CN104033550B - Multi-shifting speed variator - Google Patents
Multi-shifting speed variator Download PDFInfo
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- CN104033550B CN104033550B CN201410256012.0A CN201410256012A CN104033550B CN 104033550 B CN104033550 B CN 104033550B CN 201410256012 A CN201410256012 A CN 201410256012A CN 104033550 B CN104033550 B CN 104033550B
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- 230000005540 biological transmission Effects 0.000 claims abstract description 25
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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
- 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
- F16H2200/0069—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising ten 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)
- Transmission Devices (AREA)
- Structure Of Transmissions (AREA)
Abstract
本发明涉及一种十挡变速器，该变速器包括输入构件，输出构件，四个行星齿轮排，三个离合器、三个制动器和四个连接构件。各个行星齿轮排包括太阳轮，行星架和齿圈。使用该变速器的行星排连接形式和结合元件布置方式可实现10个前进挡和1个倒挡，总传动比为8.84，四个行星排的K值均在1.80-2.72范围内，且每个行星排均为单行星轮行星排。
The invention relates to a ten-speed transmission, which includes an input member, an output member, four planetary gear rows, three clutches, three brakes and four connecting members. Each planetary gear row includes the sun gear, planet carrier and ring gear. Using the connection form of the planetary rows and the arrangement of the combined elements of the transmission can realize 10 forward gears and 1 reverse gear, the total transmission ratio is 8.84, the K values of the four planetary rows are all in the range of 1.80-2.72, and each planetary The rows are single planetary planetary rows.
Description
技术领域technical field
本发明属于车辆（汽车、特种车辆、工程机械）传动技术领域，具体涉及一种十挡变速器。The invention belongs to the technical field of vehicle (automotive, special vehicle, construction machinery) transmission, and specifically relates to a ten-speed transmission.
背景技术Background technique
为改善车辆的性能（动力性能、燃料经济性、换挡性能），轿车挡位数正向六挡以上发展，自卸车也要求六挡以上，为此要寻找挡位更多，同时行星排与结合元件更少的传动方案。In order to improve the performance of the vehicle (power performance, fuel economy, shifting performance), the number of car gears is developing towards more than six gears, and dump trucks also require more than six gears, so more gears need to be found. Combine drive solutions with fewer components.
发明内容Contents of the invention
本发明的目的在于提供一种车辆用十挡行星自动变速器,使用较少的行星排和结合元件使变速器实现更多的挡位。The object of the present invention is to provide a ten-speed planetary automatic transmission for vehicles, which uses fewer planetary rows and coupling elements to enable the transmission to achieve more gears.
本发明提出的多挡变速器，包括行星排、输入构件23、输出构件(24)、连接构件、离合器和制动器，所述行星排有四个，且为单行星轮行星排，第一行星排25包括第一齿圈1、第一行星架2、第一太阳轮3，第二行星排26包括第二齿圈4、第二行星架5、第二太阳轮6，第三行星排27包括第三齿圈7、第三行星架8、第三太阳轮9，第四行星排28包括第四齿圈10、第四行星架11、第四太阳轮12；所述连接构件有四个，分别为第一连接构件19、第二连接构件20、第三连接构件21和第四连接构件22；所述离合器有三个，分别为第一离合器13、第二离合器14和第三离合器15；所述制动器有三个，分别为第一制动器16、第二制动器17和第三制动器18；The multi-speed transmission proposed by the present invention includes a planetary row, an input member 23, an output member (24), a connecting member, a clutch, and a brake. There are four planetary rows, and they are single planetary wheel planetary rows. Including the first ring gear 1, the first planet carrier 2, and the first sun gear 3, the second planet row 26 includes the second ring gear 4, the second planet carrier 5, and the second sun gear 6, and the third planet row 27 includes the first The third ring gear 7, the third planet carrier 8, the third sun gear 9, and the fourth planet row 28 include the fourth ring gear 10, the fourth planet carrier 11, and the fourth sun gear 12; there are four connecting members, respectively It is the first connecting member 19, the second connecting member 20, the third connecting member 21 and the fourth connecting member 22; there are three clutches, namely the first clutch 13, the second clutch 14 and the third clutch 15; There are three brakes, respectively the first brake 16, the second brake 17 and the third brake 18;
所述第一连接构件19将所述第一行星架2、所述第二齿圈4与所述第三齿圈7固定地互连起来；The first connecting member 19 fixedly interconnects the first planet carrier 2, the second ring gear 4 and the third ring gear 7;
所述第二连接构件20将所述第一齿圈1与所述第二行星架5固定地互连起来；The second connecting member 20 fixedly interconnects the first ring gear 1 and the second planet carrier 5 ;
所述第三连接构件21将所述第三行星架8与所述第四齿圈10固定地互连起来；The third connecting member 21 fixedly interconnects the third planet carrier 8 with the fourth ring gear 10 ;
所述第四连接构件22将所述第三太阳轮9与所述第四太阳轮12固定地互连起来；Said fourth connecting member 22 fixedly interconnects said third sun gear 9 with said fourth sun gear 12;
所述第一离合器13将所述输入构件23与所述第四连接构件22互连起来；The first clutch 13 interconnects the input member 23 with the fourth connecting member 22;
所述第二离合器14将所述输入构件23与所述第二太阳轮6互连起来；The second clutch 14 interconnects the input member 23 with the second sun gear 6;
所述第三离合器15将所述第二太阳轮6与所述第三连接构件21互连起来；The third clutch 15 interconnects the second sun gear 6 with the third connecting member 21;
所述第一制动器16将所述第二连接构件20与固定构件互连起来；said first brake 16 interconnects said second connecting member 20 with a fixed member;
所述第二制动器17将所述第一太阳轮3与固定构件互连起来；said second brake 17 interconnects said first sun gear 3 with a stationary member;
所述第三制动器18将所述第三连接构件21与固定构件互连起来。The third brake 18 interconnects the third connecting member 21 with a fixed member.
本发明中，所述输出构件与所述第四行星架11固定地互连。In the present invention, the output member is fixedly interconnected with the fourth planet carrier 11 .
本发明中，述固定构件是变速器壳体。In the present invention, the fixing member is a transmission case.
本发明中，所述变速器建立至少十个前进速比和一个倒挡速比，具体为：In the present invention, the transmission establishes at least ten forward speed ratios and one reverse gear ratio, specifically:
当第二离合器14、第二制动器17、第三制动器18结合时，输入构件23和第二太阳轮6共同旋转，第一太阳轮3和第三连接构件21制动，实现倒挡；When the second clutch 14, the second brake 17, and the third brake 18 are combined, the input member 23 and the second sun gear 6 rotate together, and the first sun gear 3 and the third connecting member 21 brake to realize reverse gear;
当第二离合器14、第一制动器16和第三制动器18结合时，输入构件23和第二太阳轮6共同旋转，第二连接构件20和第三连接构件21制动，实现第一挡；When the second clutch 14, the first brake 16 and the third brake 18 are combined, the input member 23 and the second sun gear 6 rotate together, and the second connecting member 20 and the third connecting member 21 brake to realize the first gear;
当第一离合器13和第一制动器16和第三制动器18结合时，输入构件23和第四连接构件22共同旋转，第二连接构件20和第三连接构件21制动，实现第二挡；When the first clutch 13 is combined with the first brake 16 and the third brake 18, the input member 23 and the fourth connecting member 22 rotate together, and the second connecting member 20 and the third connecting member 21 brake to realize the second gear;
当第一离合器13、第二离合器14和第一制动器16结合时，输入构件23同时和第二太阳轮6及第四连接构件22共同旋转，第二连接构件20制动，实现第三挡；When the first clutch 13, the second clutch 14 and the first brake 16 are combined, the input member 23 rotates together with the second sun gear 6 and the fourth connecting member 22 at the same time, and the second connecting member 20 brakes to realize the third gear;
当第一离合器13、第三离合器15和第一制动器16结合时，输入构件23和第四连接构件22共同旋转，第二太阳轮6和第三连接构件21共同旋转，第二连接构件20制动，实现第四挡；When the first clutch 13, the third clutch 15 and the first brake 16 are combined, the input member 23 and the fourth connecting member 22 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the second connecting member 20 move to achieve the fourth gear;
当第一离合器13和第一制动器16和第二制动器17结合时，输入构件23和第四连接构件22共同旋转，第二连接构件20和第一太阳轮3制动，实现第五挡；When the first clutch 13 is combined with the first brake 16 and the second brake 17, the input member 23 and the fourth connecting member 22 rotate together, and the second connecting member 20 and the first sun gear 3 brake to realize the fifth gear;
当第一离合器13、第三离合器15和第二制动器17结合时，输入构件23和第四连接构件22共同旋转，第二太阳轮6和第三连接构件21共同旋转，第一太阳轮3制动，实现第六挡；When the first clutch 13, the third clutch 15 and the second brake 17 are combined, the input member 23 and the fourth connecting member 22 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the first sun gear 3 move to achieve the sixth gear;
当第一离合器13、第二离合器14和第二制动器17结合时，输入构件23同时和第二太阳轮6及第四连接构件22共同旋转，第一太阳轮3制动，实现第七挡；When the first clutch 13, the second clutch 14 and the second brake 17 are combined, the input member 23 rotates together with the second sun gear 6 and the fourth connecting member 22 at the same time, and the first sun gear 3 brakes to realize the seventh gear;
当第一离合器13、第二离合器14和第三离合器15结合时，输入构件23同时和第二太阳轮6、第四连接构件22以及第三连接构件21共同旋转，实现第八挡；When the first clutch 13, the second clutch 14 and the third clutch 15 are combined, the input member 23 rotates together with the second sun gear 6, the fourth connecting member 22 and the third connecting member 21 at the same time, realizing the eighth gear;
当第二离合器14、第三离合器15和第二制动器17结合时，输入构件23和第二太阳轮6共同旋转，第二太阳轮6和第三连接构件21共同旋转，第一太阳轮3制动，实现第九挡；When the second clutch 14, the third clutch 15 and the second brake 17 are combined, the input member 23 and the second sun gear 6 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the first sun gear 3 move to realize the ninth gear;
当第二离合器14、第三离合器15和第一制动器16结合时，输入构件23和第二太阳轮6共同旋转，第二太阳轮6和第三连接构件21共同旋转，第二连接构件20制动，实现第十挡。When the second clutch 14, the third clutch 15 and the first brake 16 are combined, the input member 23 and the second sun gear 6 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the second connecting member 20 Move to tenth gear.
本发明使用四个单行星轮行星排，六个结合元件包括三个离合器和三个制动器，结合其中三个，实现十个前进挡和一个倒挡。挡位间速比间隔在1.10至1.50之间，符合车辆的速比分配要求，并且结构简单，空转元件少，挡位间相互转换可能性大。The present invention uses four single-planet wheel planetary rows, and six combination elements include three clutches and three brakes, and three of them are combined to realize ten forward gears and one reverse gear. The speed ratio interval between the gears is between 1.10 and 1.50, which meets the speed ratio distribution requirements of the vehicle, and has a simple structure, fewer idling components, and a great possibility of mutual conversion between the gears.
附图说明Description of drawings
图1是本发明的十挡变速器各构件的布置及连接示意图。Fig. 1 is a schematic diagram of the arrangement and connection of various components of the ten-speed transmission of the present invention.
图2是间隔挡位间的转换图。Figure 2 is a transition diagram between interval gears.
图中标号：1为第一齿圈，2为第一行星架，3为第一太阳轮，4为第二齿圈，5为第二行星架，6为第二太阳轮，7为第三齿圈，8为第三行星架，9为第三太阳轮，10为第四齿圈，11为第四行星架，12为第四太阳轮，13为第一离合器，14为第二离合器，15为第三离合器，16为第一制动器，17为第二制动器，18为第三制动器，19为第一连接构件，20为第二连接构件，21为第三连接构件，22为第四连接构件，23为输入构件，24为输出构件，25为第一行星排，26为第二行星排，27为第三行星排，28为第四行星排。Numbers in the figure: 1 is the first ring gear, 2 is the first planet carrier, 3 is the first sun gear, 4 is the second ring gear, 5 is the second planet carrier, 6 is the second sun gear, 7 is the third Ring gear, 8 is the third planet carrier, 9 is the third sun gear, 10 is the fourth ring gear, 11 is the fourth planet carrier, 12 is the fourth sun gear, 13 is the first clutch, 14 is the second clutch, 15 is the third clutch, 16 is the first brake, 17 is the second brake, 18 is the third brake, 19 is the first connection member, 20 is the second connection member, 21 is the third connection member, 22 is the fourth connection Components, 23 is the input component, 24 is the output component, 25 is the first planetary row, 26 is the second planetary row, 27 is the third planetary row, 28 is the fourth planetary row.
具体实施方式detailed description
下面结合附图和具体实施方式对本发明做进一步说明。The present invention will be further described below in conjunction with the accompanying drawings and specific embodiments.
实施例1：Example 1:
1.构件连接及结合元件1. Component connection and combination elements
行星排之间的构件连接：Component connections between planetary rows:
参看图1：第一行星排25包括第一太阳轮3、第一行星架2、第一齿圈1；第一太阳轮3与第二制动器17相连接；第一行星架2与第一连接构件19相连；第一齿圈1与第二连接构件20及第一制动器16相连。Referring to Figure 1: the first planetary row 25 includes the first sun gear 3, the first planet carrier 2, and the first ring gear 1; the first sun gear 3 is connected to the second brake 17; the first planet carrier 2 is connected to the first The member 19 is connected; the first ring gear 1 is connected with the second connecting member 20 and the first brake 16 .
第二行星排26包括第二太阳轮6、第二行星架5、第二齿圈4；第二太阳轮6与第二离合器14及第三离合器15相连接；第二行星架5与第二连接构件20及第一制动器16相连；第二齿圈4与第一连接构件19相连。The second planet row 26 includes the second sun gear 6, the second planet carrier 5, and the second ring gear 4; the second sun gear 6 is connected with the second clutch 14 and the third clutch 15; the second planet carrier 5 is connected with the second The connecting member 20 is connected to the first brake 16 ; the second ring gear 4 is connected to the first connecting member 19 .
第三行星排27包括第三太阳轮9、第三行星架8、第三齿圈7；第三太阳轮9与第四连接构件22及第一离合器13相连接；第三行星架8与第三连接构件21及第三离合器15相连；第三齿圈7与第一连接构件19相连。The third planet row 27 includes the third sun gear 9, the third planet carrier 8, and the third ring gear 7; the third sun gear 9 is connected with the fourth connecting member 22 and the first clutch 13; the third planet carrier 8 is connected with the first clutch 13; The third connecting member 21 is connected to the third clutch 15 ; the third ring gear 7 is connected to the first connecting member 19 .
第四行星排28包括第四太阳轮12、第四行星架11、第四齿圈10；第四太阳轮12与第四连接构件22相连接；第四行星架11与输出构件相连；第四齿圈7与第三连接构件21及第三制动器18相连。The fourth planet row 28 includes the fourth sun gear 12, the fourth planet carrier 11, and the fourth ring gear 10; the fourth sun gear 12 is connected to the fourth connecting member 22; the fourth planet carrier 11 is connected to the output member; the fourth The ring gear 7 is connected to the third connecting member 21 and the third brake 18 .
结合元件的布置：Arrangement of binding elements:
第一离合器13可有选择地结合，以便将输入构件23与第四连接构件22连接起来。第二离合器14可有选择地结合，以便将输入构件23与第二太阳轮6连接起来。第三离合器15可有选择地结合，以便将第二太阳轮6与第三连接构件21连接起来。第一制动器16可有选择地结合，以便将第二连接构件20与壳体连接起来。第二制动器17可有选择地结合，以便将第一太阳轮3与壳体连接起来。第三制动器18可有选择地结合，以便将第三连接构件21与壳体连接起来。The first clutch 13 is selectively engageable to connect the input member 23 with the fourth connecting member 22 . The second clutch 14 is selectively engageable to connect the input member 23 with the second sun gear 6 . The third clutch 15 is selectively engageable to connect the second sun gear 6 with the third connecting member 21 . The first stopper 16 is selectively engageable to connect the second connecting member 20 to the housing. The second brake 17 is selectively engageable to connect the first sun gear 3 with the housing. The third stopper 18 is selectively engageable to connect the third connecting member 21 with the housing.
2.各挡位的实现方法2. The realization method of each gear
参看图1和表1，以十挡变速器的操作为例说明，表2中的九挡变速器挡位实现方法与十挡类似。Referring to Fig. 1 and Table 1, the operation of the ten-speed transmission is taken as an example to illustrate that the nine-speed transmission in Table 2 is similar to the ten-speed gear.
通过结合六个结合元件中的三个，能够获得包括2个超速挡在内的10个前进挡和1个倒退挡。图1是代表在各个挡位时的结合元件的结合状态表，其中“●”代表结合元件处于结合状态。表中还有各个挡位的速比及两个相邻挡位间的速比间隔。但需要注意，这些数字只是示例性的，而且可在极大范围内调整这些数值。所述速比是指输入转速与输出转速之比，行星排K值是指行星排的齿圈齿数与太阳轮齿数之比。By combining three of the six coupling elements, 10 forward gears including 2 overdrive gears and 1 reverse gear can be obtained. Fig. 1 is a table representing the combined states of the combined elements at various gears, where "●" means that the combined elements are in the combined state. The table also includes the speed ratio of each gear and the speed ratio interval between two adjacent gears. It should be noted, however, that these figures are exemplary only, and that these values can be adjusted within a wide range. The speed ratio refers to the ratio of the input rotational speed to the output rotational speed, and the K value of the planetary row refers to the ratio of the number of teeth of the ring gear of the planetary row to the number of teeth of the sun gear.
表1十挡变速器速比，速比间隔和结合元件结合状态表Table 1 Ten-speed transmission speed ratio, speed ratio interval and combination state of combination elements
k1=2.72;k2=2.70;k3=1.80;k4=2.43;i=8.84k1=2.72;k2=2.70;k3=1.80;k4=2.43;i=8.84
当第二离合器14、第二制动器17、第三制动器18结合时，输入构件23和第二太阳轮6共同旋转，第一太阳轮3和第三连接构件21制动，实现倒挡。When the second clutch 14, the second brake 17, and the third brake 18 are combined, the input member 23 and the second sun gear 6 rotate together, and the first sun gear 3 and the third connecting member 21 brake to realize reverse gear.
当第二离合器14、第一制动器16和第三制动器18结合时，输入构件23和第二太阳轮6共同旋转，第二连接构件20和第三连接构件21制动，实现第一挡。When the second clutch 14, the first brake 16 and the third brake 18 are combined, the input member 23 and the second sun gear 6 rotate together, and the second connecting member 20 and the third connecting member 21 brake to realize the first gear.
当第一离合器13和第一制动器16和第三制动器18结合时，输入构件23和第四连接构件22共同旋转，第二连接构件20和第三连接构件21制动，实现第二挡。When the first clutch 13 is combined with the first brake 16 and the third brake 18, the input member 23 and the fourth connecting member 22 rotate together, and the second connecting member 20 and the third connecting member 21 brake to realize the second gear.
当第一离合器13、第二离合器14和第一制动器16结合时，输入构件23同时和第二太阳轮6及第四连接构件22共同旋转，第二连接构件20制动，实现第三挡。When the first clutch 13 , the second clutch 14 and the first brake 16 are combined, the input member 23 rotates together with the second sun gear 6 and the fourth connecting member 22 at the same time, and the second connecting member 20 brakes to realize the third gear.
当第一离合器13、第三离合器15和第一制动器16结合时，输入构件23和第四连接构件22共同旋转，第二太阳轮6和第三连接构件21共同旋转，第二连接构件20制动，实现第四挡。When the first clutch 13, the third clutch 15 and the first brake 16 are combined, the input member 23 and the fourth connecting member 22 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the second connecting member 20 move to achieve fourth gear.
当第一离合器13和第一制动器16和第二制动器17结合时，输入构件23和第四连接构件22共同旋转，第二连接构件20和第一太阳轮3制动，实现第五挡。When the first clutch 13 is combined with the first brake 16 and the second brake 17, the input member 23 and the fourth connecting member 22 rotate together, and the second connecting member 20 and the first sun gear 3 brake to realize the fifth gear.
当第一离合器13、第三离合器15和第二制动器17结合时，输入构件23和第四连接构件22共同旋转，第二太阳轮6和第三连接构件21共同旋转，第一太阳轮3制动，实现第六挡。When the first clutch 13, the third clutch 15 and the second brake 17 are combined, the input member 23 and the fourth connecting member 22 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the first sun gear 3 Move to achieve sixth gear.
当第一离合器13、第二离合器14和第二制动器17结合时，输入构件23同时和第二太阳轮6及第四连接构件22共同旋转，第一太阳轮3制动，实现第七挡。When the first clutch 13, the second clutch 14 and the second brake 17 are combined, the input member 23 rotates together with the second sun gear 6 and the fourth connecting member 22 at the same time, and the first sun gear 3 brakes to realize the seventh gear.
当第一离合器13、第二离合器14和第三离合器15结合时，输入构件23同时和第二太阳轮6、第四连接构件22以及第三连接构件21共同旋转，实现第八挡。When the first clutch 13 , the second clutch 14 and the third clutch 15 are engaged, the input member 23 rotates together with the second sun gear 6 , the fourth connecting member 22 and the third connecting member 21 at the same time, realizing the eighth gear.
当第二离合器14、第三离合器15和第二制动器17结合时，输入构件23和第二太阳轮6共同旋转，第二太阳轮6和第三连接构件21共同旋转，第一太阳轮3制动，实现第九挡。When the second clutch 14, the third clutch 15 and the second brake 17 are combined, the input member 23 and the second sun gear 6 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the first sun gear 3 Move to achieve ninth gear.
当第二离合器14、第三离合器15和第一制动器16结合时，输入构件23和第二太阳轮6共同旋转，第二太阳轮6和第三连接构件21共同旋转，第二连接构件20制动，实现第十挡。When the second clutch 14, the third clutch 15 and the first brake 16 are combined, the input member 23 and the second sun gear 6 rotate together, the second sun gear 6 and the third connecting member 21 rotate together, and the second connecting member 20 Move to tenth gear.
3.低于十挡的变速器方案3. The transmission scheme below the tenth gear
参看图2，不相邻的挡位之间也可转换。例如第一挡可以直接换挡到第三挡，同时满足oneshift要求（只改变两个结合元件的结合状态）。在一定条件下可以实现挡位间的跳跃，跳过一些不需要的挡位，因此本发明也可作为十挡以下变速器使用。参看表2为十挡变速器去除一个挡位后得到的九挡变速器方案。Referring to Fig. 2, non-adjacent gears are also switchable. For example, the first gear can be directly shifted to the third gear, while meeting the requirements of oneshift (only changing the combined state of the two combined elements). Under certain conditions, jumping between gears can be realized, and some unnecessary gears can be skipped, so the present invention can also be used as a speed changer below ten gears. Refer to Table 2 for the nine-speed transmission scheme obtained after removing one gear from the ten-speed transmission.
表2九挡变速器速比，速比间隔和结合元件结合状态表Table 2 Nine-speed transmission speed ratio, speed ratio interval and combined state table of combining elements
k1=2.72;k2=2.70;k3=1.80;k4=2.43;i=8.84k1=2.72;k2=2.70;k3=1.80;k4=2.43;i=8.84
在本实施例中，k1=2.72;k2=2.70;k3=1.80;k4=2.43;总传动比范围为8.84。In this embodiment, k1=2.72; k2=2.70; k3=1.80; k4=2.43; the total transmission ratio range is 8.84.
但本发明的描述在性质上仅仅是示例性的，通过调整K值取值可大幅改变各挡速比和速比间隔，因而在不脱离本发明要点前提下的变形和改进将处于本发明的范围内。But the description of the present invention is only exemplary in nature, can greatly change each gear speed ratio and speed ratio interval by adjusting the value of K value, thus deformation and improvement will be in the scope of the present invention without departing from the gist of the present invention. within range.
Claims (4)
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Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101655581B1 (en) * | 2014-11-26 | 2016-09-08 | 현대자동차주식회사 | Multy stage transmmission for vehicle |
| KR101664050B1 (en) * | 2014-12-15 | 2016-10-10 | 현대자동차 주식회사 | Planetary gear train of automatic transmission for vehicles |
| KR101684062B1 (en) * | 2015-02-09 | 2016-12-08 | 현대자동차주식회사 | Multy stage transmmission for vehicle |
| KR101734270B1 (en) * | 2015-05-13 | 2017-05-11 | 현대자동차 주식회사 | Planetary gear train of automatic transmission for vehicles |
| EP3320228B1 (en) | 2015-07-10 | 2020-08-19 | Volvo Construction Equipment AB | A method for controlling a gear shift in a transmission arrangement |
| WO2017044021A1 (en) * | 2015-09-09 | 2017-03-16 | Volvo Construction Equipment Ab | A transmission arrangement for a vehicle |
| WO2017044020A1 (en) | 2015-09-09 | 2017-03-16 | Volvo Construction Equipment Ab | A transmission arrangement for a vehicle |
| EP3347619B1 (en) | 2015-09-09 | 2020-10-28 | Volvo Construction Equipment AB | A transmission arrangement for a vehicle |
| DE102015016740A1 (en) * | 2015-12-23 | 2017-06-29 | Daimler Ag | Multi-speed transmission with ten forward gears |
| DE102015016994A1 (en) * | 2015-12-24 | 2017-06-29 | Daimler Ag | Multi-speed transmission with ten forward gears |
| DE102016203887A1 (en) * | 2016-03-09 | 2017-09-14 | Zf Friedrichshafen Ag | Automatic transmission in planetary construction |
| KR101846889B1 (en) * | 2016-03-18 | 2018-04-09 | 현대자동차 주식회사 | Planetary gear train of automatic transmission for vehicles |
| US10473190B2 (en) | 2016-09-28 | 2019-11-12 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10316940B2 (en) | 2016-09-28 | 2019-06-11 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10072735B2 (en) * | 2016-09-28 | 2018-09-11 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10253850B2 (en) | 2016-09-28 | 2019-04-09 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10364867B2 (en) | 2016-09-28 | 2019-07-30 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10323722B2 (en) | 2016-09-28 | 2019-06-18 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| US10302173B2 (en) * | 2016-09-28 | 2019-05-28 | Allison Transmission, Inc. | Multi-speed planetary transmission |
| CN108180265B (en) * | 2017-12-29 | 2021-12-24 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN108194587B (en) * | 2017-12-29 | 2021-10-26 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4420992A (en) * | 1981-07-07 | 1983-12-20 | Caterpillar Tractor Co. | Planetary transmission |
| CN103032532A (en) * | 2011-10-03 | 2013-04-10 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| DE102009028671A1 (en) * | 2009-08-20 | 2011-02-24 | Zf Friedrichshafen Ag | Multi-speed transmission |
| US8758187B2 (en) * | 2012-02-06 | 2014-06-24 | Gm Global Technology Operations, Llc | Multi-speed transmission |
-
2014
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4420992A (en) * | 1981-07-07 | 1983-12-20 | Caterpillar Tractor Co. | Planetary transmission |
| CN103032532A (en) * | 2011-10-03 | 2013-04-10 | 通用汽车环球科技运作有限责任公司 | Multi-speed transmission |
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