CN112984060A - Eight-front two-reverse planetary gear automatic transmission - Google Patents

Eight-front two-reverse planetary gear automatic transmission Download PDF

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Publication number
CN112984060A
CN112984060A CN202110456753.3A CN202110456753A CN112984060A CN 112984060 A CN112984060 A CN 112984060A CN 202110456753 A CN202110456753 A CN 202110456753A CN 112984060 A CN112984060 A CN 112984060A
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China
Prior art keywords
gear
rotating element
engagement
planetary
closed
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Pending
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CN202110456753.3A
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Chinese (zh)
Inventor
徐向阳
董鹏
徐荥
刘艳芳
王书翰
郭伟
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Beihang University
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Beihang University
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Priority to CN202110456753.3A priority Critical patent/CN112984060A/en
Publication of CN112984060A publication Critical patent/CN112984060A/en
Pending legal-status Critical Current

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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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • 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
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements

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

Abstract

The invention discloses an eight-front-two-reverse planetary gear automatic transmission, which adopts 4 minus planetary rows, 7 rotating shafts and 6 gear shifting elements, and comprises 2 clutches and 4 brakes, wherein the 4 brakes are arranged in a nested planetary row, and the 2 clutches are positioned at the front part of the transmission, so that the structural layout is more compact. According to the invention, each gear is closed by 2 gear shifting elements, 8 forward gears and 2 reverse gears can be realized, and a wider speed ratio range and a more uniform transmission step ratio can be obtained along with the increase of the gear number.

Description

Eight-front two-reverse planetary gear automatic transmission
Technical Field
The invention belongs to the technical field of vehicle transmissions, relates to a multi-gear planetary gear automatic transmission, and particularly relates to a longitudinally-arranged eight-front-two-reverse planetary gear automatic transmission for a front-mounted rear-drive vehicle.
Background
In the process of continuous development of the automobile industry, a transmission which is an important component of a transmission system is also rapidly developed and evolved, the number of gears of a passenger vehicle or a commercial vehicle is continuously increased, and the transmission ratio range is also continuously enlarged, so that the automobile is more flexible in gear shifting, and a driver can have better driving experience. The existing hydromechanical automatic transmission comprises a planet row, a clutch and a brake, the conversion of various transmission ratios can be realized by controlling the clutch and the brake, the power transmission is completed by depending on a planetary gear set, and the main structure of the transmission comprises a sun gear, a planet carrier and a gear ring. In a sequential shifting mode, an automatic transmission should try to avoid engaging and disengaging two shifting elements, and should try to follow a simple shift logic.
In the prior art, 8-gear planetary automatic transmissions are mentioned, which comprise 4 planetary rows, 6 shift elements (3 clutches and 3 brakes), and 3 shift elements are engaged per gear to achieve 8 forward gears and 1 reverse gear. However, the scheme can only realize 1 reverse gear, the number of the reverse gears is small, 3 clutches and 3 brakes are arranged in 6 gear shifting elements, 2 clutches are arranged in the middle of the transmission in 3 clutches, and the oil supply duct is complex in design and high in cost.
The prior art also mentions a 7-speed hydroautomatic transmission comprising 4 planetary rows, 6 shift elements (2 clutches and 4 brakes), each gear closing 2 shift elements achieving 7 forward gears and 2 reverse gears. In the solution, there are 6 shift elements, 2 clutches and 4 brakes, but only 7 forward gears can be achieved. And one planet row in the 4 planet rows is a plus planet row, the plus planet row has more parts, complex design and high cost, and the inherent transmission efficiency is lower than that of a minus planet row.
Disclosure of Invention
In order to solve the defects of the prior art, the invention provides an eight-front two-reverse planetary gear automatic transmission, which has the following specific technical scheme:
an eight-front two-reverse planetary automatic transmission comprising:
the box body is a fixed component and is used for mounting the transmission, and the brake is connected with the box body to realize the opening and closing of the brake so as to realize the switching of the gear shifting modes;
seven rotating elements, namely a first rotating element, a second rotating element, a third rotating element, a fourth rotating element, a fifth rotating element, a sixth rotating element and a seventh rotating element; the first rotating element is an input shaft, and the second rotating element is an output shaft and is used for power input and power output respectively; the third rotating element, the fourth rotating element, the fifth rotating element, the sixth rotating element, and the seventh rotating element are used for power transmission between the planetary rows;
a shift element including four brakes, a third engagement element, a fourth engagement element, a fifth engagement element, and a sixth engagement element, respectively; two clutches, a first engaging element and a second engaging element, respectively;
four planetary rows, respectively a first planetary row P1, a second planetary row P2, a third planetary row P3 and a fourth planetary row P4;
wherein the first engaging element connects the first rotating element and the third rotating element; the second engaging element connects the first rotating element and the fourth rotating element;
the third joint element connects the seventh rotating element and the box body, the fourth joint element connects the sixth rotating element and the box body, the fifth joint element connects the fifth rotating element and the box body, and the sixth joint element connects the fourth rotating element and the box body; the third engagement element, the fourth engagement element, the fifth engagement element, and the sixth engagement element are all abutted against the inner wall of the case, the third engagement element is nested outside the ring gear of the first planetary row P1, the fourth engagement element is nested outside the ring gear of the second planetary row P2, the fifth engagement element is nested outside the ring gear of the third planetary row P3, and the sixth engagement element is nested outside the ring gear of the fourth planetary row P4;
the sun gear of the first planetary row P1 is located on the first rotating element, the carrier is located on the sixth rotating element, and the ring gear is located on the seventh rotating element; the sun gear of the second planetary row P2 is located on the first rotating element, the carrier is located on the fifth rotating element, and the ring gear is located on the sixth rotating element; the sun gear of the third planetary row P3 is located on the third rotating element, the carrier is located on the fourth rotating element, and the ring gear is located on the fifth rotating element; the sun gear of the fourth planetary row P4 is located on the third rotating element, the carrier is located on the second rotating element, and the ring gear is located on the fourth rotating element;
the shifting elements can be selectively operated, so that eight forward gears and two reverse gears can be realized by different transmission ratios between the first and second rotating elements, each gear only requiring two shifting elements to be closed.
Preferably, all the planet rows comprise a sun wheel, a planet wheel and a ring gear; the first, second, third and fourth planetary rows P1, P2, P3, P4 are simple negative planetary rows and the main gear ratios are all negative.
Preferably, a second reverse gear is realized by the third and sixth engaging elements being closed, a first reverse gear is realized by the fourth and sixth engaging elements being closed, a first forward gear is realized by the first and sixth engaging elements being closed, a second forward gear is realized by the first and fifth engaging elements being closed, a third forward gear is realized by the first and fourth engaging elements being closed, a fourth forward gear is realized by the first and third engaging elements being closed, a fifth forward gear is realized by the first and second engaging elements being closed, a sixth forward gear is realized by the second and third engaging elements being closed, and a seventh forward gear is realized by the second and fourth engaging elements being closed, the eighth forward gear is achieved by the second engaging element and the fifth engaging element being closed.
The invention has the advantages that:
1. according to the invention, a very efficient gear shifting combination of 8 forward gears and 2 reverse gears is realized through six gear shifting elements, more gears can enable the vehicle to work in a reasonable interval, oil is saved more, and the reverse gear performance of the vehicle is obviously improved by two reverse gear speed ratios.
2. According to the invention, the adjacent gears are simply shifted, and only the mutual combination and separation between the clutch and the brake are required to be controlled, so that compared with the situation that two gears are separated and the other two gears are combined, the shifting process is easier to control, and the shifting impact can be reduced, so that the shifting is smoother.
3. The double-clutch transmission has the advantages that the number of brakes is large, the brakes are all connected with the gear rings of the planet row, the gear rings can be arranged in a nested manner with the planet row, the axial length of the transmission is reduced, the clutch is located at the front end of the transmission, the double clutches are arranged in a nested manner, the clutch group can be formed, and the design complexity of an oil supply passage is reduced.
4. The invention is formed by combining simple minus planet rows, has fewer parts, low production cost and better overall reliability, and can effectively prolong the service life of the transmission.
5. The planet rows are structurally characterized in that the planet carriers of one group of planet rows are connected with the gear rings of the other group of planet rows, so that the connection span between the planet rows is small, and the structure is reliable.
Drawings
In order to illustrate embodiments of the present invention or technical solutions in the prior art more clearly, the drawings which are needed in the embodiments will be briefly described below, so that the features and advantages of the present invention can be understood more clearly by referring to the drawings, which are schematic and should not be construed as limiting the present invention in any way, and for a person skilled in the art, other drawings can be obtained on the basis of these drawings without any inventive effort. Wherein:
fig. 1 is a structural view of an eight-front two-reverse planetary gear automatic transmission, in which 1-a first rotating element, 2-a second rotating element, 3-a third rotating element, 4-a fourth rotating element, 5-a fifth rotating element, 6-a sixth rotating element, 7-a seventh rotating element, 8-a first engaging element, 9-a second engaging element, 10-a third engaging element, 11-a fourth engaging element, 12-a fifth engaging element, and 13-a sixth engaging element.
Detailed Description
In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments of the present invention and features of the embodiments may be combined with each other without conflict.
In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced in other ways than those specifically described herein, and therefore the scope of the present invention is not limited by the specific embodiments disclosed below.
As shown in fig. 1, an eight-front two-reverse planetary automatic transmission includes: the gearbox is a fixed component and used for mounting a transmission, and the brake is connected with the gearbox to realize opening and closing of the brake so as to realize switching of gear shifting modes;
seven rotating elements, a first rotating element 1, a second rotating element 2, a third rotating element 3, a fourth rotating element 4, a fifth rotating element 5, a sixth rotating element 6 and a seventh rotating element 7, respectively; the first rotating element 1 is an input shaft, and the second rotating element 2 is an output shaft, and is used for power input and power output respectively; the third rotating element 3, the fourth rotating element 4, the fifth rotating element 5, the sixth rotating element 6, and the seventh rotating element 7 are used for power transmission between the planetary rows;
shift elements including four brakes, a third engaging element 10, a fourth engaging element 11, a fifth engaging element 12, and a sixth engaging element 13, respectively; two clutches, respectively, a first engaging element 8 and a second engaging element 9;
four planetary rows, respectively a first planetary row P1, a second planetary row P2, a third planetary row P3 and a fourth planetary row P4;
wherein the first engaging element 8 connects the first rotating element 1 and the third rotating element 3; the second engaging element 9 connects the first rotating element 1 and the fourth rotating element 4;
a third engaging member 10 connects the seventh rotating member 7 and the case, a fourth engaging member 11 connects the sixth rotating member 6 and the case, a fifth engaging member 12 connects the fifth rotating member 5 and the case, and a sixth engaging member 13 connects the fourth rotating member 4 and the case; the third engaging element 10, the fourth engaging element 11, the fifth engaging element 12 and the sixth engaging element 13 are all abutted against the inner wall of the case, the third engaging element 10 is nested outside the ring gear of the first planetary row P1, the fourth engaging element 11 is nested outside the ring gear of the second planetary row P2, the fifth engaging element 12 is nested outside the ring gear of the third planetary row P3, and the sixth engaging element 13 is nested outside the ring gear of the fourth planetary row P4;
the sun gear of the first planetary row P1 is located on the first rotating element 1, the planet carrier is located on the sixth rotating element 6, and the ring gear is located on the seventh rotating element 7; the sun gear of the second planetary row P2 is located on the first rotating element 1, the planet carrier is located on the fifth rotating element 5, and the ring gear is located on the sixth rotating element 6; the sun gear of the third planetary row P3 is located on the third rotating element 3, the planet carrier is located on the fourth rotating element 4, and the ring gear is located on the fifth rotating element 5; the sun gear of the fourth planetary row P4 is located on the third rotating element 3, the planet carrier is located on the second rotating element 2, and the ring gear is located on the fourth rotating element 4;
the shifting elements can be selectively operated, so that eight forward gears and two reverse gears can be achieved by means of different transmission ratios between the first rotating element 1 and the second rotating element 2, each gear only requiring two shifting elements to be closed.
In some embodiments, all of the planet rows comprise a sun gear, planet gears, and an annulus gear; the first, second, third and fourth planetary rows P1, P2, P3 and P4 are simple negative planetary rows and the main gear ratios are all negative.
The eight forward gears and the two reverse gears are realized in the following modes: the second reverse gear is implemented by the third and sixth engaging elements 10 and 13 which are closed, the first reverse gear is implemented by the fourth and sixth engaging elements 11 and 13 which are closed, the first forward gear is implemented by the first and sixth engaging elements 8 and 13 which are closed, the second forward gear is implemented by the first and fifth engaging elements 8 and 12 which are closed, the third forward gear is implemented by the first and fourth engaging elements 8 and 11 which are closed, the fourth forward gear is implemented by the first and third engaging elements 8 and 10 which are closed, the fifth forward gear is implemented by the first and second engaging elements 8 and 9 which are closed, the sixth forward gear is implemented by the second and third engaging elements 9 and 10 which are closed, the seventh forward gear is implemented by the second and fourth engaging elements 9 and 11 which are closed, and the eighth forward gear is implemented by the second and fifth engaging elements 9 and 12 which are closed.
The invention adopts 4 minus planetary rows, 7 rotating elements, 6 shifting elements (comprising 2 clutches and 4 brakes), 4 brakes are nested in the planetary rows, 2 clutches are positioned at the front part of the transmission, the structural layout is more compact, and the oil supply is very convenient.
According to the invention, each gear is closed by 2 gear shifting elements, 8 forward gears and 2 reverse gears can be realized, the number of gears is more, and the transmission ratio range is wider. With the increase of the gear number, a wider speed ratio range and a more uniform transmission step ratio can be obtained.
Table 1 shows the shift logic of the present solution and the possible gear ratios of the gears, where the adjacent gears are simply shifted, ● indicates the shifting element is closed, and x indicates the shifting element is open. 1 great 1-gear speed ratio can be realized, and the low-speed running operation of the commercial vehicle is facilitated.
TABLE 1 Shift logic and one possible Gear ratio
Gear position C1 C2 B1 B2 B3 B4 Transmission ratio
Reverse 2 gear × × ● × × ● -2.717
Reverse 1 gear × × × ● × ● -4.483
1 gear ● × × × × ● 3.1
2 keeps off ● × × × ● × 1.811
3 grade ● × × ● × × 1.406
4-gear ● × ● × × × 1.228
5-gear ● ● × × × × 1
6-gear × ● ● × × × 0.793
7 shift × ● × ● × × 0.711
8 keep off × ● × × ● × 0.614
According to the invention, through 6 gear shifting elements, wherein 2 clutches and 4 brakes are combined and closed, the switching of different gear modes can be effectively realized, and 8 forward gears and 2 reverse gears with different transmission ratios can be effectively realized in the process from an input rotating element to an output rotating element. The main function of the shifting element is to realize mode switching better, a proper wet or dry friction type shifting element can be selected in a targeted manner in the design process of an actual product, and for the selection of specific specifications of different shifting elements, the limit load born by the shifting element in the process of matching different power transmission lines is matched so as to ensure the product reliability of the automatic transmission.
The invention adopts the structural characteristics of few clutches and multiple brakes, and the planet row is nested in the brakes for arrangement, and utilizes 6 gear shifting elements, namely 2 clutches and 4 brakes to realize the mode switching of 8 forward gears and 2 reverse gears, so that the gear shifting elements are easy to assemble, and a required hydraulic system can be directly supplied from a shell, thereby simplifying the structural design size of the planetary gear transmission.
In the present invention, the terms "first", "second", "third" and "fourth" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance. The term "plurality" means two or more unless expressly limited otherwise.
The above applications are only some embodiments of the present application. It will be apparent to those skilled in the art that various changes and modifications can be made without departing from the inventive concept herein, and it is intended to cover all such modifications and variations as fall within the scope of the invention.

Claims (3)

1. An eight-front-two-reverse planetary automatic transmission, comprising:
the box body is a fixed component and is used for mounting the transmission, and the brake is connected with the box body to realize the opening and closing of the brake so as to realize the switching of the gear shifting modes;
the seven rotating elements are respectively a first rotating element (1), a second rotating element (2), a third rotating element (3), a fourth rotating element (4), a fifth rotating element (5), a sixth rotating element (6) and a seventh rotating element (7); the first rotating element (1) is an input shaft, and the second rotating element (2) is an output shaft and is used for power input and power output respectively; the third rotating element (3), the fourth rotating element (4), the fifth rotating element (5), the sixth rotating element (6) and the seventh rotating element (7) are used for power transmission among the planetary rows;
a shift element including four brakes, a third engagement element (10), a fourth engagement element (11), a fifth engagement element (12), and a sixth engagement element (13), respectively; two clutches, respectively a first engaging element (8) and a second engaging element (9);
four planetary rows, respectively a first planetary row P1, a second planetary row P2, a third planetary row P3 and a fourth planetary row P4;
wherein the first engagement element (8) connects the first and third rotational elements (1, 3); the second engagement element (9) connects the first rotary element (1) and the fourth rotary element (4);
the third engaging element (10) connects the seventh rotating element (7) and the case, the fourth engaging element (11) connects the sixth rotating element (6) and the case, the fifth engaging element (12) connects the fifth rotating element (5) and the case, and the sixth engaging element (13) connects the fourth rotating element (4) and the case; the third engagement element (10), the fourth engagement element (11), the fifth engagement element (12) and the sixth engagement element (13) are all abutted against the inner wall of the case body, the third engagement element (10) is nested outside the ring gear of the first planet row P1, the fourth engagement element (11) is nested outside the ring gear of the second planet row P2, the fifth engagement element (12) is nested outside the ring gear of the third planet row P3, and the sixth engagement element (13) is nested outside the ring gear of the fourth planet row P4;
the sun gear of the first planetary row P1 is located on the first rotating element (1), the planet carrier is located on the sixth rotating element (6), and the ring gear is located on the seventh rotating element (7); the sun gear of the second planetary row P2 is located on the first rotating element (1), the planet carrier is located on the fifth rotating element (5), and the ring gear is located on the sixth rotating element (6); the sun gear of the third planetary row P3 is located on the third rotating element (3), the planet carrier is located on the fourth rotating element (4), and the ring gear is located on the fifth rotating element (5); the sun gear of the fourth planetary row P4 is located on the third rotating element (3), the planet carrier is located on the second rotating element (2), and the ring gear is located on the fourth rotating element (4);
the shifting elements can be selectively operated, so that eight forward gears and two reverse gears can be realized by different transmission ratios between the first rotating element (1) and the second rotating element (2), and each gear only needs to be closed by two shifting elements.
2. An eight-front-two-reverse planetary automatic transmission according to claim 1, wherein all the planetary rows include a sun gear, a planetary gear, and a ring gear; the first, second, third and fourth planetary rows P1, P2, P3, P4 are simple negative planetary rows and the main gear ratios are all negative.
3. An eight-first-two-reverse planetary gear automatic transmission according to claim 1 or 2, characterized in that a second reverse gear is realized by the third and sixth engagement elements (10, 13) being closed, a first reverse gear is realized by the fourth and sixth engagement elements (11, 13) being closed, a first forward gear is realized by the first and sixth engagement elements (8, 13) being closed, a second forward gear is realized by the first and fifth engagement elements (8, 12) being closed, a third forward gear is realized by the first and fourth engagement elements (8, 11) being closed, a fourth forward gear is realized by the first and third engagement elements (8, 10) being closed, a fifth forward gear is realized by the first and second engagement elements (8, 9) being closed, sixth forward gear is realized by the closed second engagement element (9) and the closed third engagement element (10), seventh forward gear is realized by the closed second engagement element (9) and the closed fourth engagement element (11), and eighth forward gear is realized by the closed second engagement element (9) and the closed fifth engagement element (12).
CN202110456753.3A 2021-04-27 2021-04-27 Eight-front two-reverse planetary gear automatic transmission Pending CN112984060A (en)

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Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041509A1 (en) * 2004-08-27 2006-03-16 Zf Friedrichshafen Ag Automobile multi-speed gearbox, with eight forward and two reverse gears, has three planet wheel sets and six switch units between the drive input and output shafts
CN103758977A (en) * 2014-01-09 2014-04-30 湖北航天技术研究院特种车辆技术中心 Eight-gear hydraulic automatic speed changer
CN104565238A (en) * 2014-12-26 2015-04-29 燕山大学 8-gear automatic transmission
CN104565240A (en) * 2014-12-26 2015-04-29 燕山大学 Transmission with wider speed range
CN104896038A (en) * 2015-06-19 2015-09-09 陕西法士特齿轮有限责任公司 Multi-gear transmission and planetary gear train thereof
CN105003633A (en) * 2015-07-17 2015-10-28 中国地质大学（武汉） Improved eight-gear transmission
CN106402293A (en) * 2016-09-30 2017-02-15 中国北方车辆研究所 Eight-gear automatic planetary transmission
CN106523628A (en) * 2016-12-16 2017-03-22 贵州凯星液力传动机械有限公司 Eight-gear planetary automatic transmission
CN110439975A (en) * 2019-07-15 2019-11-12 中国北方车辆研究所 A kind of eight-gear planetary automatic speed changer
CN111536211A (en) * 2020-06-23 2020-08-14 北京航空航天大学 Multi-gear planetary gear speed change device
CN111853182A (en) * 2020-06-30 2020-10-30 宝能(西安)汽车研究院有限公司 Transmission, power drive system and vehicle

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004041509A1 (en) * 2004-08-27 2006-03-16 Zf Friedrichshafen Ag Automobile multi-speed gearbox, with eight forward and two reverse gears, has three planet wheel sets and six switch units between the drive input and output shafts
CN103758977A (en) * 2014-01-09 2014-04-30 湖北航天技术研究院特种车辆技术中心 Eight-gear hydraulic automatic speed changer
CN104565238A (en) * 2014-12-26 2015-04-29 燕山大学 8-gear automatic transmission
CN104565240A (en) * 2014-12-26 2015-04-29 燕山大学 Transmission with wider speed range
CN104896038A (en) * 2015-06-19 2015-09-09 陕西法士特齿轮有限责任公司 Multi-gear transmission and planetary gear train thereof
CN105003633A (en) * 2015-07-17 2015-10-28 中国地质大学（武汉） Improved eight-gear transmission
CN106402293A (en) * 2016-09-30 2017-02-15 中国北方车辆研究所 Eight-gear automatic planetary transmission
CN106523628A (en) * 2016-12-16 2017-03-22 贵州凯星液力传动机械有限公司 Eight-gear planetary automatic transmission
CN110439975A (en) * 2019-07-15 2019-11-12 中国北方车辆研究所 A kind of eight-gear planetary automatic speed changer
CN111536211A (en) * 2020-06-23 2020-08-14 北京航空航天大学 Multi-gear planetary gear speed change device
CN111853182A (en) * 2020-06-30 2020-10-30 宝能(西安)汽车研究院有限公司 Transmission, power drive system and vehicle

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Application publication date: 20210618