CN105003633A - Improved eight-gear transmission - Google Patents
Improved eight-gear transmission Download PDFInfo
- Publication number
- CN105003633A CN105003633A CN201510422364.3A CN201510422364A CN105003633A CN 105003633 A CN105003633 A CN 105003633A CN 201510422364 A CN201510422364 A CN 201510422364A CN 105003633 A CN105003633 A CN 105003633A
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- Prior art keywords
- gear
- planet
- coupling member
- break
- clutch
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
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- 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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- 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
- F16H2306/00—Shifting
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The invention provides an improved eight-gear transmission which mainly comprises an input shaft, an output shaft, planet gear rows, connecting components and torque transmission devices. The input shaft, the output shaft, the planet gear rows, the connecting components and the torque transmission devices are arranged in a transmission shell. Each planet gear row comprises a sun gear, a planet carrier, a planet wheel and a gear ring. Each torque transmission device comprises two clutches and four brakes, wherein the two clutches and the four brakes are connected selectively so that the sun wheels, the planet carriers, the gear rings and one of the five connecting components can rotate or can be fixed. In addition, at least two torque transmission devices can be connected selectively in a combined mode so that eight forward gear speed ratios and one reverse gear ratio can be established between the input shaft and the output component; the forward gears are five deceleration gears, one direct gear and two overspeed gears. The transmission is compact in structure, low in weight, small in size and easy to arrange on an automobile, and the speed ratio step among the gears of the transmission meets the requirement of the transmission.
Description
Technical field
The present invention relates to a kind of modified model eight 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 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 eight 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 eight 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, and 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 sun gear of first planet gear row and the sun gear of the second epicyclic gear train, second coupling member connects the gear ring of first planet gear row and the gear ring of the second epicyclic gear train, 3rd coupling member connects the gear ring that the planet carrier of the second epicyclic gear train and third 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 sun gear that the sun gear of 5-linked connection member connection third planet gear row and fourth planet gear are arranged,
Described first break is connected with the second coupling member, and the planet carrier that second brake is arranged with first planet gear is connected, and the 3rd break is connected with the 3rd coupling member, and the 4th break is connected with the 4th coupling member;
Described input shaft and the first coupling member are connected, the planet carrier that output shaft is arranged with fourth planet gear is connected, the planet carrier that input shaft is arranged by first clutch and third planet gear is connected, and is connected by the sun gear that second clutch and third planet gear are arranged.
As shown from the above technical solution, modified model eight shift transmission 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 planet carrier that input shaft and third 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 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; Second brake 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; 3rd break optionally engages to connect the 3rd coupling member and gearbox case, and object is to stop the 3rd 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 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) the first break and the 4th break engage, and realize the foundation of reversing gear, the velocity ratio reversed gear is-8;
2) second brake and the 4th break engage, and realize the foundation of a gear (slow down gear), the velocity ratio of a gear is 8;
3) second clutch and the 4th break engage, and realize the foundation of two gears (slow down gear), the velocity ratio of two gears is 5, and speed ratio step is 1.6;
4) second clutch and second brake engage, and realize the foundation of three gears (slow down gear), the velocity ratio of three gears is 3.5, and speed ratio step is 1.43.
5) second clutch and the 3rd break engage, and realize the foundation of four gears (slow down gear), the velocity ratio of four gears is 2.3, and speed ratio step is 1.52;
6) second clutch and the first break engage, and realize the foundation of five gears (slow down gear), the velocity ratio of five gears is 1.75, and speed ratio step is 1.31;
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 1.75;
8) first clutch and the first break 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) first 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.
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, 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 five 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 reaches 12, 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 two overgears is all less, is respectively 1.37 and 1.04, can transmission stably, improves the power performance of automobile.
Accompanying drawing explanation
Fig. 1 is the structure diagram of modified model eight 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, 9-5-linked connection 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.
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 of gearbox case 3,
Described coupling member group comprises the first coupling member 5, second coupling member 6, the 3rd coupling member 7, the 4th coupling member 8 and 5-linked connection member 9, and wherein first planet gear row's sun gear 14 and the second epicyclic gear train sun gear 24 interconnect by the first coupling member 5; First planet gear toothrow circle 11 and the second epicyclic gear train gear ring 21 interconnect by the second coupling member 6; Second epicyclic gear train planet carrier 33 and fourth planet gear toothrow circle 41 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; Third planet gear row sun gear 34 is arranged sun gear 44 with fourth planet gear and is interconnected by 5-linked connection member 9;
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 third planet gear seniority among brothers and sisters carrier 33 is interconnected; Input shaft 1 and 5-linked connection member 9 interconnect by second clutch C2; Described second coupling member 6 and gearbox case 3 interconnect by the first break B1; Described first planet gear seniority among brothers and sisters carrier 13 interconnects with gearbox case 3 by described second brake B2; Described 3rd coupling member 7 and gearbox case 3 interconnect by described 3rd break B3; Described 4th coupling member 8 and gearbox case 3 interconnect by described 4th break B4;
The output terminal of described input shaft 1 is connected with the first coupling member 5 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 modified model eight shift transmission 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, the first break B1 and the 4th break B4 engages.Specifically, the first break B1 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 3.4th 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), second brake B2 and the 4th break B4 is engaged.Specifically, second brake B2 is engaged to connect first planet gear seniority among brothers and sisters carrier 13 and gearbox case 3, prevents first planet gear to rank the rotation of carrier 13 relative to 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 a gear.
The foundation of two gears (slow down gear), second clutch C2 and the 4th break B4 is engaged.Specifically, second clutch C2 is engaged rotates together with input shaft 1 to connect 5-linked connection member 9.4th 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.The velocity ratio of two gears is established thus between input shaft 1 and output shaft 2.
The foundation of three gears (slow down gear), second clutch C2 and second brake B2 is engaged.Specifically, second clutch C2 is engaged rotates together with input shaft 1 to connect 5-linked connection member 9.Second brake B2 is engaged to be connected with gearbox case 3 to make first planet gear rank carrier 13, prevents first planet gear to rank the rotation of carrier 13 relative to 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), second clutch C2 and the 3rd break B3 is engaged.Specifically, second clutch C2 is engaged rotates together with input shaft 1 to connect 5-linked connection member 9.3rd break B3 is engaged to make the 3rd coupling member 7 be connected with gearbox case 3, prevents the 3rd coupling member 7 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), second clutch C2 and the first break B1 is engaged.Specifically, second clutch C2 is engaged rotates together with input shaft 1 to connect 5-linked connection member 9.First break B1 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 five gears.
The foundation of six gears (directly keeping off), first clutch C1 and second clutch C2 is engaged.Specifically, the engaged input shaft 1 that connects of first clutch C1 rotates together with planet carrier 33.Second clutch C2 is engaged to be rotated together with the 4th coupling member 9 to connect input shaft 1.Thus, between input shaft 1 and output shaft 2, establish the velocity ratio of six gears.
The foundation of seven gears (overgear), first clutch C1 and the first break B1 is engaged.Specifically, the engaged input shaft 1 that connects of first clutch C1 rotates together with planet carrier 33.First break B1 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 seven gears.
The foundation of eight gears (overgear), first clutch C1 and the 3rd break B3 is engaged.Specifically, the engaged input shaft 1 that connects of first clutch C1 rotates together with planet carrier 33.3rd break B3 is engaged to make the 3rd coupling member 7 be connected with gearbox case 3, prevents the 3rd coupling member 7 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. modified model eight 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, 4th coupling member and 5-linked connection member, wherein the first coupling member connects the sun gear of first planet gear row and the sun gear of the second epicyclic gear train, second coupling member connects the gear ring of first planet gear row and the gear ring of the second epicyclic gear train, 3rd coupling member connects the gear ring that the planet carrier of the second epicyclic gear train and third 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 sun gear that the sun gear of 5-linked connection member connection third planet gear row and fourth planet gear are arranged,
Described first break is connected with the second coupling member, and the planet carrier that second brake is arranged with first planet gear is connected, and the 3rd break is connected with the 3rd coupling member, and the 4th break is connected with the 4th coupling member;
Described input shaft and the first coupling member are connected, the planet carrier that output shaft is arranged with fourth planet gear is connected, the planet carrier that input shaft is arranged by first clutch and third planet gear is connected, and is connected by the sun gear that second clutch and third planet gear are arranged.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510422364.3A CN105003633B (en) | 2015-07-17 | 2015-07-17 | A kind of shift transmission of modified eight |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510422364.3A CN105003633B (en) | 2015-07-17 | 2015-07-17 | A kind of shift transmission of modified eight |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105003633A true CN105003633A (en) | 2015-10-28 |
| CN105003633B CN105003633B (en) | 2017-11-07 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510422364.3A Expired - Fee Related CN105003633B (en) | 2015-07-17 | 2015-07-17 | A kind of shift transmission of modified eight |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105003633B (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106402293A (en) * | 2016-09-30 | 2017-02-15 | 中国北方车辆研究所 | Eight-gear automatic planetary transmission |
| CN106917849A (en) * | 2017-04-27 | 2017-07-04 | 广州汽车集团股份有限公司 | Eight speed automatic transmissions |
| CN107035828A (en) * | 2016-02-03 | 2017-08-11 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| WO2019020129A1 (en) * | 2017-07-25 | 2019-01-31 | 罗灿 | Reverse-type connection planetary row transmission mechanism |
| CN109812550A (en) * | 2019-02-28 | 2019-05-28 | 东华大学 | A kind of eight gear gearboxes of bull-dozer |
| CN109854690A (en) * | 2018-12-21 | 2019-06-07 | 中国北方车辆研究所 | A kind of eight-gear planetary automatic speed changer |
| CN110608270A (en) * | 2019-09-24 | 2019-12-24 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN112984060A (en) * | 2021-04-27 | 2021-06-18 | 北京航空航天大学 | Eight-front two-reverse planetary gear automatic transmission |
| CN113251119A (en) * | 2021-06-03 | 2021-08-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission |
| CN116379112A (en) * | 2023-06-05 | 2023-07-04 | 北京航空航天大学 | Multi-gear planetary gear speed change mechanism and automatic speed changer thereof |
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| JP2008215396A (en) * | 2007-02-28 | 2008-09-18 | Aisin Aw Co Ltd | Automatic transmission |
| CN202418448U (en) * | 2012-01-13 | 2012-09-05 | 江福荣 | Composite type automatic stepless speed change device |
| CN104565238A (en) * | 2014-12-26 | 2015-04-29 | 燕山大学 | 8-gear automatic transmission |
| CN104595435A (en) * | 2014-12-26 | 2015-05-06 | 燕山大学 | Eight-gear transmission |
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2015
- 2015-07-17 CN CN201510422364.3A patent/CN105003633B/en not_active Expired - Fee Related
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080020890A1 (en) * | 2006-07-20 | 2008-01-24 | Hyu Tae Shim | Power train of automatic transmission |
| JP2008215396A (en) * | 2007-02-28 | 2008-09-18 | Aisin Aw Co Ltd | Automatic transmission |
| CN202418448U (en) * | 2012-01-13 | 2012-09-05 | 江福荣 | Composite type automatic stepless speed change device |
| CN104565238A (en) * | 2014-12-26 | 2015-04-29 | 燕山大学 | 8-gear automatic transmission |
| CN104595435A (en) * | 2014-12-26 | 2015-05-06 | 燕山大学 | Eight-gear transmission |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107035828A (en) * | 2016-02-03 | 2017-08-11 | 现代自动车株式会社 | Epicyclic train for the automatic transmission of vehicle |
| CN106402293A (en) * | 2016-09-30 | 2017-02-15 | 中国北方车辆研究所 | Eight-gear automatic planetary transmission |
| CN106917849A (en) * | 2017-04-27 | 2017-07-04 | 广州汽车集团股份有限公司 | Eight speed automatic transmissions |
| WO2019020129A1 (en) * | 2017-07-25 | 2019-01-31 | 罗灿 | Reverse-type connection planetary row transmission mechanism |
| CN109854690A (en) * | 2018-12-21 | 2019-06-07 | 中国北方车辆研究所 | A kind of eight-gear planetary automatic speed changer |
| CN109812550A (en) * | 2019-02-28 | 2019-05-28 | 东华大学 | A kind of eight gear gearboxes of bull-dozer |
| CN110608270A (en) * | 2019-09-24 | 2019-12-24 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN110608270B (en) * | 2019-09-24 | 2024-05-14 | 陕西法士特齿轮有限责任公司 | Hydraulic automatic transmission |
| CN112984060A (en) * | 2021-04-27 | 2021-06-18 | 北京航空航天大学 | Eight-front two-reverse planetary gear automatic transmission |
| CN113251119A (en) * | 2021-06-03 | 2021-08-13 | 北方汤臣传动科技有限公司 | Eight-gear automatic transmission |
| CN116379112A (en) * | 2023-06-05 | 2023-07-04 | 北京航空航天大学 | Multi-gear planetary gear speed change mechanism and automatic speed changer thereof |
| CN116379112B (en) * | 2023-06-05 | 2023-07-28 | 北京航空航天大学 | Multi-gear planetary gear speed change mechanism and automatic speed changer thereof |
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| CN105003633B (en) | 2017-11-07 |
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