CN105065589A - Eight-gear transmission - Google Patents
Eight-gear transmission Download PDFInfo
- Publication number
- CN105065589A CN105065589A CN201510422368.1A CN201510422368A CN105065589A CN 105065589 A CN105065589 A CN 105065589A CN 201510422368 A CN201510422368 A CN 201510422368A CN 105065589 A CN105065589 A CN 105065589A
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- Prior art keywords
- gear
- planet
- coupling member
- break
- clutch
- 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.)
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four sets of orbital gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides an eight-gear transmission. The eight-gear transmission mainly comprises an input shaft, an output shaft, planetary gear rows, a connecting component and torque transmission devices, wherein all the components are arranged in a transmission shell. Each planetary gear row comprises a sun gear, a gear ring, a planet carrier and a planet gear supported by the planet carrier. The torque transmission devices comprise two clutches and four brakes, wherein the two clutches and the four brakes are selectively connected to enable the sun gears, the planet carriers, the gear rings and one of the five connecting components to rotate or be fixed. Furthermore, at least two of the torque transmission devices can be selectively combined so that eight forward gear speed ratios and a reverse gear speed ratio can be established between the input shaft and the output shaft, and forward gears include five deceleration gears, one direct gear and two overgears. The transmission is compact in structure, lighter and small and can be arranged easily on an automobile. The step speed ratio between the transmission ratios of the gears of the transmission meets the requirement of the transmission.
Description
Technical field
The present invention relates to a kind of eight shift transmissions, 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 to be determined, therefore the improvement of speed changer is mainly improved to the performance of speed changer, when speed changer composition component remains unchanged substantially, how by improving the annexation of 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 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 eight shift transmissions of the difficulty controlled and the ratio coverage expanding speed changer.
Realizing the technological scheme that the object of the invention adopts is, a kind of eight shift transmissions, comprise 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, 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, described coupling member group comprises the first coupling member, second coupling member, 3rd coupling member, 4th coupling member and 5-linked connection 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 planet carrier of first planet gear row and the planet carrier of the second epicyclic gear train, the planet carrier that the gear ring of the 3rd coupling member connection third planet gear row and fourth planet gear are arranged, 4th coupling member connects the gear ring that the planet carrier of third planet gear row and fourth planet gear are arranged, and 5-linked connection member connects the sun gear that the planet carrier of the second epicyclic gear train and third planet gear are arranged,
Described first break connects the sun gear of first planet gear row, and second brake connects the planet carrier of the second epicyclic gear train, and the 3rd break connects the first coupling member, and the 4th break connects the planet carrier of third planet gear row;
The sun gear of described input shaft and the second epicyclic gear train is 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, eight shift transmissions provided by the invention, realize speed changer eight 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 sun gear and the gearbox case that connect first planet gear row, and object is the rotation of the sun gear in order to stop first planet gear to be arranged relative to gearbox case; Second brake optionally engages the planet carrier and the gearbox case that connect the second epicyclic gear train, and the planet carrier of the second epicyclic gear train is connected with the second coupling member, and object is to stop the second coupling member relative to the rotation of gearbox case; 3rd break 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; 4th break optionally engages the planet carrier and the gearbox case that connect third planet gear row, and the planet carrier of third planet gear row is connected with the 4th coupling member, 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 five coupling members) is rotated or fixes, and wherein torque transmitter optionally can engage can set up eight 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, eight forward gears comprise five gears that slow down, a direct gear and two overgears, are specially:
1) second brake and the 4th break engage, and realize the foundation of reversing gear, the velocity ratio reversed gear is-9;
2) first clutch and the first break engage, and realize the foundation of a gear (slow down gear), the velocity ratio of a gear is 7.15;
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 3.9, and speed ratio step is 1.83;
4) the first break and the 4th break engage, and realize the foundation of three gears (slow down gear), the velocity ratio of three gears is 2.67, and speed ratio step is 1.46.
5) first clutch and second brake engage, and realize the foundation of four gears (slow down gear), the velocity ratio of four gears is 1.97, and speed ratio step is 1.36;
6) first clutch and the 3rd break engage, and realize the foundation of five gears (slow down gear), the velocity ratio of five gears is 1.62, and speed ratio step is 1.22;
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 1.62;
8) second clutch and the 3rd break engage, and realize the foundation of seven gears (overgear), and the velocity ratio of seven gears is 0.72, and speed ratio step is 1.39;
9) second clutch and second brake engage, and realize the foundation of eight gears (overgear), and the velocity ratio of eight gears is 0.67, and speed ratio step is 1.07.
Compared with prior art, beneficial effect of the present invention is:
1, eight shift transmissions provided by the invention adopt 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, eight 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), controls simple;
4, this speed changer utilizes coupling member to be linked together by the component of different gear train, can form new transmission mechanism, and the quantity of coupling member and the difference of position will cause the transmission mechanism difference in essence formed.This speed changer utilizes five coupling members, connecting mode empirical tests is feasible, and make the total slewing range of each gear to reach 10.6 by the special parameter that preferably obtains, than the slewing range 7.37 of the ZF8 speed transmission of classics and the slewing range 6.71 of Lexus LS460 speed changer wider;
5, through preferably, the speed ratio step of two overgears is all less, is respectively 1.39 and 1.07, can steadily transmission, the power performance of raising automobile.
Accompanying drawing explanation
Fig. 1 is the structure diagram of eight shift transmissions provided by the invention.
Wherein, 1-input shaft, 2-output shaft, 3-gearbox case, 4-5-linked connection member, 5-first coupling member, 6-second coupling member, 7-the 3rd coupling member, 8-the 4th coupling member, 2-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.
Eight shift transmissions 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, 3rd coupling member 7, 4th coupling member 8 and 5-linked connection member 4, wherein first planet gear toothrow circle 2 and the second epicyclic gear train gear ring 21 interconnect by the first coupling member 5, second coupling member 6 by first planet gear seniority among brothers and sisters carrier 13 and the second epicyclic gear train planet carrier 23 interconnected, 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, second epicyclic gear train planet carrier 23 is arranged sun gear 34 with third planet gear and is interconnected by 5-linked connection member 4,
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, and wherein input shaft 1 and fourth planet gear row sun gear 44 interconnect by first clutch C1; Second clutch C2 is by input shaft and the interconnection of the 4th coupling member; First planet gear row's sun gear 14 and gearbox case 3 interconnect by the first break B1; Second coupling member and gearbox case interconnect by second brake B2; 3rd break B3 is by the first coupling member and gearbox case interconnection; Third planet gear seniority among brothers and sisters carrier 33 interconnects with gearbox case 3 by the 4th break B4;
The output terminal of described input shaft 1 is connected with the second epicyclic gear train sun gear 24 all the time, 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 eight shift transmissions provided by the invention is introduced, this speed changer can realize eight 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 B3 and the 4th break B4 engages.Specifically, the 3rd break B3 is engaged to make the first coupling member 5 be connected with gearbox case 3, prevents the first coupling member relative to the rotation of gearbox case 3.4th break B4 is engaged to make the 4th coupling member 8 be connected with gearbox case 3, prevents the 4th coupling member 8 relative to the rotation of gearbox case 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), first clutch C1 and the first break B1 is engaged.Specifically, first clutch C1 is engaged rotates together with sun gear 44 to connect sun gear 24.First break B1 is engaged to make sun gear 14 be connected with gearbox case 3, prevents sun gear 14 relative to the rotation of gearbox case 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 rotates together with sun gear 44 to connect sun gear 24.4th break B4 is engaged to make the 4th coupling member 8 be connected with gearbox case 3, prevents the 4th coupling member 8 relative to the rotation of gearbox case 3.Result in formation of the transmission of single planetary gear row, between input shaft 1 and output shaft 2, establish the velocity ratio of two gears thus.
The foundation of three gears (slow down gear), the first break B1 and the 4th break B4 is engaged.Specifically, the first break B1 is engaged to make sun gear 14 be connected with gearbox case 3, prevents sun gear 14 relative to the rotation of gearbox case 3.4th break B4 is engaged to make the 4th coupling member 8 be connected with gearbox case 3, prevents the 4th coupling member 8 relative to the rotation of gearbox case 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 second brake B2 is engaged.Specifically, first clutch C1 is engaged rotates together with sun gear 44 to connect sun gear 24.Second brake B2 is engaged to make the second coupling member 6 be connected with gearbox case 3, prevents the second coupling member 6 relative to the rotation of gearbox case 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 the 3rd break B3 is engaged.Specifically, first clutch C1 is engaged rotates together with sun gear 44 to connect sun gear 24.3rd break B3 is engaged to make the first coupling member 5 be connected with gearbox case 3, prevents the first coupling member 5 relative to the rotation of gearbox case 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 rotates together with sun gear 44 to connect sun gear 24.Second clutch C2 is engaged to be rotated together with the 4th coupling member 8 to connect sun gear 24.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 the 3rd break B3 is engaged.Specifically, second clutch C2 is engaged rotates together with the 4th coupling member 8 to connect sun gear 24.3rd break B3 is engaged to make the first coupling member 5 be connected with gearbox case 3, prevents the first coupling member 5 relative to the rotation of gearbox case 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 second brake B2 is engaged.Specifically, second clutch C2 is engaged rotates together with the 4th coupling member 8 to connect sun gear 24.Second brake B2 is engaged to make the second coupling member 6 be connected with gearbox case 3, prevents the second coupling member 6 relative to the rotation of gearbox case 3.Thus, between input shaft 1 and output shaft 2, set up the velocity ratio of eight 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. a shift transmission, comprise 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, 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, 4th coupling member and 5-linked connection 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 planet carrier of first planet gear row and the planet carrier of the second epicyclic gear train, the planet carrier that the gear ring of the 3rd coupling member connection third planet gear row and fourth planet gear are arranged, 4th coupling member connects the gear ring that the planet carrier of third planet gear row and fourth planet gear are arranged, and 5-linked connection member connects the sun gear that the planet carrier of the second epicyclic gear train and third planet gear are arranged,
Described first break connects the sun gear of first planet gear row, and second brake connects the planet carrier of the second epicyclic gear train, and the 3rd break connects the first coupling member, and the 4th break connects the planet carrier of third planet gear row;
The sun gear of described input shaft and the second epicyclic gear train is 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 |
|---|---|---|---|
| CN201510422368.1A CN105065589A (en) | 2015-07-17 | 2015-07-17 | Eight-gear transmission |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510422368.1A CN105065589A (en) | 2015-07-17 | 2015-07-17 | Eight-gear transmission |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105065589A true CN105065589A (en) | 2015-11-18 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510422368.1A Pending CN105065589A (en) | 2015-07-17 | 2015-07-17 | Eight-gear transmission |
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| CN (1) | CN105065589A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107100968A (en) * | 2016-02-19 | 2017-08-29 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN109812550A (en) * | 2019-02-28 | 2019-05-28 | 东华大学 | A kind of eight gear gearboxes of bull-dozer |
| CN111750047A (en) * | 2019-03-29 | 2020-10-09 | 长城汽车股份有限公司 | Multi-gear planetary row type automatic transmission, control method thereof and vehicle |
| CN112324875A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
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| CN101067440A (en) * | 2006-02-14 | 2007-11-07 | Zf腓德烈斯哈芬股份公司 | Multi-shifting speed variator |
| CN101109433A (en) * | 2006-02-14 | 2008-01-23 | Zf腓德烈斯哈芬股份公司 | Multi-speed transmission |
| US20090264244A1 (en) * | 2008-04-21 | 2009-10-22 | Gm Global Technology Operations, Inc. | Eight speed automatic transmission |
| DE102008041207A1 (en) * | 2008-08-13 | 2010-02-18 | Zf Friedrichshafen Ag | Multi-speed transmission |
| CN102644710A (en) * | 2011-02-17 | 2012-08-22 | 通用汽车环球科技运作有限责任公司 | Clutch and gear arrangement for rear wheel drive vehicle |
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2015
- 2015-07-17 CN CN201510422368.1A patent/CN105065589A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101067440A (en) * | 2006-02-14 | 2007-11-07 | Zf腓德烈斯哈芬股份公司 | Multi-shifting speed variator |
| CN101109433A (en) * | 2006-02-14 | 2008-01-23 | Zf腓德烈斯哈芬股份公司 | Multi-speed transmission |
| US20090264244A1 (en) * | 2008-04-21 | 2009-10-22 | Gm Global Technology Operations, Inc. | Eight speed automatic transmission |
| DE102008041207A1 (en) * | 2008-08-13 | 2010-02-18 | Zf Friedrichshafen Ag | Multi-speed transmission |
| CN102644710A (en) * | 2011-02-17 | 2012-08-22 | 通用汽车环球科技运作有限责任公司 | Clutch and gear arrangement for rear wheel drive vehicle |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107100968A (en) * | 2016-02-19 | 2017-08-29 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN107100968B (en) * | 2016-02-19 | 2021-03-12 | 现代自动车株式会社 | Planetary gear train of automatic transmission for vehicle |
| CN109812550A (en) * | 2019-02-28 | 2019-05-28 | 东华大学 | A kind of eight gear gearboxes of bull-dozer |
| CN109812550B (en) * | 2019-02-28 | 2022-03-04 | 东华大学 | Eight-gear gearbox for bulldozer |
| CN111750047A (en) * | 2019-03-29 | 2020-10-09 | 长城汽车股份有限公司 | Multi-gear planetary row type automatic transmission, control method thereof and vehicle |
| CN112324875A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
| CN112324875B (en) * | 2020-11-19 | 2023-04-18 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
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Application publication date: 20151118 |