CN105927717B - A kind of six speed automatic transmission of list double pinions combined type - Google Patents
A kind of six speed automatic transmission of list double pinions combined type Download PDFInfo
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- CN105927717B CN105927717B CN201610394747.9A CN201610394747A CN105927717B CN 105927717 B CN105927717 B CN 105927717B CN 201610394747 A CN201610394747 A CN 201610394747A CN 105927717 B CN105927717 B CN 105927717B
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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
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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
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three 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
- F16H2200/2051—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with eight engaging means
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Abstract
Description
技术领域technical field
本发明涉及一种单双级行星齿轮组合式六挡自动变速器。The invention relates to a single and double-stage planetary gear combined six-speed automatic transmission.
背景技术Background technique
自动变速器主要包括行星齿轮单元、离合器和制动器。自动变速器是通过自动变速器油进行能量转换和动力传递，利用油泵、油路回路、离合器、行星齿轮组、多个电磁阀等零部件实现自动变速，为人们的汽车驾驶带来轻松简便的驾驭感受。An automatic transmission mainly includes a planetary gear unit, clutches and brakes. The automatic transmission uses automatic transmission oil for energy conversion and power transmission, and uses oil pumps, oil circuits, clutches, planetary gear sets, multiple solenoid valves and other components to realize automatic transmission, bringing easy and simple driving experience to people's car driving .
而现有的双离合自动变速器具有两个动力输入离合器，其中一个离合器负责奇数档的动力输入，另一个离合器负责偶数档的动力输入，它具有换挡平稳、舒适性好、节油的优点。目前，现有的双离合自动变速器一般采用平行轴式齿轮结构，该结构的自动变速器结构不够紧凑，执行元件多、换挡时执行元件变换多、容易造成运动干涉。And existing double-clutch automatic transmission has two power input clutches, and wherein a clutch is responsible for the power input of odd-numbered gears, and another clutch is responsible for the power input of even-numbered gears, and it has the advantages of smooth shifting, good comfort, and fuel economy. At present, the existing dual-clutch automatic transmission generally adopts a parallel-shaft gear structure. The structure of the automatic transmission with this structure is not compact enough, there are many actuators, and the actuators are changed during gear shifting, which is easy to cause motion interference.
发明内容Contents of the invention
本发明目的是针对现有技术存在的缺陷提供一种单双级行星齿轮组合式六挡自动变速器。The purpose of the present invention is to provide a single-stage and double-stage planetary gear combined six-speed automatic transmission aiming at the defects in the prior art.
本发明为实现上述目的，采用如下技术方案：一种单双级行星齿轮组合式六挡自动变速器，包括由前排行星架6、前排行星齿轮7、前排太阳轮和前排齿圈构成的前排单级行星齿轮机构，由中排行星架13、中排第一行星齿轮11、中排第二行星齿轮10、中排太阳轮和中排齿圈构成的中排双级行星齿轮机构，以及由后排行星架15、后排行星齿轮17、后排太阳轮16和后排齿圈18构成的后排单级行星齿轮机构；其中，所述前排太阳轮和中排太阳轮合制成共用的前中排太阳轮8，所述前排齿圈和中排齿圈制成共用的前中排齿圈9；In order to achieve the above object, the present invention adopts the following technical scheme: a single- and double-stage planetary gear combined six-speed automatic transmission, comprising a front row planetary carrier 6, a front row planetary gear 7, a front row sun gear and a front row ring gear The front-row single-stage planetary gear mechanism is a middle-row double-stage planetary gear mechanism composed of the middle-row planet carrier 13, the middle-row first planetary gear 11, the middle-row second planetary gear 10, the middle-row sun gear and the middle-row ring gear. , and the rear single-stage planetary gear mechanism composed of the rear planetary carrier 15, the rear planetary gear 17, the rear sun gear 16 and the rear ring gear 18; wherein, the front sun gear and the middle row sun gear are combined A common front middle row sun gear 8 is made, and the front middle row ring gear and the middle row ring gear are made into a common front middle row ring gear 9;
动力输入轴1的第一输出端分别与第一离合器2、第二离合器4以及第三离合器14的输入端连接，所述第一离合器2的输出端与所述前排行星架6连接，所述第二离合器4的输出端与所述前中排太阳轮8连接，所述第三离合器14的输出端与所述中排行星架13连接，所述前中排齿圈9与后排齿圈18相连接，所述后排齿圈18的输出端通过第四离合器19与所述后排太阳轮16连接，所述后排行星架15的输出端与动力输出轴21连接；The first output end of the power input shaft 1 is respectively connected with the input ends of the first clutch 2, the second clutch 4 and the third clutch 14, and the output end of the first clutch 2 is connected with the front planetary carrier 6, so The output end of the second clutch 4 is connected to the front middle row sun gear 8, the output end of the third clutch 14 is connected to the middle row planet carrier 13, and the front middle row ring gear 9 is connected to the rear row of gears. The ring 18 is connected, the output end of the rear ring gear 18 is connected with the rear sun gear 16 through the fourth clutch 19, and the output end of the rear planet carrier 15 is connected with the power output shaft 21;
其中，所述第一离合器2与所述前排行星架6之间设置有用于对所述前排行星架6制动的第一制动器3；所述第二离合器4与所述前中排太阳轮8之间设置有用于对所述前中排太阳轮8制动的第二制动器5；所述第三离合器14与所述中排行星架13之间设置有用于对所述中排行星架13制动的第三制动器12；所述第四离合器19与所述后排太阳轮16之间设置有用于对所述后排太阳轮16制动的第四制动器20。Wherein, a first brake 3 for braking the front row planet carrier 6 is provided between the first clutch 2 and the front row planet carrier 6; the second clutch 4 is connected to the front middle row sun A second brake 5 for braking the front middle row sun gear 8 is provided between the wheels 8; a second brake 5 for braking the middle row planet carrier 13 is provided between the third clutch 14 and the middle row planet carrier 13 13 a third brake 12 for braking; a fourth brake 20 for braking the rear sun gear 16 is provided between the fourth clutch 19 and the rear sun gear 16 .
本发明的有益效果：本发明的自动变速器具有结构简单紧凑、加工零件类型少、成本低、执行元件少、换挡时执行元件变换少、不易运动干涉的特点。Beneficial effects of the present invention: the automatic transmission of the present invention has the characteristics of simple and compact structure, few types of machined parts, low cost, few actuators, less change of actuators during gear shifting, and less movement interference.
附图说明Description of drawings
图1本发明的结构示意图。Fig. 1 is a structural schematic diagram of the present invention.
具体实施方式Detailed ways
图1所示，涉及一种单双级行星齿轮组合式六挡自动变速器，包括由前排行星架6、前排行星齿轮7、前排太阳轮和前排齿圈构成的前排单级行星齿轮机构，由中排行星架13、中排第一行星齿轮11、中排第二行星齿轮10、中排太阳轮和中排齿圈构成的中排双级行星齿轮机构，以及由后排行星架15、后排行星齿轮17、后排太阳轮16和后排齿圈18构成的后排单级行星齿轮机构；其中，所述前排太阳轮和中排太阳轮合制成共用的前中排太阳轮8，所述前排齿圈和中排齿圈制成共用的前中排齿圈9；As shown in Figure 1, it involves a single- and double-stage planetary gear combined six-speed automatic transmission, including a front row single-stage planetary gear consisting of a front row planetary carrier 6, a front row planetary gear 7, a front row sun gear and a front row ring gear. The gear mechanism is a middle-row double-stage planetary gear mechanism consisting of the middle-row planetary carrier 13, the middle-row first planetary gear 11, the middle-row second planetary gear 10, the middle-row sun gear and the middle-row ring gear, and the rear-row planetary gear The rear row single-stage planetary gear mechanism composed of frame 15, rear row planetary gear 17, rear row sun gear 16 and rear row ring gear 18; Row of sun gears 8, the front and middle row of ring gears are made into a common front and middle row of ring gears 9;
动力输入轴1的第一输出端分别与第一离合器2、第二离合器4以及第三离合器14的输入端连接，所述第一离合器2的输出端与所述前排行星架6连接，所述第二离合器4的输出端与所述前中排太阳轮8连接，所述第三离合器14的输出端与所述中排行星架13连接，所述前中排齿圈9与后排齿圈18相连接，所述后排齿圈18的输出端通过第四离合器19与所述后排太阳轮16连接，所述后排行星架15的输出端与动力输出轴21连接；The first output end of the power input shaft 1 is respectively connected with the input ends of the first clutch 2, the second clutch 4 and the third clutch 14, and the output end of the first clutch 2 is connected with the front planetary carrier 6, so The output end of the second clutch 4 is connected to the front middle row sun gear 8, the output end of the third clutch 14 is connected to the middle row planet carrier 13, and the front middle row ring gear 9 is connected to the rear row of gears. The ring 18 is connected, the output end of the rear ring gear 18 is connected with the rear sun gear 16 through the fourth clutch 19, and the output end of the rear planet carrier 15 is connected with the power output shaft 21;
其中，所述第一离合器2与所述前排行星架6之间设置有用于对所述前排行星架6制动的第一制动器3；所述第二离合器4与所述前中排太阳轮8之间设置有用于对所述前中排太阳轮8制动的第二制动器5；所述第三离合器14与所述中排行星架13之间设置有用于对所述中排行星架13制动的第三制动器12；所述第四离合器19与所述后排太阳轮16之间设置有用于对所述后排太阳轮16制动的第四制动器20。Wherein, a first brake 3 for braking the front row planet carrier 6 is provided between the first clutch 2 and the front row planet carrier 6; the second clutch 4 is connected to the front middle row sun A second brake 5 for braking the front middle row sun gear 8 is provided between the wheels 8; a second brake 5 for braking the middle row planet carrier 13 is provided between the third clutch 14 and the middle row planet carrier 13 13 a third brake 12 for braking; a fourth brake 20 for braking the rear sun gear 16 is provided between the fourth clutch 19 and the rear sun gear 16 .
本发明的自动变速器由三排行星齿轮机构、离合器、制动器组成，前排与后排行星齿轮机构为单级式，中排行星齿轮机构为双级式，离合器、制动器均为片式结构。前排、中排与后排行星齿轮机构的太阳轮与齿圈的各参数完全相同，其参数合理配置可形成6个传动比合理分布的挡位，且各挡工作时动力传递路线简单。The automatic transmission of the present invention is made up of three rows of planetary gear mechanisms, clutches and brakes. The front row and rear row planetary gear mechanisms are single-stage, the middle row of planetary gear mechanisms is double-stage, and the clutches and brakes are plate structures. The parameters of the sun gear and the ring gear of the front row, middle row and rear row planetary gear mechanism are exactly the same, and the reasonable configuration of the parameters can form 6 gears with reasonable distribution of transmission ratio, and the power transmission route is simple when each gear is working.
使用时，假设太阳轮齿数为Z1，齿圈齿数为Z2，则可令α＝Z2/Z1。以下为各挡动力传递路线和传动比计算。In use, assuming that the number of teeth of the sun gear is Z 1 and the number of teeth of the ring gear is Z 2 , then α=Z 2 /Z 1 can be set. The following is the calculation of the power transmission route and transmission ratio of each gear.
1挡：第二离合器4、第三制动器12、第四制动器20工作。动力从动力输入轴1经第二离合器4由前中排太阳轮8输入，经中排第一行星齿轮11、中排第二行星齿轮10、前中排齿圈9、后排齿圈18、后排行星齿轮17、后排行星架15、动力输出轴21输出动力。根据运动关系式计算，1挡传动比i1＝1+α。1st gear: the second clutch 4, the third brake 12, and the fourth brake 20 work. The power is input from the power input shaft 1 through the second clutch 4 from the front middle row sun gear 8, through the middle row first planetary gear 11, the middle row second planetary gear 10, the front middle row ring gear 9, the rear row ring gear 18, Rear row planetary gear 17, rear row planetary carrier 15, power take-off shaft 21 output power. Calculated according to the kinematic relational formula, the transmission ratio i 1 of the first gear = 1+α.
2挡：第二制动器5、第三离合器14、第四制动器20工作。动力从动力输入轴1经第三离合器14由中排行星架13输入，经中排第二行星齿轮10、前中排齿圈9、后排齿圈18、后排行星齿轮17、后排行星架15、动力输出轴21输出动力。根据运动关系式计算，2挡传动比i2＝(α+1)/(α-1)。2nd gear: the second brake 5, the third clutch 14, and the fourth brake 20 work. The power is input from the power input shaft 1 through the third clutch 14 and the middle planetary carrier 13, then through the second middle planetary gear 10, the front middle ring gear 9, the rear ring gear 18, the rear planetary gear 17, and the rear planetary gear Frame 15, power output shaft 21 output power. Calculated according to the kinematic relational formula, the transmission ratio i 2 of the second gear = (α+1)/(α-1).
3挡：第二离合器4、第三制动器12、第四离合器19工作。动力从动力输入轴1经第二离合器4由前中排太阳轮8输入，经中排第一行星齿轮11、中排第二行星齿轮10、前中排齿圈9，再同时经后排齿圈18与第四离合器19、后排太阳轮16传给后排行星齿轮17，再经后排行星架15、动力输出轴21输出动力。根据运动关系式计算，3挡传动比i3＝α。3rd gear: the second clutch 4, the third brake 12, and the fourth clutch 19 work. The power is input from the power input shaft 1 through the second clutch 4, from the front middle row sun gear 8, through the middle row first planetary gear 11, the middle row second planetary gear 10, the front middle row ring gear 9, and at the same time through the rear row gear Circle 18 and the 4th clutch 19, rear row sun gear 16 pass to rear row planetary gear 17, then through rear row planet carrier 15, power output shaft 21 output power. Calculated according to the kinematic relational formula, the transmission ratio i 3 of the third gear = α.
4挡：第一离合器2、第二离合器4、第四制动器20工作。动力从动力输入轴1同时经第一离合器2与第二离合器4传给前排行星架6与前中排太阳轮8，再经前排行星齿轮7、前中排齿圈9、后排齿圈18、后排行星齿轮17、后排行星架15、动力输出轴21输出动力。根据运动关系式计算，4挡传动比i4＝(1+α)/α。4th gear: the first clutch 2, the second clutch 4, and the fourth brake 20 work. The power is transmitted from the power input shaft 1 to the front planetary carrier 6 and the front middle row sun gear 8 through the first clutch 2 and the second clutch 4 at the same time, and then through the front row planetary gear 7, the front middle row ring gear 9, and the rear row of gears. Circle 18, rear row planetary gear 17, rear row planet carrier 15, power output shaft 21 output power. Calculated according to the kinematic relational formula, the transmission ratio i 4 of the fourth gear = (1+α)/α.
5挡：第一离合器2、第二离合器4、第四离合器19工作。动力从动力输入轴1同时经第一离合器2与第二离合器4传给前排行星架6与前中排太阳轮8，再经前排行星齿轮7传给前中排齿圈9，再同时经后排齿圈18与第四离合器19、后排太阳轮16传给后排行星齿轮17，再经后排行星架15、动力输出轴21输出动力。根据运动关系式计算，5挡传动比i5＝1。5th gear: the first clutch 2, the second clutch 4, and the fourth clutch 19 work. The power is transmitted from the power input shaft 1 to the front planetary carrier 6 and the front middle row sun gear 8 through the first clutch 2 and the second clutch 4 at the same time, and then to the front middle row ring gear 9 through the front planetary gear 7, and then at the same time Pass the rear row ring gear 18 and the fourth clutch 19, the rear row sun gear 16 to the rear row planetary gear 17, and then output power through the rear row planet carrier 15 and the power output shaft 21. Calculated according to the kinematic relational formula, the transmission ratio i 5 of the 5th gear =1.
6挡：第一离合器2、第二制动器5、第四离合器19工作。动力从动力输入轴1由第一离合器2经前排行星架6输入，经前排行星齿轮7传给前中排齿圈9，再同时经后排齿圈18与第四离合器19、后排太阳轮16传给后排行星齿轮17，再经后排行星架15、动力输出轴21输出动力。根据运动关系式计算，6挡传动比i6＝α/(1+α)。6th gear: the first clutch 2, the second brake 5, and the fourth clutch 19 work. The power is input from the power input shaft 1 by the first clutch 2 through the front planetary carrier 6, then transmitted to the front middle row ring gear 9 through the front row planetary gear 7, and then simultaneously passes through the rear row ring gear 18 and the fourth clutch 19, the rear row The sun gear 16 is transmitted to the rear planetary gear 17, and then through the rear planetary carrier 15 and the power output shaft 21 output power. Calculated according to the kinematic relational formula, the transmission ratio i 6 of the 6th gear =α/(1+α).
倒挡[R挡]：第一制动器3、第二离合器4、第四离合器19工作。动力从动力输入轴1经第二离合器4由前中排太阳轮8输入，经前排行星齿轮7传给前中排齿圈9，再同时经后排齿圈18与第四离合器19、后排太阳轮16传给后排行星齿轮17，再经后排行星架15、动力输出轴21输出动力。根据运动关系式计算，倒挡传动比iR＝-α。Reverse gear [R gear]: the first brake 3, the second clutch 4, and the fourth clutch 19 work. The power is input from the power input shaft 1 through the second clutch 4, the sun gear 8 in the front middle row, the power is transmitted to the ring gear 9 in the front row through the planetary gear 7 in the front row, and then through the ring gear 18 in the rear row, the fourth clutch 19, and the rear row at the same time. Row sun gear 16 passes to rear row planetary gear 17, then through rear row planet carrier 15, power output shaft 21 output power. Calculated according to the kinematic relationship formula, the reverse transmission ratio i R =-α.
以上所述仅为本发明的较佳实施例，并不用以限制本发明，凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。The above descriptions are only preferred embodiments of the present invention, and are not intended to limit the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention shall be included in the protection of the present invention. within range.
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| JPH0235246A (en) * | 1988-07-25 | 1990-02-05 | Toyota Motor Corp | Planetary geared transmission for vehicle |
| KR0145492B1 (en) * | 1994-10-03 | 1998-08-01 | 와다 아키히로 | Gear transmission for automatic transmission |
| DE102013210493A1 (en) * | 2013-06-06 | 2014-12-24 | Zf Friedrichshafen Ag | Transmission for a motor vehicle |
| CN105546060B (en) * | 2016-01-19 | 2017-09-19 | 无锡商业职业技术学院 | A planetary gear type dual-clutch four-speed automatic transmission |
| CN205663839U (en) * | 2016-05-29 | 2016-10-26 | 无锡商业职业技术学院 | Single-stage and double-stage planetary gear combined six-gear automatic transmission |
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Application publication date: 20160907 Assignee: Hangzhou Juxian Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039927 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Jingchu Holdings (Group) Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039926 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Aiyue Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039925 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241221 Application publication date: 20160907 Assignee: Hangzhou Zuocheng Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039960 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Zhigu Information Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039954 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Zhengxiang Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039949 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Yuhan Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039939 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Yongting Pharmaceutical Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039937 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Shanwu Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039936 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 Application publication date: 20160907 Assignee: Hangzhou Lizao Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980039931 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241224 |
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Application publication date: 20160907 Assignee: Hangzhou Yuegu Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980041667 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241230 Application publication date: 20160907 Assignee: Hangzhou Hongxiao Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980041658 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241230 Application publication date: 20160907 Assignee: Hangzhou Buwei Technology Co.,Ltd. Assignor: Tongxiang Zhimeng Intellectual Property Operation Co.,Ltd. Contract record no.: X2024980041651 Denomination of invention: A single and dual stage planetary gear combination six speed automatic transmission Granted publication date: 20180417 License type: Common License Record date: 20241230 |