CN112324873A - Multi-gear transmission of passenger car - Google Patents

Multi-gear transmission of passenger car Download PDF

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Publication number
CN112324873A
CN112324873A CN202011356560.2A CN202011356560A CN112324873A CN 112324873 A CN112324873 A CN 112324873A CN 202011356560 A CN202011356560 A CN 202011356560A CN 112324873 A CN112324873 A CN 112324873A
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China
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gear
clutch
sun gear
planetary
engaged
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CN202011356560.2A
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Chinese (zh)
Inventor
李玉良
余锐
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Donghua University
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Donghua University
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • 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
    • 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
    • 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
    • F16H2200/202—Transmissions using gears with orbital motion characterised by the type of Ravigneaux set

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

本发明公开了一种乘用车多挡变速器，包括输入轴、输出轴、第一行星排、第二行星排和第三行星排，所述输入轴上连接有第一行星排和第二行星排，所述输出轴上连接有第三行星排，第三行星排通过四个离合器分别与第一行星排和第二行星排连接，第一行星排和第三行星排均设置有一个制动器，通过不同离合器和制动器的结合和分离，可实现不同挡位的切换。本发明结构简单，在满足多挡位需求的情况下使用较少的零件数量，降低结构复杂性，使制造安装简易，减小变速器尺寸。

Figure 202011356560

The invention discloses a multi-speed transmission for passenger cars, comprising an input shaft, an output shaft, a first planetary row, a second planetary row and a third planetary row, and the input shaft is connected with the first planetary row and the second planetary row The output shaft is connected with a third planetary row, the third planetary row is connected with the first planetary row and the second planetary row respectively through four clutches, and the first planetary row and the third planetary row are both provided with a brake, Through the combination and separation of different clutches and brakes, the switching of different gears can be realized. The present invention has a simple structure, uses a small number of parts under the condition of meeting the requirements of multiple gears, reduces the structural complexity, makes the manufacture and installation simple, and reduces the size of the transmission.

Figure 202011356560

Description

Multi-gear transmission of passenger car
Technical Field
The invention relates to the field of automobile transmissions, in particular to a multi-gear transmission for a passenger vehicle.
Background
The transmission is one of important parts of an automobile transmission system, and plays an important place in the development process of automobile products. The main function of the speed changer is to make the passenger car better adapt to various road conditions, adjust the speed of the car in time and meet various driving requirements of the driver. The multi-gear transmission can provide a reasonable gear range in the driving process of an automobile, and the reasonable gear range can meet certain driving comfort, reduce the oil consumption of the automobile and ensure certain economical efficiency. The excellent transmission can greatly improve the performance of automobile products. In order to improve the driving comfort and fuel saving characteristics of automobiles, the development of automatic transmissions is directed toward multi-speed, compact and lightweight transmissions. The multi-gear development mainly considers the dynamic property and fuel property of the automobile, and in terms of the dynamic property, the gears are more, so that the engine can exert the maximum power and use high power as much as possible, and the climbing and accelerating capability of the automobile is improved.
The prior market is more applied to hydraulic automatic transmissions, which mainly use a planetary gear mechanism as a transmission device, and the planetary gear mechanism mainly comprises three types: basic planetary gear mechanism, Simpson gear mechanism, Ravigneaux gear mechanism.
However, the existing planetary transmission for passenger vehicles generally adopts 4 rows and more basic planetary rows to meet the requirement of more gears, for example, the existing patent document CN101275644A, named as "eight-gear automatic transmission", is a requirement that 4 basic planetary rows are needed to achieve 8-gear shifting, and has a complex structure, so that the structure of the transmission is too large, the manufacturing is difficult, and the cost is high.
Disclosure of Invention
The invention provides a multi-gear transmission of a passenger car, which has a simple structure, uses less parts under the condition of meeting the requirement of multiple gears, reduces the structural complexity, ensures simple manufacture and installation and reduces the size of the transmission.
In order to achieve the purpose, the invention provides the following technical scheme: a passenger car multi-gear transmission comprises an input shaft, a first planet row, a second planet row, a third planet row and an output shaft, wherein the first planet row comprises a first sun gear, a first gear ring, a first planet carrier and a first planet gear;
the second planet row comprises a second sun gear and a second planet gear, the second planet gear is arranged on the first planet carrier and is simultaneously meshed with the first planet gear and the second sun gear, and a third clutch is arranged outside the second sun gear;
the third planet row comprises a third sun gear, a second gear ring, a second planet carrier and a third planet gear, the second gear ring is connected with a third clutch, the second gear ring is connected with a fourth clutch, a first clutch is connected between the second planet carrier and the first sun gear, the second clutch is arranged between the third sun gear and the first sun gear, a second brake is arranged outside the third sun gear, the third planet gear is arranged on the second planet carrier and is meshed with the second gear ring and the third sun gear simultaneously, and the output shaft is fixedly connected with the second planet carrier.
And the switching of different gears is realized through the connection and the disconnection of the first brake, the second brake, the first clutch, the second clutch, the third clutch and the fourth clutch. It can be seen that a standard Ravigneaux structure is formed by the first planet row and the second planet row, and compared with a common planet row structure, the structure has fewer components, more compact structure and smaller size.
When the second brake is engaged, the third sun gear is fixed, meanwhile, the second clutch is engaged, the first sun gear and the third sun gear are connected into a whole, meanwhile, the fourth clutch is engaged, the first ring gear and the second ring gear are connected into a whole, and at the moment, forward and first gear are realized;
when the second brake is engaged, the third sun gear is fixed, meanwhile, the first clutch is engaged, the first sun gear and the second planet carrier are connected into a whole, meanwhile, the fourth clutch is engaged, the first ring gear and the second ring gear are connected into a whole, and at the moment, forward and second gears are realized;
when the second brake is engaged, the third sun gear is fixed, meanwhile, the third clutch is engaged, the second sun gear and the second gear ring are connected into a whole, and simultaneously, the fourth clutch is engaged, the first gear ring gear and the second gear ring are connected into a whole, so that the forward three gears are realized;
when the second brake is engaged, the third sun gear is fixed, meanwhile, the first clutch is engaged, the first sun gear and the second planet carrier are connected into a whole, meanwhile, the third clutch is engaged, the second sun gear and the second gear ring are connected into a whole, and at the moment, forward fourth gear is realized;
when the first clutch is engaged, the first sun gear and the second planet carrier are connected into a whole, meanwhile, the second clutch is engaged, the first sun gear and the third sun gear are connected into a whole, meanwhile, the third clutch is engaged, and the second sun gear and the second gear ring are connected into a whole, so that the forward fifth gear is realized;
when the second brake is engaged, the third sun gear is fixed, meanwhile, the second clutch is engaged, the first sun gear and the third sun gear are connected into a whole, meanwhile, the third clutch is engaged, and the second sun gear and the second gear ring are connected into a whole, so that the forward six-gear is realized;
when the first brake is engaged, the first gear ring is fixed, meanwhile, the second clutch is engaged, the first sun gear and the third sun gear are connected into a whole, meanwhile, the third clutch is engaged, and the second sun gear and the second gear ring are connected into a whole, so that a forward seven-gear is realized;
when the first brake is engaged, the first gear ring is fixed, meanwhile, the second brake is engaged, the third sun gear is fixed, meanwhile, the third clutch is engaged, and the second sun gear and the second gear ring are connected into a whole, so that eight forward gears are realized;
when the second brake is engaged, the third sun gear is fixed, and at the same time, the second clutch is engaged, the first sun gear and the third sun gear are connected into a whole, and at the same time, the fourth clutch is engaged, the first ring gear and the second ring gear are connected into a whole, so that the reverse gear is realized.
Preferably, the first brake and the second brake are both wet multi-disc brakes.
Preferably, the first clutch, the second clutch, the third clutch and the fourth clutch are all wet multi-plate clutches.
Compared with the prior art, the invention has the beneficial effects that:
the invention adopts 1 standard Ravigneaux structure and 1 single planet row, and 2 clutches and 4 clutches arranged on the planet row, realizes 8 forward gears and 1 backward gear, realizes the requirement of multi-gear speed change by using less parts, and has simple structure, convenient manufacture and installation and small mechanism size.
Drawings
FIG. 1 is a schematic structural view of the present invention;
reference numerals: 1. an input shaft; 2. an output shaft; 3. a first planet row; 31. a first sun gear; 32. a first ring gear; 33. a first carrier; 34. a first planet gear; 4. a second planet row; 41. a second sun gear; 44. a second planet wheel; 5. a third planet row; 51. a third sun gear; 52. a second ring gear; 53. a second planet carrier 54, a third planet gear; 7. a first brake; 8. a second brake; 9. a first clutch; 10. a second clutch; 11. a third clutch; 12. and a fourth clutch.
Detailed Description
The technical solution in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention.
As shown in fig. 1, the invention relates to a multi-speed transmission for a passenger vehicle, comprising an input shaft 1, a first planetary row 3, a second planetary row 4, a third planetary row 5 and an output shaft 2, characterized in that,
the first planet carrier 3 comprises a first sun gear 31, a first ring gear 32, a first planet carrier 33 and a first planet gear 34, a first brake 7 and a fourth clutch 12 are arranged outside the first ring gear 32, the first planet gear 34 is arranged on the first planet carrier 33 and meshed with the first sun gear 31, and the input shaft 1 is fixedly connected with the first planet carrier 33;
the second planetary row 4 comprises a second sun gear 41 and a second planetary gear 44, the second planetary gear 44 is arranged on the first planetary carrier 33 and is meshed with the first planetary gear 34 and the second sun gear 41 at the same time, and a third clutch 11 is arranged outside the second sun gear 41;
the third planetary gear set 5 includes a third sun gear 51, a second ring gear 52, a second planetary carrier 53 and a third planetary gear 54, the second ring gear 52 is connected with a third clutch 11, the second ring gear 52 is connected with a fourth clutch 12, a first clutch 9 is connected between the second planetary carrier 53 and the first sun gear 31, a second clutch 10 is arranged between the third sun gear 51 and the first sun gear 31, a second brake 8 is arranged outside the third sun gear 51, the third planetary gear 54 is arranged on the second planetary carrier 53, and is simultaneously engaged with the second ring gear 52 and the third sun gear 51, and the output shaft 2 is fixedly connected with the second planetary carrier 53.
It can be seen that in the present embodiment, the first planet row 3 and the second planet row 4 form a standard ravigneaux structure, which has fewer components, a more compact structure and a smaller size compared with a common planet row structure.
The switching of different gears is realized by the engagement and disengagement of the first brake 7, the second brake 8, the first clutch 9, the second clutch 10, the third clutch 11 and the fourth clutch 12.
The specific use principle is as follows:
when the second brake 8 is engaged, the third sun gear 51 is fixed, the second clutch 10 is engaged, the first sun gear 31 and the third sun gear 51 are connected into a whole, and the fourth clutch 12 is engaged, the first ring gear 32 and the second ring gear 52 are connected into a whole, so that the forward first gear is realized, and the transmission ratio of the forward first gear is 3.251;
when the second brake 8 is engaged, the third sun gear 51 is fixed, the first clutch 9 is engaged, the first sun gear 31 and the second carrier 53 are connected into a whole, and the fourth clutch 12 is engaged, the first ring gear 32 and the second ring gear 52 are connected into a whole, so that the forward two-gear is realized, and the transmission ratio of the forward two-gear is 2.28;
when the second brake 8 is engaged, the third sun gear 51 is fixed, the third clutch 11 is engaged, the second sun gear 41 and the second ring gear 52 are connected into a whole, and the fourth clutch 12 is engaged, the first ring gear 32 and the second ring gear 52 are connected into a whole, so that the forward third gear is realized, and the transmission ratio of the forward third gear is 1.649;
when the second brake 8 is engaged, the third sun gear 51 is fixed, the first clutch 9 is engaged, the first sun gear 31 and the second carrier 53 are connected as a whole, and the third clutch 11 is engaged, the second sun gear 41 and the second ring gear 52 are connected as a whole, so that the fourth forward gear is realized, and the transmission ratio of the fourth forward gear is 1.372;
when the first clutch 9 is engaged, the first sun gear 31 and the second planet carrier 53 are connected into a whole, meanwhile, the second clutch 10 is engaged, the first sun gear 31 and the third sun gear 51 are connected into a whole, meanwhile, the third clutch 11 is engaged, the second sun gear 41 and the second ring gear 52 are connected into a whole, then, the forward fifth gear is realized, and the transmission ratio of the forward fifth gear is 1;
when the second brake 8 is engaged, the third sun gear 51 is fixed, at the same time, the second clutch 10 is engaged, the first sun gear 31 and the third sun gear 51 are connected into a whole, at the same time, the third clutch 11 is engaged, the second sun gear 41 and the second ring gear 52 are connected into a whole, and then, the forward six gears are realized, and the transmission ratio of the forward six gears is 0.946;
when the first brake 7 is engaged to fix the first ring gear 32, the second clutch 10 is engaged, the first sun gear 31 and the third sun gear 51 are integrally connected, and the third clutch 11 is engaged to integrally connect the second sun gear 41 and the second ring gear 52, thereby realizing seven forward gears, wherein the transmission ratio of the seven forward gears is 0.896;
when the first brake 7 is engaged, the first ring gear 32 is fixed, the second brake 8 is engaged, the third sun gear 51 is fixed, the third clutch 11 is engaged, and the second sun gear 41 and the second ring gear 52 are connected into a whole, so that the eight forward gears are realized, and the transmission ratio of the eight forward gears is 0.657;
when the second brake 8 is engaged to fix the third sun gear 51, the second clutch 10 is engaged to integrally connect the first sun gear 31 and the third sun gear 51, and the fourth clutch 12 is engaged to integrally connect the first ring gear 32 and the second ring gear 52, the reverse gear is realized, and the transmission ratio of the reverse gear is-2.466.
The parameters for each planet row are detailed in the following table:
TABLE 1 is the parameter table of each planetary row of the transmission
Figure BDA0002802728100000071
The operation and transmission ratio of the operating elements in each working condition are detailed in the following table:
TABLE 2 operating table for operating elements of various working conditions
Figure BDA0002802728100000072
While the invention has been described above with reference to an embodiment, various modifications may be made and equivalents may be substituted for elements thereof without departing from the scope of the invention. In particular, the various features of the embodiments disclosed herein may be used in any combination, provided that there is no structural conflict, and the combinations are not exhaustively described in this specification merely for the sake of brevity and conservation of resources. Therefore, it is intended that the invention not be limited to the particular embodiments disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.

Claims (3)

1.一种乘用车多挡变速器，包括输入轴(1)、第一行星排(3)、第二行星排(4)、第三行星排(5)和输出轴(2)，其特征在于，1. A multi-speed transmission for a passenger car, comprising an input shaft (1), a first planetary row (3), a second planetary row (4), a third planetary row (5) and an output shaft (2), wherein is, 所述第一行星排(3)包括第一太阳轮(31)、第一齿圈(32)、第一行星架(33)和第一行星轮(34)，所述第一齿圈(32)外部设置有第一制动器(7)和第四离合器(12)，所述第一行星轮(34)设置在所述第一行星架(33)上且与所述第一太阳轮(31)啮合，所述输入轴(1)与第一行星架(33)固定连接；The first planetary row (3) includes a first sun gear (31), a first ring gear (32), a first planet carrier (33) and a first planetary gear (34). The first ring gear (32) ) externally provided with a first brake (7) and a fourth clutch (12), the first planetary gear (34) is arranged on the first planetary carrier (33) and is connected with the first sun gear (31) meshing, the input shaft (1) is fixedly connected with the first planet carrier (33); 所述第二行星排(4)包括第二太阳轮(41)和第二行星轮(44)，所述第二行星轮(44)设置在所述第一行星架(33)上，且同时与第一行星轮(34)以及第二太阳轮(41)啮合，所述第二太阳轮(41)外部设置有第三离合器(11)；The second planetary row (4) includes a second sun gear (41) and a second planetary gear (44), the second planetary gear (44) is arranged on the first planetary carrier (33), and at the same time meshing with the first planetary gear (34) and the second sun gear (41), the second sun gear (41) is provided with a third clutch (11) outside; 所述第三行星排(5)包括第三太阳轮(51)、第二齿圈(52)、第二行星架(53)和第三行星轮(54)，所述第二齿圈(52)与第三离合器(11)相连，所述第二齿圈(52)与第四离合器(12)相连，所述第二行星架(53)与第一太阳轮(31)之间连接有第一离合器(9)，所述第三太阳轮(51)与第一太阳轮(31)之间设置有第二离合器(10)，所述第三太阳轮(51)外部设置有第二制动器(8)，所述第三行星轮(54)设置在第二行星架(53)上，且同时与第二齿圈(52)以及第三太阳轮(51)啮合，所述输出轴(2)与第二行星架(53)固定连接。The third planetary row (5) includes a third sun gear (51), a second ring gear (52), a second planet carrier (53) and a third planetary gear (54). The second ring gear (52) ) is connected with the third clutch (11), the second ring gear (52) is connected with the fourth clutch (12), and the second planet carrier (53) is connected with the first sun gear (31) A clutch (9), a second clutch (10) is arranged between the third sun gear (51) and the first sun gear (31), and a second brake ( 8), the third planetary gear (54) is arranged on the second planetary carrier (53), and meshes with the second ring gear (52) and the third sun gear (51) at the same time, the output shaft (2) It is fixedly connected with the second planet carrier (53). 2.根据权利要求1所述的乘用车多挡变速器，其特征在于：所述第一制动器(7)和第二制动器(8)均为湿式多盘制动器。2 . The multi-speed transmission for passenger cars according to claim 1 , wherein the first brake ( 7 ) and the second brake ( 8 ) are both wet multi-disc brakes. 3 . 3.根据权利要求2所述的乘用车多挡变速器，其特征在于：所述第一离合器(9)、第二离合器(10)、第三离合器(11)和第四离合器(12)均为湿式多片式离合器。3. The multi-speed transmission for a passenger car according to claim 2, wherein the first clutch (9), the second clutch (10), the third clutch (11) and the fourth clutch (12) are all It is a wet multi-plate clutch.
CN202011356560.2A 2020-11-27 2020-11-27 Multi-gear transmission of passenger car Pending CN112324873A (en)

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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2093736C1 (en) * 1995-08-15 1997-10-20 Волгоградский государственный технический университет Planet gear box
CN202165553U (en) * 2011-06-30 2012-03-14 长城汽车股份有限公司 Automatic transmission with eight forward gears and one reverse gear
CN205383229U (en) * 2016-03-21 2016-07-13 岭南师范学院 Novel nine -gear automatic gearbox drive mechanism
CN205383227U (en) * 2016-03-21 2016-07-13 岭南师范学院 Nine -gear automatic gearbox drive mechanism
CN110822034A (en) * 2018-08-10 2020-02-21 广州汽车集团股份有限公司 Nine-speed automatic transmission
CN111577844A (en) * 2020-04-28 2020-08-25 东华大学 Passenger car gearbox

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2093736C1 (en) * 1995-08-15 1997-10-20 Волгоградский государственный технический университет Planet gear box
CN202165553U (en) * 2011-06-30 2012-03-14 长城汽车股份有限公司 Automatic transmission with eight forward gears and one reverse gear
CN205383229U (en) * 2016-03-21 2016-07-13 岭南师范学院 Novel nine -gear automatic gearbox drive mechanism
CN205383227U (en) * 2016-03-21 2016-07-13 岭南师范学院 Nine -gear automatic gearbox drive mechanism
CN110822034A (en) * 2018-08-10 2020-02-21 广州汽车集团股份有限公司 Nine-speed automatic transmission
CN111577844A (en) * 2020-04-28 2020-08-25 东华大学 Passenger car gearbox

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