first clutch C1 and the 3rd break B3 is engaged.Specifically, first clutch C1 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and fourth planet gear row sun gear 44.3rd break B3 is engaged to make the second coupling member 6 be connected with case of transmission 3, prevents the second coupling member 6 relative to the rotation of case of transmission 3.Thus, between input shaft 1 and output shaft 2, establish the velocity ratio of four gears.
The foundation of five gears (slow down gear), first clutch C1 and second brake B2 is engaged.Specifically, first clutch C1 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and fourth planet gear row sun gear 44.Second brake B2 is engaged to make the first coupling member 5 be connected with case of transmission 3, prevents the first coupling member 5 relative to the rotation of case of transmission 3.Thus, between input shaft 1 and output shaft 2, establish the velocity ratio of five gears.
The foundation of six gears (directly keeping off), first clutch C1 and second clutch C2 is engaged.Specifically, first clutch C1 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and fourth planet gear row sun gear 44.Second clutch C2 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and the 4th coupling member 8.Thus, between input shaft 1 and output shaft 2, establish the velocity ratio of six gears.
The foundation of seven gears (overgear), second clutch C2 and second brake B2 is engaged.Specifically, second clutch C2 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and the 4th coupling member 8.Second brake B2 is engaged to make the first coupling member 5 be connected with case of transmission 3, prevents the first coupling member 5 relative to the rotation of case of transmission 3.Thus, between input shaft 1 and output shaft 2, set up the velocity ratio of seven gears.
The foundation of eight gears (overgear), second clutch C2 and the 3rd break B3 is engaged.Specifically, second clutch C2 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and the 4th coupling member 8.3rd break B3 is engaged to make the second coupling member 6 be connected with case of transmission 3, prevents the second coupling member 6 relative to the rotation of case of transmission 3.Thus, between input shaft 1 and output shaft 2, set up the velocity ratio of eight gears.
The foundation of nine gears (overgear), second clutch C2 and the first break B1 is engaged.Specifically, second clutch C2 is engaged to link together rotation to make first planet gear arrange sun gear 14, second epicyclic gear train sun gear 24 and the 4th coupling member 8.First break B1 is engaged to be connected with case of transmission 3 to make first planet gear rank carrier 13, prevents first planet gear to rank the rotation of carrier 13 relative to case of transmission 3.Thus, between input shaft 1 and output shaft 2, set up the velocity ratio of nine gears.
The velocity ratio of each gear, speed ratio step and each gear torque transmitter jointing state are as shown in the table:
In table: X represents joint and transmitting torque, O represents and engages but not transmitting torque.
Claims (1)
1. modified model nine shift transmission, comprises gearbox case and is installed on the input shaft of gearbox case inside, output shaft, epicyclic gear train group, coupling member group and torque transmitter, described epicyclic gear train group comprises the first planet gear row installed successively from front to back, second epicyclic gear train, third planet gear row and fourth planet gear row, each epicyclic gear train is by sun gear, planet carrier, planet wheel and gear ring are formed, and described torque transmitter comprises first clutch, second clutch, first break, second brake, 3rd break and the 4th break, each break is all connected with the housing of gearbox case, it is characterized in that: described coupling member group comprises the first coupling member, second coupling member, 3rd coupling member and the 4th coupling member, wherein the first coupling member connects the gear ring of first planet gear row and the gear ring of the second epicyclic gear train, second coupling member connects the sun gear that the planet carrier of the second epicyclic gear train and third planet gear are arranged, the planet carrier that the gear ring of the 3rd coupling member connection third planet gear row and fourth planet gear are arranged, the gear ring that the planet carrier of the 4th coupling member connection third planet gear row and fourth planet gear are arranged,
The planet carrier that described first break and first planet gear are arranged is connected, and second brake is connected with the first coupling member, and the 3rd break is connected with the second coupling member, and the planet carrier that the 4th break and third planet gear are arranged is connected;
The sun gear of the sun gear that described input shaft and first planet gear are arranged and the second epicyclic gear train is all connected, the planet carrier that output shaft is arranged with fourth planet gear is connected, the sun gear that input shaft is arranged by first clutch and fourth planet gear is connected, and is connected with the 4th coupling member by second clutch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510424619.XA CN105179615B (en) | 2015-07-17 | 2015-07-17 | A kind of nine speed transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510424619.XA CN105179615B (en) | 2015-07-17 | 2015-07-17 | A kind of nine speed transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105179615A true CN105179615A (en) | 2015-12-23 |
| CN105179615B CN105179615B (en) | 2018-02-27 |
Family
ID=54901924
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510424619.XA Expired - Fee Related CN105179615B (en) | 2015-07-17 | 2015-07-17 | A kind of nine speed transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105179615B (en) |
Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105736654A (en) * | 2016-04-20 | 2016-07-06 | 长安大学 | Two-stage gearbox of electric vehicle |
| CN107816519A (en) * | 2016-09-12 | 2018-03-20 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107816515A (en) * | 2016-09-12 | 2018-03-20 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107882933A (en) * | 2016-09-29 | 2018-04-06 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN110486426A (en) * | 2019-07-15 | 2019-11-22 | 中国北方车辆研究所 | A kind of nine-gear planetary automatic gearbox |
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN112324874A (en) * | 2020-11-30 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with stable step ratio |
| CN112324876A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with large speed ratio range |
| CN114001133A (en) * | 2021-10-26 | 2022-02-01 | 中国地质大学（武汉） | Nine-forward-gear automatic transmission |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101344147A (en) * | 2007-07-13 | 2009-01-14 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| CN101852278A (en) * | 2010-07-09 | 2010-10-06 | 中国北方车辆研究所 | Nine-gear planetary automatic transmission |
| CN102562969A (en) * | 2010-12-13 | 2012-07-11 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| CN102588533A (en) * | 2011-01-06 | 2012-07-18 | 通用汽车环球科技运作有限责任公司 | Torque transmitting device control strategy for a nine speed transmission |
| US20120214637A1 (en) * | 2011-02-17 | 2012-08-23 | GM Global Technology Operations LLC | Clutch and gear arrangement for a rear wheel drive vehicle |
| CN104565240A (en) * | 2014-12-26 | 2015-04-29 | 燕山大学 | Transmission with wider speed range |
-
2015
- 2015-07-17 CN CN201510424619.XA patent/CN105179615B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101344147A (en) * | 2007-07-13 | 2009-01-14 | 通用汽车环球科技运作公司 | Multi-speed transmission |
| CN101852278A (en) * | 2010-07-09 | 2010-10-06 | 中国北方车辆研究所 | Nine-gear planetary automatic transmission |
| CN102562969A (en) * | 2010-12-13 | 2012-07-11 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
| CN102588533A (en) * | 2011-01-06 | 2012-07-18 | 通用汽车环球科技运作有限责任公司 | Torque transmitting device control strategy for a nine speed transmission |
| US20120214637A1 (en) * | 2011-02-17 | 2012-08-23 | GM Global Technology Operations LLC | Clutch and gear arrangement for a rear wheel drive vehicle |
| CN104565240A (en) * | 2014-12-26 | 2015-04-29 | 燕山大学 | Transmission with wider speed range |
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105736654A (en) * | 2016-04-20 | 2016-07-06 | 长安大学 | Two-stage gearbox of electric vehicle |
| CN107816519B (en) * | 2016-09-12 | 2020-04-14 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN107816519A (en) * | 2016-09-12 | 2018-03-20 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107816515A (en) * | 2016-09-12 | 2018-03-20 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107816515B (en) * | 2016-09-12 | 2020-04-14 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN107882933A (en) * | 2016-09-29 | 2018-04-06 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN110486426A (en) * | 2019-07-15 | 2019-11-22 | 中国北方车辆研究所 | A kind of nine-gear planetary automatic gearbox |
| CN110486426B (en) * | 2019-07-15 | 2022-01-21 | 中国北方车辆研究所 | Nine-gear planetary automatic transmission |
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN112324876A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with large speed ratio range |
| CN112324877B (en) * | 2020-11-19 | 2023-04-18 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN112324874A (en) * | 2020-11-30 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with stable step ratio |
| CN114001133A (en) * | 2021-10-26 | 2022-02-01 | 中国地质大学（武汉） | Nine-forward-gear automatic transmission |
| CN114001133B (en) * | 2021-10-26 | 2023-04-18 | 中国地质大学（武汉） | Nine-forward-gear automatic transmission |
Also Published As
| Publication number | Publication date |
|---|---|
| CN105179615B (en) | 2018-02-27 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105179615A (en) | Improved nine-gear transmission | |
| CN105003633A (en) | Improved eight-gear transmission | |
| CN102758889B (en) | Multi-speed transmission | |
| CN105090394A (en) | Nine-gear speed changer | |
| CN102444698B (en) | Transmission having at least ten speeds | |
| CN102444697B (en) | There is the speed changer of at least ten grades | |
| CN102588530B (en) | Multi-speed transmission | |
| CN102644703B (en) | Multi-speed transmission | |
| CN102588529B (en) | Multi-speed transmission | |
| CN101839317B (en) | Multi-speed transmission | |
| CN103032531B (en) | Multi-speed transmission | |
| CN102889348B (en) | For controlling multi-speed transmission to produce the method for at least nine drive gears | |
| CN101545523B (en) | Multi-speed split dual clutch transmission | |
| CN103089937B (en) | Multi-speed transmission | |
| CN102954162B (en) | There is the multi-shifting speed variator of engine starting/stopping enabler | |
| CN103244617B (en) | Multi-speed transmission | |
| US20050101426A1 (en) | Transmission | |
| CN103133611B (en) | With the multi-speed transmission of stacked planetary gear set | |
| CN102588528B (en) | Multi-speed transmission having stacked planetary gear sets | |
| JP2016514808A (en) | Planetary gear type multi-stage transmission | |
| CN109764095B (en) | Nine-gear transmission | |
| CN102913597A (en) | Seven-level planet automatic speed changer | |
| CN104565238A (en) | 8-gear automatic transmission | |
| CN104373527A (en) | Getriebe mit dreifach-eingangskupplung | |
| CN103133612A (en) | Multi-speed transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20180227 Termination date: 20210717 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |