CN105065589A - Eight-gear transmission - Google Patents
Eight-gear transmission Download PDFInfo
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- 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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- 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)
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Abstract
本发明提供了一种八挡变速器，主要包括输入轴、输出轴、行星齿轮排、联接构件和扭矩传递装置，这些构件均设在变速器壳体内，每一个行星齿轮排均包括太阳轮、齿圈、行星架和其支撑的行星轮，所述的扭矩传递装置包括两个离合器和四个制动器，二个离合器和四个制动器选择性地接合，使得太阳轮、行星架、齿圈和五个联接构件中的某一个旋转或是固定，并且其中扭矩传递装置能够以至少两个的组合形式选择性的接合以便能在所述的输入轴和输出轴之间建立起八个前进挡速比和一个倒挡速比，前进挡为五个减速挡、一个直接挡和两个超速挡；该变速器结构紧凑、重量较轻、体积小，在汽车上易布置，变速器的各挡位的传动比之间的速比阶跃符合变速器的要求。
The invention provides an eight-speed transmission, which mainly includes an input shaft, an output shaft, a planetary gear row, a coupling member and a torque transmission device. , the planetary carrier and the planetary gear supported by it, the torque transmission device includes two clutches and four brakes, the two clutches and the four brakes are selectively engaged, so that the sun gear, the planetary carrier, the ring gear and the five couplings One of the members rotates or is fixed, and wherein the torque transmitting devices are selectively engageable in combinations of at least two to establish eight forward speed ratios and one The reverse gear ratio, the forward gear is five deceleration gears, one direct gear and two overdrive gears; the transmission is compact in structure, light in weight, small in size, easy to arrange on the car, and the transmission ratio of each gear of the transmission The speed ratio step meets the requirements of the transmission.
Description
技术领域technical field
本发明涉及一种八挡变速器，属于车辆传动技术领域。The invention relates to an eight-speed transmission, which belongs to the technical field of vehicle transmission.
背景技术Background technique
典型的多速变速器使用摩擦离合器、行星齿轮装置和固定互连件的组合来实现多个传动比。行星齿轮组的数量和物理设置通常由封装、成本和期望速度比规定。虽然当前的变速器实现了其预期目的，但是随着汽车的普及，人们对新式和改进变速器配置的需要实质上是持续不断的。A typical multi-speed transmission uses a combination of friction clutches, planetary gearing, and fixed interconnections to achieve multiple gear ratios. The number and physical arrangement of planetary gear sets is usually dictated by packaging, cost and desired speed ratios. While current transmissions have served their intended purpose, the need for new and improved transmission configurations is virtually constant as automobiles proliferate.
所述变速器配置的改进主要从以下两方面着手，一是性能，具体包括传动比的范围、响应性和平滑性的角度；二是封装，主要是减少的尺寸和重量，当挡位确定时，实现固定挡位所需的构件的数量相应确定，因此对变速器的改进主要是提高变速器的性能，在变速器组成构件基本维持不变的情况下，如何通过改进各组件间的连接关系，以增加变速器可实现的挡位数和传动比参数，成为变速器改进的难点和核心。中国发明申请“八挡变速器”(申请号：CN201410829472)和中国发明申请“CN201410826601-一种变速范围更广的变速器”(申请号：CN201110094929)均公开了一种由四个行星轮系、六个扭矩传递装置和四个连接构件构成的八挡变速器，上述两个变速器均实现八个前进挡速比和一个倒挡速比，但存在速比较小、传动平稳性较低的问题。The improvement of the transmission configuration mainly starts from the following two aspects. One is performance, specifically including the range of transmission ratio, responsiveness and smoothness; the other is packaging, mainly reducing size and weight. When the gear is determined, The number of components required to achieve a fixed gear is determined accordingly. Therefore, the improvement of the transmission is mainly to improve the performance of the transmission. Under the condition that the components of the transmission remain basically unchanged, how to improve the connection relationship between the components to increase the transmission capacity. The achievable number of gears and transmission ratio parameters become the difficulty and core of transmission improvement. The Chinese invention application "eight-speed transmission" (application number: CN201410829472) and the Chinese invention application "CN201410826601-a transmission with a wider range of speed change" (application number: CN201110094929) both disclose a four-planetary gear train, six An eight-speed transmission composed of a torque transmission device and four connecting members. The above two transmissions both realize eight forward gear ratios and one reverse gear ratio, but there are problems of small speed ratios and low transmission stability.
发明内容Contents of the invention
本发明的目的在于提供一种能够减小减速器的体积，减低控制的难度和扩大变速器的速比范围的八挡变速器。The object of the present invention is to provide an eight-speed transmission capable of reducing the volume of the speed reducer, reducing the difficulty of control and expanding the speed ratio range of the transmission.
实现本发明目的所采用的技术方案为，一种八挡变速器，包括变速器外壳以及安装于变速器外壳内部的输入轴、输出轴、行星齿轮排组、联接构件组和扭矩传递装置，所述行星齿轮排组包括从前往后依次安装的第一行星齿轮排、第二行星齿轮排、第三行星齿轮排和第四行星齿轮排，各行星齿轮排均由太阳轮、行星架、行星轮和齿圈构成，所述扭矩传递装置包括第一离合器、第二离合器、第一制动器、第二制动器、第三制动器和第四制动器，各制动器均与变速器外壳的壳体固连，所述联接构件组包括第一联接构件、第二联接构件、第三联接构件、第四联接构件和第五联接构件，其中第一联接构件连接第一行星齿轮排的齿圈与第二行星齿轮排的齿圈；第二联接构件连接第一行星齿轮排的行星架与第二行星齿轮排的行星架，第三联接构件连接第三行星齿轮排的齿圈与第四行星齿轮排的行星架，第四联接构件连接第三行星齿轮排的行星架与第四行星齿轮排的齿圈，第五联接构件连接第二行星齿轮排的行星架与第三行星齿轮排的太阳轮；The technical solution adopted to realize the object of the present invention is an eight-speed transmission, including a transmission housing and an input shaft, an output shaft, a planetary gear row set, a coupling member group and a torque transmission device installed inside the transmission housing. The row group includes the first planetary gear row, the second planetary gear row, the third planetary gear row and the fourth planetary gear row installed in sequence from front to back, and each planetary gear row consists of a sun gear, a planet carrier, a planetary gear and a ring gear The torque transmission device includes a first clutch, a second clutch, a first brake, a second brake, a third brake and a fourth brake, each brake is fixedly connected to the casing of the transmission casing, and the coupling member group includes a first coupling member, a second coupling member, a third coupling member, a fourth coupling member and a fifth coupling member, wherein the first coupling member connects the ring gear of the first planetary gear row with the ring gear of the second planetary gear row; The second connecting member connects the planet carrier of the first planetary gear row with the planet carrier of the second planetary gear row, the third connecting member connects the ring gear of the third planetary gear row with the planet carrier of the fourth planetary gear row, and the fourth connecting member connects the planetary carrier of the third planetary gear row and the ring gear of the fourth planetary gear row, and the fifth coupling member connects the planetary carrier of the second planetary gear row and the sun gear of the third planetary gear row;
所述第一制动器连接第一行星齿轮排的太阳轮，第二制动器连接第二行星齿轮排的行星架，第三制动器连接第一联接构件，第四制动器连接第三行星齿轮排的行星架；The first brake is connected to the sun gear of the first planetary gear row, the second brake is connected to the planet carrier of the second planetary gear row, the third brake is connected to the first coupling member, and the fourth brake is connected to the planet carrier of the third planetary gear row;
所述输入轴与第二行星齿轮排的太阳轮固连，输出轴与第四行星齿轮排的行星架连接，输入轴通过第一离合器与第四行星齿轮排的太阳轮连接，并且通过第二离合器与第四联接构件连接。The input shaft is fixedly connected to the sun gear of the second planetary gear row, the output shaft is connected to the planet carrier of the fourth planetary gear row, the input shaft is connected to the sun gear of the fourth planetary gear row through the first clutch, and is connected to the sun gear of the fourth planetary gear row through the second clutch. A clutch is connected with the fourth coupling member.
由上述技术方案可知，本发明提供的八挡变速器，通过四个行星齿轮排和六个扭矩传递装置实现变速器八个前进挡速比和一个倒挡速比，每一个挡位的速比的形成通过接合两个扭矩传递装置而获得；其中第一离合器可选择性地接合以连接输入轴与第四行星齿轮排的太阳轮一起旋转；第二离合器可选择性地接合以连接输入轴与第四联接构件一起旋转；第一制动器可选择性地接合以连接第一行星齿轮排的太阳轮与变速器外壳，目的是为了阻止第一行星齿轮排的太阳轮相对于变速器外壳的旋转；第二制动器可选择性地接合以连接第二行星齿轮排的行星架与变速器外壳，第二行星齿轮排的行星架与第二联接构件连接，目的是为了阻止第二联接构件相对于变速器外壳的旋转；第三制动器可选择性地接合以连接第一联接构件与变速器外壳，目的是为了阻止第一联接构件相对于变速器外壳的旋转；第四制动器可选择性地接合以连接第三行星齿轮排的行星架与变速器外壳，第三行星齿轮排的行星架与第四联接构件连接，目的是为了阻止第四联接构件相对于变速器外壳的旋转。It can be seen from the above technical solution that the eight-speed transmission provided by the present invention realizes eight forward speed ratios and one reverse speed ratio of the transmission through four planetary gear rows and six torque transmission devices, and the formation of the speed ratio of each gear is obtained by engaging two torque transmitting devices; where the first clutch is selectively engageable to connect the input shaft with the sun gear of the fourth planetary gear row; the second clutch is selectively engageable to connect the input shaft to the fourth The coupling members rotate together; the first brake is selectively engageable to connect the sun gear of the first planetary gear row with the transmission housing for the purpose of preventing the sun gear of the first planetary gear row from rotating relative to the transmission housing; the second brake can selectively engageable to connect the planet carrier of the second planetary gear row with the transmission housing, the planet carrier of the second planet gear row connected with the second coupling member for the purpose of preventing rotation of the second coupling member relative to the transmission housing; third a brake is selectively engageable to connect the first coupling member with the transmission housing for the purpose of preventing rotation of the first coupling member relative to the transmission housing; a fourth brake is selectively engageable to connect the carrier of the third planetary gear row with the In the transmission housing, the planet carrier of the third planetary gear row is connected to the fourth coupling member for preventing the rotation of the fourth coupling member relative to the transmission housing.
二个离合器和四个制动器选择性地接合，使得运动构件(太阳轮、行星架、齿圈或五个联接构件中的某一个)旋转或是固定，并且其中扭矩传递装置能够以至少两个的组合形式选择性的接合以便能在所述的输入轴和输出轴之间建立起八个前进挡速比和一个倒挡速比，八个前进挡包括五个减速挡、一个直接挡和两个超速挡，具体为：Two clutches and four brakes are selectively engaged so that the moving member (sun gear, planet carrier, ring gear, or one of the five coupling members) rotates or is fixed, and wherein the torque transmitting device can operate with at least two The combined form is selectively engaged so that eight forward speed ratios and one reverse speed ratio can be established between the input shaft and the output shaft. The eight forward speed ratios include five reduction gears, one direct gear and two Overdrive, specifically:
1)第二制动器和第四制动器接合，实现倒挡的建立，倒挡的传动比为-9；1) The second brake and the fourth brake are engaged to realize the establishment of the reverse gear, and the transmission ratio of the reverse gear is -9;
2)第一离合器和第一制动器接合，实现一挡(减速挡)的建立，一挡的传动比为7.15；2) The first clutch and the first brake are engaged to realize the establishment of the first gear (reduction gear), and the transmission ratio of the first gear is 7.15;
3)第一离合器和第四制动器接合，实现二挡(减速挡)的建立，二挡的传动比为3.9，速比阶跃为1.83；3) The first clutch and the fourth brake are engaged to realize the establishment of the second gear (reduction gear). The transmission ratio of the second gear is 3.9, and the speed ratio step is 1.83;
4)第一制动器和第四制动器接合，实现三挡(减速挡)的建立，三挡的传动比为2.67，速比阶跃为1.46。4) The first brake and the fourth brake are engaged to realize the establishment of the third gear (reduction gear). The transmission ratio of the third gear is 2.67, and the speed ratio step is 1.46.
5)第一离合器和第二制动器接合，实现四挡(减速挡)的建立，四挡的传动比为1.97，速比阶跃为1.36；5) The first clutch and the second brake are engaged to realize the establishment of the fourth gear (reduction gear), the transmission ratio of the fourth gear is 1.97, and the speed ratio step is 1.36;
6)第一离合器和第三制动器接合，实现五挡(减速挡)的建立，五挡的传动比为1.62，速比阶跃为1.22；6) The first clutch and the third brake are engaged to realize the establishment of the fifth gear (reduction gear), the transmission ratio of the fifth gear is 1.62, and the speed ratio step is 1.22;
7)第一离合器和第二离合器接合，实现六挡(直接挡)的建立，六挡的传动比为1，速比阶跃为1.62；7) The first clutch and the second clutch are engaged to realize the establishment of the sixth gear (direct gear), the transmission ratio of the sixth gear is 1, and the speed ratio step is 1.62;
8)第二离合器和第三制动器接合，实现七挡(超速挡)的建立，七挡的传动比为0.72，速比阶跃为1.39；8) The second clutch and the third brake are engaged to realize the establishment of the seventh gear (overdrive gear), the transmission ratio of the seventh gear is 0.72, and the speed ratio step is 1.39;
9)第二离合器和第二制动器接合，实现八挡(超速挡)的建立，八挡的传动比为0.67，速比阶跃为1.07。9) The second clutch and the second brake are engaged to realize the establishment of the eighth gear (overdrive gear). The transmission ratio of the eighth gear is 0.67, and the speed ratio step is 1.07.
与现有技术相比，本发明的有益效果为：Compared with prior art, the beneficial effect of the present invention is:
1、本发明提供的八挡变速器采用行星传动，齿轮集中在中间，而且其动力可以通过几个行星轮来传动，齿轮的模数小，结构紧凑，重量较轻，在汽车上易布置；1. The eight-speed transmission provided by the present invention adopts planetary transmission, the gears are concentrated in the middle, and its power can be transmitted through several planetary gears. The gears have a small modulus, compact structure, light weight, and are easy to arrange on automobiles;
2、减少了扭矩传递构件的个数，八挡变速器仅仅采用了六个扭矩传递构件，在很大程度上减小变速器的体积；2. The number of torque transmission components is reduced, and the eight-speed transmission only uses six torque transmission components, which greatly reduces the volume of the transmission;
3、各个挡位的控制只需要两个结合构件(离合器或制动器)，控制简单；3. The control of each gear only needs two coupling components (clutch or brake), so the control is simple;
4、该变速器利用联接构件将不同齿轮组的构件连接在一起，可形成新的变速器机构，联接构件的数量和位置的不同将导致形成的变速器机构本质上的不同。该变速器利用五个联接构件，联接方式经验证可行，且通过优选得到的特性参数使得各挡位总的变速范围可达10.6，比经典的ZF8速变速器的变速范围7.37和雷克萨斯LS460变速器的变速范围6.71更广；4. The transmission utilizes coupling components to connect the components of different gear sets together to form a new transmission mechanism, and the difference in the number and position of the coupling components will result in a substantial difference in the formed transmission mechanism. The transmission utilizes five coupling components, and the coupling method has been verified to be feasible, and the characteristic parameters obtained through optimization make the total transmission range of each gear up to 10.6, compared with the transmission range of the classic ZF 8-speed transmission of 7.37 and the transmission range of Lexus LS460 6.71 wider;
5、经过优选，两个超速挡的速比阶跃均较小，分别为1.39和1.07，能够平稳传动，提高汽车的动力性能。5. After optimization, the speed ratio steps of the two overdrive gears are small, 1.39 and 1.07 respectively, which can drive smoothly and improve the power performance of the car.
附图说明Description of drawings
图1为本发明提供的八挡变速器的结构简图。Fig. 1 is a schematic structural diagram of an eight-speed transmission provided by the present invention.
其中，1-输入轴，2-输出轴，3-变速器外壳，4-第五联接构件，5-第一联接构件，6-第二联接构件，7-第三联接构件，8-第四联接构件，2-第一行星齿轮排齿圈，12-第一行星齿轮排行星轮，13-第一行星齿轮排行星架，14-第一行星齿轮排太阳轮，21-第二行星齿轮排齿圈，22-第二行星齿轮排行星轮，23-第二行星齿轮排行星架，24-第二行星齿轮排太阳轮，31-第三行星齿轮排齿圈，32-第三行星齿轮排行星轮，33-第三行星齿轮排行星架，34-第三行星齿轮排太阳轮，41-第四行星齿轮排齿圈，42-第四行星齿轮排行星轮，43-第四行星齿轮排行星架，44-第四行星齿轮排太阳轮，C1-第一离合器，C2-第二离合器，B1-第一制动器，B2-第二制动器，B3-第三制动器，B4-第四制动器。Among them, 1-input shaft, 2-output shaft, 3-transmission housing, 4-fifth coupling member, 5-first coupling member, 6-second coupling member, 7-third coupling member, 8-fourth coupling Components, 2-the first planetary gear ring gear, 12-the first planetary gear planetary gear, 13-the first planetary gear planet carrier, 14-the first planetary gear sun gear, 21-the second planetary gear tooth Circle, 22-the second planetary gear row planetary gear, 23-the second planetary gear row planet carrier, 24-the second planetary gear row sun gear, 31-the third planetary gear row ring gear, 32-the third planetary gear row planet Wheel, 33-the third planetary gear row planet carrier, 34-the third planetary gear row sun gear, 41-the fourth planetary gear row ring gear, 42-the fourth planetary gear row planet gear, 43-the fourth planetary gear row planet frame, 44-the fourth planetary gear row sun gear, C1-the first clutch, C2-the second clutch, B1-the first brake, B2-the second brake, B3-the third brake, B4-the fourth brake.
具体实施方式Detailed ways
下面结合附图和实施例对本发明进行详细具体说明，本发明的内容不局限于以下实施例。The present invention will be described in detail below in conjunction with the accompanying drawings and embodiments, and the content of the present invention is not limited to the following embodiments.
本发明提供的八挡变速器，其结构如图1所示，包括变速器外壳3以及安装于变速器外壳内部的输入轴1、输出轴2、行星齿轮排组、联接构件组和扭矩传递装置，所述行星齿轮排组包括从前往后依次安装的第一行星齿轮排、第二行星齿轮排、第三行星齿轮排和第四行星齿轮排，各行星齿轮排均由太阳轮(14、24、34和44)、行星架(13、23、33和43)、行星轮(13、23、33和43)和齿圈(12、22、32和42)构成，其中行星齿轮排中的行星轮与太阳轮和齿圈均通过齿轮副互相啮合，所述扭矩传递装置包括第一离合器C1、第二离合器C2、第一制动器B1、第二制动器B2、第三制动器B3和第四制动器B4，各制动器均与变速器外壳的壳体3固连；The eight-speed transmission provided by the present invention has a structure as shown in Figure 1, including a transmission housing 3 and an input shaft 1, an output shaft 2, a planetary gear set, a coupling member group and a torque transmission device installed inside the transmission housing. The planetary gear row set includes the first planetary gear row, the second planetary gear row, the third planetary gear row and the fourth planetary gear row installed in sequence from front to back, and each planetary gear row is composed of sun gears (14, 24, 34 and 44), planet carrier (13, 23, 33 and 43), planetary gear (13, 23, 33 and 43) and ring gear (12, 22, 32 and 42), wherein the planetary gear in the planetary gear row and the sun Both the wheel and the ring gear are meshed with each other through a gear pair, and the torque transmission device includes a first clutch C1, a second clutch C2, a first brake B1, a second brake B2, a third brake B3 and a fourth brake B4, and each brake is It is fixedly connected with the casing 3 of the transmission casing;
所述联接构件组包括第一联接构件5、第二联接构件6、第三联接构件7、第四联接构件8和第五联接构件4，其中第一联接构件5将第一行星齿轮排齿圈2与第二行星齿轮排齿圈21互连，第二联接构件6将第一行星齿轮排行星架13与第二行星齿轮排行星架23互联，第三联接构件7将第三行星齿轮排齿圈31和第四行星齿轮排行星架43互连，第四联接构件8将第三行星齿轮排行星架33与第四行星齿轮排齿圈41互连，第五联接构件4将第二行星齿轮排行星架23与第三行星齿轮排太阳轮34互连；The set of coupling components includes a first coupling component 5, a second coupling component 6, a third coupling component 7, a fourth coupling component 8 and a fifth coupling component 4, wherein the first coupling component 5 connects the first planetary gear ring gear 2 is interconnected with the second planetary gear ring gear 21, the second coupling member 6 interconnects the first planetary gear carrier 13 with the second planetary gear carrier 23, and the third coupling member 7 connects the third planetary gear The ring 31 and the fourth planetary gear carrier 43 are interconnected, the fourth coupling member 8 interconnects the third planetary gear carrier 33 with the fourth planetary gear ring gear 41, and the fifth coupling member 4 interconnects the second planetary gear The row planet carrier 23 is interconnected with the third planetary gear row sun gear 34;
所述扭矩传递装置包括第一离合器C1、第二离合器C2、第一制动器B1、第二制动器B2、第三制动器B3和第四制动器B4，其中第一离合器C1将输入轴1和第四行星齿轮排太阳轮44互连；第二离合器C2将输入轴和第四联接构件互连；第一制动器B1将第一行星齿轮排太阳轮14和变速器外壳3互连；第二制动器B2将第二联接构件与变速器外壳互连；第三制动器B3将第一联接构件和变速器外壳互连；第四制动器B4将第三行星齿轮排行星架33与变速器外壳3互连；The torque transmission device includes a first clutch C1, a second clutch C2, a first brake B1, a second brake B2, a third brake B3 and a fourth brake B4, wherein the first clutch C1 connects the input shaft 1 and the fourth planetary gear The second clutch C2 interconnects the input shaft and the fourth coupling member; the first brake B1 interconnects the first planetary gear row sun gear 14 and the transmission housing 3; the second brake B2 interconnects the second The components are interconnected with the transmission housing; the third brake B3 interconnects the first coupling member and the transmission housing; the fourth brake B4 interconnects the third planetary gear carrier 33 with the transmission housing 3;
所述输入轴1的输出端始终与第二行星齿轮排太阳轮24连接，输入轴1的输入端始终被连接至发动机或者变矩器的涡轮，输出轴2的输入端始终与第四行星齿轮排行星架43连接，输出轴2的输出端被连接至下一级减速器。The output end of the input shaft 1 is always connected with the second planetary gear row sun gear 24, the input end of the input shaft 1 is always connected to the turbine of the engine or torque converter, and the input end of the output shaft 2 is always connected with the fourth planetary gear The row planet carrier 43 is connected, and the output end of the output shaft 2 is connected to the next stage reducer.
下面对本发明提供的八挡变速器的变挡原理进行介绍，该变速器能实现八个前进挡速比和一个倒挡速比，每一个挡位的速比的形成通过接合两个扭矩传递装置而获得，下面详细介绍各个挡位的工作过程：The shifting principle of the eight-speed transmission provided by the present invention is introduced below. This transmission can realize eight forward gear ratios and one reverse gear ratio. The speed ratio of each gear is formed by engaging two torque transmission devices. , the working process of each gear is introduced in detail below:
倒挡的建立，第二制动器B3和第四制动器B4接合。具体来说，第三制动器B3被接合以使得第一联接构件5与变速器外壳3相连，阻止了第一联接构件相对于变速器外壳3的旋转。第四制动器B4被接合以使得第四联接构件8与变速器外壳3相连，阻止了第四联接构件8相对于变速器外壳3的旋转。由此，在输入轴1和输出轴2之间建立起倒挡的传动比。The reverse gear is established, the second brake B3 and the fourth brake B4 are engaged. Specifically, the third brake B3 is engaged such that the first coupling member 5 is connected to the transmission housing 3 , preventing rotation of the first coupling member relative to the transmission housing 3 . The fourth brake B4 is engaged to connect the fourth coupling member 8 with the transmission housing 3 , preventing rotation of the fourth coupling member 8 relative to the transmission housing 3 . As a result, a reverse gear ratio is established between the input shaft 1 and the output shaft 2 .
一挡(减速挡)的建立，第一离合器C1和第一制动器B1被接合。具体来说，第一离合器C1被接合以连接太阳轮24和太阳轮44一起旋转。第一制动器B1被接合以使得太阳轮14和变速器外壳3相连，阻止了太阳轮14相对于变速器外壳3的旋转。由此，在输入轴1和输出轴2之间建立起了一挡的传动比。When the first gear (reduction gear) is established, the first clutch C1 and the first brake B1 are engaged. Specifically, the first clutch C1 is engaged to connect the sun gear 24 to rotate with the sun gear 44 . The first brake B1 is engaged to connect the sun gear 14 to the transmission housing 3 , preventing the sun gear 14 from rotating relative to the transmission housing 3 . As a result, a gear ratio of first gear is established between the input shaft 1 and the output shaft 2 .
二挡(减速挡)的建立，第一离合器C1和第四制动器B4被接合。具体来说，第一离合器C1被接合以连接太阳轮24和太阳轮44一起旋转。第四制动器B4被接合以使得第四联接构件8和变速器外壳3相连，阻止了第四联接构件8相对于变速器外壳3的旋转。这样形成了单行星齿轮排的传动，由此在输入轴1和输出轴2之间建立起了二挡的传动比。When the second gear (reduction gear) is established, the first clutch C1 and the fourth brake B4 are engaged. Specifically, the first clutch C1 is engaged to connect the sun gear 24 to rotate with the sun gear 44 . The fourth brake B4 is engaged to connect the fourth coupling member 8 and the transmission housing 3 , preventing rotation of the fourth coupling member 8 relative to the transmission housing 3 . This results in a transmission of a single planetary gear row, whereby a transmission ratio of second gear is established between the input shaft 1 and the output shaft 2 .
三挡(减速挡)的建立，第一制动器B1和第四制动器B4被接合。具体来说，第一制动器B1被接合以使得太阳轮14和变速器外壳3相连，阻止了太阳轮14相对于变速器外壳3的旋转。第四制动器B4被接合以使得第四联接构件8与变速器外壳3相连，阻止了第四联接构件8相对于变速器外壳3的旋转。由此，在输入轴1和输出轴2之间建立起了三挡的传动比。The third gear (reduction gear) is established, the first brake B1 and the fourth brake B4 are engaged. Specifically, the first brake B1 is engaged to connect the sun gear 14 to the transmission housing 3 , preventing the sun gear 14 from rotating relative to the transmission housing 3 . The fourth brake B4 is engaged to connect the fourth coupling member 8 with the transmission housing 3 , preventing rotation of the fourth coupling member 8 relative to the transmission housing 3 . Thus, a transmission ratio of third gear is established between the input shaft 1 and the output shaft 2 .
四挡(减速挡)的建立，第一离合器C1和第二制动器B2被接合。具体来说，第一离合器C1被接合以连接太阳轮24和太阳轮44一起旋转。第二制动器B2被接合以使得第二联接构件6和变速器外壳3相连，阻止了第二联接构件6相对于变速器外壳3的旋转。由此，在输入轴1和输出轴2之间建立起了四挡的传动比。When the fourth gear (reduction gear) is established, the first clutch C1 and the second brake B2 are engaged. Specifically, the first clutch C1 is engaged to connect the sun gear 24 to rotate with the sun gear 44 . The second brake B2 is engaged to connect the second coupling member 6 to the transmission housing 3 , preventing rotation of the second coupling member 6 relative to the transmission housing 3 . As a result, a fourth gear ratio is established between the input shaft 1 and the output shaft 2 .
五挡(减速挡)的建立，第一离合器C1和第三制动器B3被接合。具体来说，第一离合器C1被接合以连接太阳轮24和太阳轮44一起旋转。第三制动器B3被接合以使得第一联接构件5和变速器外壳3相连，阻止了第一联接构件5相对于变速器外壳3的旋转。由此，在输入轴1和输出轴2之间建立起了五挡的传动比。The fifth gear (reduction gear) is established, and the first clutch C1 and the third brake B3 are engaged. Specifically, the first clutch C1 is engaged to connect the sun gear 24 to rotate with the sun gear 44 . The third brake B3 is engaged to connect the first coupling member 5 and the transmission housing 3 , preventing rotation of the first coupling member 5 relative to the transmission housing 3 . Thus, a transmission ratio of fifth gear is established between the input shaft 1 and the output shaft 2 .
六挡(直接挡)的建立，第一离合器C1和第二离合器C2被接合。具体来说，第一离合器C1被接合以连接太阳轮24和太阳轮44一起旋转。第二离合器C2被接合以连接太阳轮24和第四联接构件8一起旋转。由此，在输入轴1和输出轴2之间建立起了六挡的传动比。The sixth gear (direct gear) is established, and the first clutch C1 and the second clutch C2 are engaged. Specifically, the first clutch C1 is engaged to connect the sun gear 24 to rotate with the sun gear 44 . The second clutch C2 is engaged to connect the sun gear 24 to rotate with the fourth coupling member 8 . A sixth gear ratio is thus established between the input shaft 1 and the output shaft 2 .
七挡(超速挡)的建立，第二离合器C2和第三制动器B3被接合。具体来说，第二离合器C2被接合以连接太阳轮24和第四联接构件8一起旋转。第三制动器B3被接合以使得第一联接构件5和变速器外壳3相连，阻止了第一联接构件5相对于变速器外壳3的旋转。由此，在输入轴1和输出轴2之间建立起七挡的传动比。Seventh gear (overdrive) is established, the second clutch C2 and the third brake B3 are engaged. Specifically, the second clutch C2 is engaged to connect the sun gear 24 to rotate with the fourth coupling member 8 . The third brake B3 is engaged to connect the first coupling member 5 and the transmission housing 3 , preventing rotation of the first coupling member 5 relative to the transmission housing 3 . Thus, a transmission ratio of seven gears is established between the input shaft 1 and the output shaft 2 .
八挡(超速挡)的建立，第二离合器C2和第二制动器B2被接合。具体来说，第二离合器C2被接合以连接太阳轮24和第四联接构件8一起旋转。第二制动器B2被接合以使得第二联接构件6和变速器外壳3相连，阻止了第二联接构件6相对于变速器外壳3的旋转。由此，在输入轴1和输出轴2之间建立起八挡的传动比。Eighth gear (overdrive) is established, the second clutch C2 and the second brake B2 are engaged. Specifically, the second clutch C2 is engaged to connect the sun gear 24 to rotate with the fourth coupling member 8 . The second brake B2 is engaged to connect the second coupling member 6 to the transmission housing 3 , preventing rotation of the second coupling member 6 relative to the transmission housing 3 . Thus, an eighth gear ratio is established between the input shaft 1 and the output shaft 2 .
各个挡位的传动比、速比阶跃和各个挡位扭矩传递装置接合状态如下表所示：The gear ratios, ratio steps, and torque transfer device engagement states for each gear are shown in the table below:
表中：X表示接合并且传递扭矩，O表示接合但不传递扭矩。In the table: X means engaging and transmitting torque, O means engaging but not transmitting torque.
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