CN105546059B - A kind of double speed automatic transmissions of clutch five of planetary gear type - Google Patents
A kind of double speed automatic transmissions of clutch five of planetary gear type Download PDFInfo
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
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- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
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Abstract
本发明公开了一种行星齿轮式双离合五挡自动变速器，包括动力输入轴(1)和动力输出轴(25)；所述动力输入轴(1)的第一输出端通过第一离合器(2)分别与第二离合器(3)以及第三离合器(4)的输入端连接，所述第二离合器(3)的输出端与行星齿轮机构的前排齿圈(8)连接，所述第三离合器(4)的输出端与行星齿轮机构的前排太阳轮(6)连接。本发明的自动变速器采用行星齿轮结构，除具有双离合自动变速器的优点外，相对于平行轴式齿轮结构还具有结构紧凑、使用寿命长、运转更平稳、噪声低、技术成熟的特点。
The invention discloses a planetary gear type dual-clutch five-speed automatic transmission, which comprises a power input shaft (1) and a power output shaft (25); the first output end of the power input shaft (1) passes through the first clutch (2 ) are respectively connected with the input ends of the second clutch (3) and the third clutch (4), the output end of the second clutch (3) is connected with the front ring gear (8) of the planetary gear mechanism, and the third The output end of the clutch (4) is connected with the front sun gear (6) of the planetary gear mechanism. The automatic transmission of the present invention adopts a planetary gear structure. In addition to the advantages of a dual-clutch automatic transmission, it also has the characteristics of compact structure, long service life, more stable operation, low noise and mature technology compared with the parallel shaft gear structure.
Description
技术领域technical field
本发明涉及一种行星齿轮式双离合五挡自动变速器。The invention relates to a planetary gear type dual-clutch five-speed automatic transmission.
背景技术Background technique
自动变速器一般包括诸如行星齿轮单元的摩擦接合元件、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 generally includes frictional engagement elements such as planetary gear units, 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，运行不够平稳，噪声较大，使用寿命低。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 automatic transmission with this structure is not compact enough, the operation is not stable enough, the noise is large, and the service life is low.
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五挡行星齿轮自动变速器。The purpose of the present invention is to provide a five-speed planetary automatic transmission aimed 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：一种行星齿轮式双离合五挡自动变速器，包括动力输入轴1和动力输出轴25；In order to achieve the above object, the present invention adopts the following technical solutions: a planetary gear type dual-clutch five-speed automatic transmission, including a power input shaft 1 and a power output shaft 25;
所述动力输入轴1的第一输出端通过第一离合器2分别与第二离合器3以及第三离合器4的输入端连接，所述第二离合器3的输出端与行星齿轮机构的前排齿圈8连接，所述第三离合器4的输出端与行星齿轮机构的前排太阳轮6连接；The first output end of the power input shaft 1 is respectively connected to the input ends of the second clutch 3 and the third clutch 4 through the first clutch 2, and the output end of the second clutch 3 is connected to the front ring gear of the planetary gear mechanism. 8, the output end of the third clutch 4 is connected with the front row sun gear 6 of the planetary gear mechanism;
所述动力输入轴1的第二输出端通过第四离合器11分别与第五离合器12、第六离合器13以及第七离合器15的输入端连接，所述第五离合器12的输出端与行星齿轮机构的后排齿圈18连接，所述第六离合器13的输出端与行星齿轮机构的后排行星架19连接，所述第七离合器15的输出端与行星齿轮机构的后排太阳轮16连接；The second output end of the power input shaft 1 is respectively connected to the input ends of the fifth clutch 12, the sixth clutch 13 and the seventh clutch 15 through the fourth clutch 11, and the output end of the fifth clutch 12 is connected to the planetary gear mechanism The rear row ring gear 18 is connected, the output end of the sixth clutch 13 is connected with the rear row planet carrier 19 of the planetary gear mechanism, and the output end of the seventh clutch 15 is connected with the rear row sun gear 16 of the planetary gear mechanism;
其中，所述前排太阳轮6与前排齿圈8之间设置有带前排行星齿轮7的前排行星架9；Wherein, a front row planetary carrier 9 with a front row planetary gear 7 is arranged between the front row sun gear 6 and the front row ring gear 8;
所述后排太阳轮16与后排齿圈18之间设置有带后排行星齿轮17的所述后排行星架19；The rear planetary carrier 19 with the rear planetary gear 17 is arranged between the rear sun gear 16 and the rear ring gear 18;
所述动力输出轴25的第一输入端通过第八离合器22与所述后排行星架19的输出端连接，所述动力输出轴25的第二输入端通过第九离合器23与所述第五离合器12的输出端连接，所述动力输出轴25的第三输入端通过第十离合器24与所述前排行星架9的输出端连接；所述第二离合器3与前排齿圈8之间设置有对所述前排齿圈8制动的第一制动器5，所述第三离合器4与前排太阳轮6之间设置有对所述前排太阳轮6制动的第二制动器10，所述第五离合器12与后排齿圈18之间设置有对所述后排齿圈18制动的第三制动器14，所述第七离合器15与后排太阳轮16之间设置有对所述后排太阳轮16制动的第四制动器21，所述第八离合器22与后排行星架19之间设置有对所述后排行星架19制动的第五制动器20。The first input end of the power output shaft 25 is connected to the output end of the rear planet carrier 19 through the eighth clutch 22 , and the second input end of the power output shaft 25 is connected to the fifth input end through the ninth clutch 23 . The output end of the clutch 12 is connected, and the third input end of the power output shaft 25 is connected with the output end of the front row planet carrier 9 through the tenth clutch 24; between the second clutch 3 and the front row ring gear 8 A first brake 5 for braking the front ring gear 8 is provided, a second brake 10 for braking the front sun gear 6 is provided between the third clutch 4 and the front sun gear 6 , A third brake 14 for braking the rear ring gear 18 is provided between the fifth clutch 12 and the rear ring gear 18, and a brake for all the rear sun gears 16 is provided between the seventh clutch 15 and the rear sun gear 16. The fourth brake 21 for braking the rear sun gear 16 is provided, and the fifth brake 20 for braking the rear planet carrier 19 is arranged between the eighth clutch 22 and the rear planet carrier 19 .
本发明的有益效果：本发明的自动变速器采用行星齿轮结构，除具有双离合自动变速器的优点外，相对于平行轴式齿轮结构还具有结构紧湊、使用寿命长、运转更平稳、噪声低、技术成熟的特点。Beneficial effects of the present invention: the automatic transmission of the present invention adopts a planetary gear structure. In addition to the advantages of a dual-clutch automatic transmission, it also has the advantages of compact structure, long service life, more stable operation, low noise, The characteristics of mature technology.
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 description
图1所示，涉及一种行星齿轮式双离合五挡自动变速器，包括动力输入轴1和动力输出轴25；As shown in Fig. 1, it relates to a planetary gear type dual-clutch five-speed automatic transmission, including a power input shaft 1 and a power output shaft 25;
所述动力输入轴1的第一输出端通过第一离合器2分别与第二离合器3以及第三离合器4的输入端连接，所述第二离合器3的输出端与行星齿轮机构的前排齿圈8连接，所述第三离合器4的输出端与行星齿轮机构的前排太阳轮6连接；The first output end of the power input shaft 1 is respectively connected to the input ends of the second clutch 3 and the third clutch 4 through the first clutch 2, and the output end of the second clutch 3 is connected to the front ring gear of the planetary gear mechanism. 8, the output end of the third clutch 4 is connected with the front row sun gear 6 of the planetary gear mechanism;
所述动力输入轴1的第二输出端通过第四离合器11分别与第五离合器12、第六离合器13以及第七离合器15的输入端连接，所述第五离合器12的输出端与行星齿轮机构的后排齿圈18连接，所述第六离合器13的输出端与行星齿轮机构的后排行星架19连接，所述第七离合器15的输出端与行星齿轮机构的后排太阳轮16连接；The second output end of the power input shaft 1 is respectively connected to the input ends of the fifth clutch 12, the sixth clutch 13 and the seventh clutch 15 through the fourth clutch 11, and the output end of the fifth clutch 12 is connected to the planetary gear mechanism The rear row ring gear 18 is connected, the output end of the sixth clutch 13 is connected with the rear row planet carrier 19 of the planetary gear mechanism, and the output end of the seventh clutch 15 is connected with the rear row sun gear 16 of the planetary gear mechanism;
其中，所述前排太阳轮6与前排齿圈8之间设置有带前排行星齿轮7的前排行星架9；Wherein, a front row planetary carrier 9 with a front row planetary gear 7 is arranged between the front row sun gear 6 and the front row ring gear 8;
所述后排太阳轮16与后排齿圈18之间设置有带后排行星齿轮17的所述后排行星架19；The rear planetary carrier 19 with the rear planetary gear 17 is arranged between the rear sun gear 16 and the rear ring gear 18;
所述动力输出轴25的第一输入端通过第八离合器22与所述后排行星架19的输出端连接，所述动力输出轴25的第二输入端通过第九离合器23与所述第五离合器12的输出端连接，所述动力输出轴25的第三输入端通过第十离合器24与所述前排行星架9的输出端连接。The first input end of the power output shaft 25 is connected to the output end of the rear planet carrier 19 through the eighth clutch 22 , and the second input end of the power output shaft 25 is connected to the fifth input end through the ninth clutch 23 . The output end of the clutch 12 is connected, and the third input end of the power output shaft 25 is connected with the output end of the front planetary carrier 9 through the tenth clutch 24 .
进一步的，所述第二离合器3与前排齿圈8之间设置有对所述前排齿圈8制动的第一制动器5，所述第三离合器4与前排太阳轮6之间设置有对所述前排太阳轮6制动的第二制动器10，所述第五离合器12与后排齿圈18之间设置有对所述后排齿圈18制动的第三制动器14，所述第七离合器15与后排太阳轮16之间设置有对所述后排太阳轮16制动的第四制动器21，所述第八离合器22与后排行星架19之间设置有对所述后排行星架19制动的第五制动器20。Further, a first brake 5 for braking the front ring gear 8 is provided between the second clutch 3 and the front ring gear 8, and a first brake 5 is provided between the third clutch 4 and the front sun gear 6. There is a second brake 10 for braking the front sun gear 6, and a third brake 14 for braking the rear ring gear 18 is arranged between the fifth clutch 12 and the rear ring gear 18, so A fourth brake 21 for braking the rear sun gear 16 is provided between the seventh clutch 15 and the rear sun gear 16, and a fourth brake 21 for braking the rear sun gear 16 is provided between the eighth clutch 22 and the rear planet carrier 19. The fifth brake 20 for braking the rear planetary carrier 19 .
使用时，假设前排太阳轮齿数为Z1前，齿圈齿数为Z2前，则可令α前＝Z2前/Z1前；后排太阳轮齿数为Z1后，齿圈齿数为Z2后，则可令α后＝Z2后/Z1后；且α后＞α前。以下为各挡动力传递路线和传动比计算。When in use, assuming that the number of teeth of the front sun gear is Z 1 front , and the number of teeth of the ring gear is Z 2 front , then α front = Z 2 front /Z 1 front ; the number of teeth of the rear sun gear is Z 1 rear , and the number of teeth of the ring gear is After Z 2 , then α post =Z 2 post /Z 1 post ; and α post >α front . The following is the calculation of the power transmission route and transmission ratio of each gear.
1挡：第四离合器11、第三制动器14、第七离合器15、第八离合器22工作。动力从动力输入轴1经第四离合器11、第七离合器15由后排太阳轮16输入，经后排行星齿轮17、后排行星架19、第八离合器22、动力输出轴25输出动力。根据运动关系式计算，1挡传动比i1＝1+α后。1st gear: the fourth clutch 11, the third brake 14, the seventh clutch 15, and the eighth clutch 22 work. The power is input from the power input shaft 1 by the rear sun gear 16 through the fourth clutch 11 and the seventh clutch 15, and the power is output through the rear planetary gear 17, the rear planetary carrier 19, the eighth clutch 22, and the power output shaft 25. Calculated according to the kinematic relational formula, after the transmission ratio i 1 of the first gear = 1+α.
2挡：第一离合器2、第三离合器4、第一制动器5、第十离合器24工作。动力从动力输入轴1经第一离合器2、第三离合器4由前排太阳轮6输入，经前排行星齿轮7、前排行星架9、第十离合器24、动力输出轴25输出动力。根据运动关系式计算，2挡传动比i2＝1+α前。2nd gear: the first clutch 2, the third clutch 4, the first brake 5, and the tenth clutch 24 work. The power is input from the power input shaft 1 through the first clutch 2 and the third clutch 4 through the front sun gear 6, and the power is output through the front planetary gear 7, the front planetary carrier 9, the tenth clutch 24, and the power output shaft 25. Calculated according to the kinematic relational formula, the transmission ratio of the second gear i 2 =1+α front .
3挡：第四离合器11、第五离合器12、第四制动器21、第八离合器22工作。动力从动力输入轴1经第四离合器11、第五离合器12传给后排齿圈18，再经后排行星齿轮17、后排行星架19、第八离合器22、动力输出轴25输出动力。根据运动关系式计算，3挡传动比i3＝1+1/α后。3rd gear: the fourth clutch 11, the fifth clutch 12, the fourth brake 21, and the eighth clutch 22 work. The power is transmitted from the power input shaft 1 to the rear ring gear 18 through the fourth clutch 11 and the fifth clutch 12, and then through the rear planetary gear 17, the rear planet carrier 19, the eighth clutch 22, and the power output shaft 25 to output power. Calculated according to the kinematic relational formula, after the transmission ratio i 3 of the third gear = 1+1/α.
4挡：第一离合器2、第二离合器3、第三离合器4、第十离合器24工作。动力从动力输入轴1经第一离合器2，同时由第二离合器3传给前排齿圈8、由第三离合器4传给前排太阳轮6，再经前排行星齿轮7、前排行星架9、第十离合器24、动力输出轴25输出动力。根据运动关系式计算，4挡传动比i4＝1。4th gear: the first clutch 2, the second clutch 3, the third clutch 4, and the tenth clutch 24 work. The power is transmitted from the power input shaft 1 through the first clutch 2, and at the same time, the second clutch 3 is transmitted to the front ring gear 8, and the third clutch 4 is transmitted to the front sun gear 6, and then through the front planetary gear 7, the front planetary gear Frame 9, the tenth clutch 24, power output shaft 25 output power. Calculated according to the kinematic relational formula, the transmission ratio i 4 of the fourth gear =1.
5挡：第四离合器11、第六离合器13、第四制动器21、第九离合器23工作。动力从动力输入轴1经第四离合器11、第六离合器13传给后排行星架19，经后排行星齿轮17、后排齿圈18、第九离合器23、动力输出轴25输出动力。根据运动关系式计算，5挡传动比i5＝α后/(1+α后)。5th gear: the fourth clutch 11, the sixth clutch 13, the fourth brake 21, and the ninth clutch 23 work. The power is transmitted from the power input shaft 1 to the rear planet carrier 19 through the fourth clutch 11 and the sixth clutch 13, and the power is output through the rear planetary gear 17, the rear ring gear 18, the ninth clutch 23 and the power output shaft 25. Calculated according to the kinematic relational formula, the transmission ratio i 5 of the 5th gear = α rear /(1+α rear ).
倒挡[R挡]：第四离合器11、第七离合器15、第五制动器20、第九离合器23工作。动力从动力输入轴1经第四离合器11、第七离合器15传给后排太阳轮16，经后排行星齿轮17、后排齿圈18、第九离合器23、动力输出轴25输出动力。根据运动关系式计算，倒挡传动比iR＝-α后。Reverse gear [R gear]: the fourth clutch 11, the seventh clutch 15, the fifth brake 20, and the ninth clutch 23 work. The power is transmitted from the power input shaft 1 to the rear sun gear 16 through the fourth clutch 11 and the seventh clutch 15, and the power is output through the rear planetary gear 17, the rear ring gear 18, the ninth clutch 23 and the power output shaft 25. Calculated according to the kinematic relationship formula, after 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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| CN104896040A (en) * | 2015-05-14 | 2015-09-09 | 南宁学院 | Multi-gear line control planetary gear automatic transmission |
| CN105114559A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Automatic nine-speed transmission |
| CN205298431U (en) * | 2016-01-19 | 2016-06-08 | 无锡商业职业技术学院 | Planetary gear type double-clutch five-gear automatic transmission |
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| CN105546059A (en) | 2016-05-04 |
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