CN106884936B - Three-planet-row six-speed automatic transmission and automobile - Google Patents
Three-planet-row six-speed automatic transmission and automobile Download PDFInfo
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- CN106884936B CN106884936B CN201710231750.3A CN201710231750A CN106884936B CN 106884936 B CN106884936 B CN 106884936B CN 201710231750 A CN201710231750 A CN 201710231750A CN 106884936 B CN106884936 B CN 106884936B
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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
- F16H3/64—Gearings having three or more central gears composed of a number of gear trains, the drive always passing through all the trains, each train having not more than one connection for driving another train
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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
- F16H2200/0052—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising six 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
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three 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
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
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Abstract
The invention relates to the field of automobiles, and discloses a three-planet-row six-speed automatic transmission and an automobile, which comprise a first planet row, a second planet row and a third planet row; the first planet row comprises a first gear ring, a first inner planet wheel set, a first outer planet wheel set, a first sun gear and a first planet carrier, wherein the first inner planet wheel set and the first outer planet wheel set are meshed with each other; the second planet row comprises a second gear ring, a second planet wheel set, a second sun gear and a second planet carrier; the third planet row comprises a third gear ring, a third planet wheel set, a third sun gear and a third planet carrier; the first gear ring, the second gear ring and the third sun gear are sequentially and fixedly connected into a whole, and the first gear ring is connected to the transmission box body through a first braking component; the first planet carrier is connected with the second planet carrier through a first torque transmission member; the second planet carrier is connected with the third planet carrier through a second torque transmission member; the third carrier is connected with the second sun gear by a third torque transmitting member and the third carrier is connected to the transmission housing by a second brake member.
Description
Technical Field
The invention relates to the technical field of automobiles, in particular to a three-planetary-row six-speed automatic transmission and an automobile.
Background
The mechanism for effecting a change in speed in an electrically controlled hydrostatic transmission drive train typically includes a plurality of planetary rows. The power of the engine is transmitted into the planetary gear speed change mechanism through the hydraulic torque converter to be changed in speed and then output. The volume, weight, efficiency and load carrying capacity of an automatic transmission are directly related to the planetary gear mechanism. The more gears of the automatic transmission drive train, the lower the fuel consumption of the automobile and the better the economy, but as the number of gears increases, the number of planetary rows and the number of operating clutches and brakes also increase, and the design of meeting the theoretical step ratio is more difficult to realize. People are always seeking to combine a planetary gear speed change mechanism which meets the requirements of automobile performance, has a compact structure, higher strength and better efficiency by using fewer planetary rows, clutches and brakes.
The 6-speed automatic transmission planetary gear mechanism currently used in the passenger car market mainly comprises a Lepelelie scheme used by Esin, ZF and Jili (DSI), a scheme used by modern A6MF and A6L F series, a scheme used by universal 6T series, and A6-speed scheme used by Mazda creative blue sky.
The Lepelelayje solution is implemented by adding a row of planetary rows on the basis of a Ravignean 4-speed automatic transmission without a direct gear, the general and modern solutions are implemented by three planetary rows, the difference is that the positions of clutches are different, a planetary row in the modern mass production series A6MF and A6L F uses a double planetary gear set structure, compared with a single planetary gear set structure, under the same other conditions, a gear ring can move reversely, the modern and general solutions are implemented by 2 clutches and 3 brakes, the number of the brakes is more than that of the clutches, the brakes are finally connected to a box body through friction steel sheet teeth, more brakes increase the processing and manufacturing difficulty of the box body, and because the box body material is generally an aluminum alloy, more brakes undoubtedly cause difficulty in realizing light-weight design while ensuring strength, and the 6-speed solution used in the Chilan day originates from the U.S. A LL ISON solution used for matching a large diesel engine gear, and directly appears on a four-gear matching gasoline engine.
Disclosure of Invention
The invention aims to provide a three-planet-row six-speed automatic transmission which can realize six forward gears and one reverse gear, has a more compact whole structure and is lower in the difficulty in processing and manufacturing a box body. In addition, the invention also provides an automobile using the three-planetary-row six-speed automatic transmission.
In order to achieve the above object, the present invention provides a three planetary-row six-speed automatic transmission, comprising: a first planet row, a second planet row and a third planet row; the first planet row comprises a first gear ring, a first inner planet wheel set, a first outer planet wheel set, a first sun gear and a first planet carrier, wherein the first inner planet wheel set and the first outer planet wheel set are meshed with each other; the second planet row comprises a second gear ring, a second planet wheel set, a second sun gear and a second planet carrier; the third planet row comprises a third gear ring, a third planet wheel set, a third sun gear and a third planet carrier;
the first gear ring, the second gear ring and the third sun gear are sequentially and fixedly connected into a whole, and the first gear ring is connected to a transmission box body through a first braking component;
the first carrier is connected with the second carrier by a first torque transfer member; the second carrier is connected with the third carrier through a second torque transfer member; the third planet carrier is connected with the second sun gear through a third torque transmitting member and the third planet carrier is connected with a transmission housing through a second brake member;
the second sun gear is connected with the input end of the speed changer, and the third gear ring is connected with the output end of the speed changer.
Preferably, the first sun gear is fixedly connected with the transmission case.
Preferably, the input end of the speed changer and the output end of the speed changer are arranged on the same side.
Preferably, the first, second and third torque transmitting members are clutches.
Preferably, the clutch is a multi-plate wet clutch or a dog clutch.
Preferably, the first brake member and the second brake member are drum brakes or multi-plate wet brakes.
As a preferred scheme, the first planet carrier, the second planet carrier and the third planet carrier are all provided with a pin shaft, the first inner planet wheel set and the first outer planet wheel set are mounted on the pin shaft of the first planet carrier through bearings, the second planet wheel set is mounted on the pin shaft of the second planet carrier through bearings, and the third planet wheel set is mounted on the pin shaft of the third planet carrier through bearings.
In order to solve the same problem, the invention also provides a vehicle including the three-planetary-row six-speed automatic transmission of any one of the above aspects.
Compared with the prior art, the three-planetary-row six-speed automatic transmission and the automobile have the following advantages that:
1. the invention adopts three torque transmission components and two braking components to reasonably connect three planet rows, thereby realizing six forward gears and one reverse gear; the number of the braking components is less than that of the torque transmission components, and fewer braking components are adopted, so that the difficulty in processing and manufacturing the gearbox body of the transmission can be reduced, the lightweight of the gearbox body is facilitated, and the whole transmission is more compact; in addition, under the condition of meeting the same number of speed ratios, the utilization rate of each braking component can be obviously improved by the smaller number of the braking components, so that the whole transmission is more compact; more torque transmission components are adopted, so that the connection relation among the planet rows can be cut off under a specific gear, and the redundant planet rows do not participate in transmission, thereby reducing the oil mixing loss of the belt rows and improving the efficiency; the arrangement of more torque transmission members is not only beneficial to multi-speed expansion in a mode of adding a planet row or adding more control pieces, but also can realize nested design of the clutches if the torque transmission members are selected as the clutches when the specific structure design is realized, so that the structure of the whole transmission is more compact;
2. the first planet carrier, the second planet carrier and the third planet carrier are sequentially connected through the first torque transmission component and the second torque transmission component, so that the length of the whole transmission can be effectively reduced, and the whole transmission is more compact in structure and lighter in weight.
Drawings
FIG. 1 is a schematic illustration of a coupling arrangement for a three planetary-row six-speed automatic transmission according to an embodiment of the present invention;
FIG. 2 is a schematic illustration of a 1 speed drive path for a three planetary-row six speed automatic transmission according to an embodiment of the present invention;
FIG. 3 is a schematic 2-speed drive line for a three planetary-row six-speed automatic transmission provided by an embodiment of the present invention;
FIG. 4 is a schematic 3-speed drive-line for a three planetary-row six-speed automatic transmission provided by an embodiment of the present invention;
FIG. 5 is a schematic 4-speed drive line for a three planetary-row six-speed automatic transmission provided by an embodiment of the present invention;
FIG. 6 is a schematic illustration of a 5 speed transmission path for a three planetary-row six speed automatic transmission according to an embodiment of the present invention;
FIG. 7 is a schematic illustration of a6 speed drive path for a three planetary-row six speed automatic transmission according to an embodiment of the present invention;
FIG. 8 is a schematic representation of an R-range transmission path for a three planetary-row six-speed automatic transmission provided in accordance with an embodiment of the present invention;
wherein, 1, a first planet row; 11. a first ring gear; 12. a first outer planetary gear set; 13. a first inner planetary gear set; 14. a first carrier; 15. a first sun gear; 2. a second planet row; 21. a second ring gear; 22. a second planet carrier; 23. a second planetary gear set; 24. a second sun gear; 3. a third planet row; 31. a third ring gear; 32. a third planetary gear set; 33. a third carrier; 34. a third sun gear; 4. a transmission case; b1, a first brake member; b2, a second brake member; c1, a first torque transmitting member; c2, a second torque transmitting member; c3, a third torque transmitting member.
Detailed Description
The following detailed description of embodiments of the present invention is provided in connection with the accompanying drawings and examples. The following examples are intended to illustrate the invention but are not intended to limit the scope of the invention.
As shown in fig. 1, a preferred embodiment of the present invention, a three planetary-row six-speed automatic transmission, includes: a first planet row 1, a second planet row 2 and a third planet row 3; the first planet row 1 comprises a first ring gear 11, a first inner planet gear set 13 and a first outer planet gear set 12 which are meshed with each other, a first sun gear 15 and a first planet carrier 14; the second planet row 2 comprises a second ring gear 21, a second planet gear set 23, a second sun gear 24 and a second planet carrier 22; the third planetary row 3 includes a third ring gear 31, a third planetary set 32, a third sun gear 34, and a third carrier 33; the second planetary row 2 is located between the first planetary row 1 and the third planetary row 3. Specifically, the first inner planetary gear set 13 is externally meshed with the first sun gear 15, the first outer planetary gear set 12 is internally meshed with the first ring gear 11, the first inner planetary gear set 13 is externally meshed with the first outer planetary gear set 12, and the first inner planetary gear set 13 and the first outer planetary gear set 12 are both mounted on the first planet carrier 14; the second planetary gear set 23 is externally meshed with the second sun gear 24 and internally meshed with the second ring gear 21, and the second planetary gear set 23 is mounted on the second planet carrier 22; the third planetary gear set 32 is externally meshed with the third sun gear 34 and internally meshed with the third ring gear 31, and the third planetary gear set 32 is mounted on the third carrier 33.
The automatic transmission further includes a transmission housing 4, a first brake member B1, a second brake member B2, a first torque transmitting member C1, a second torque transmitting member C2, and a third torque transmitting member C3; the first gear ring 11, the second gear ring 21 and the third sun gear 34 are sequentially and fixedly connected into a whole, for example, connected into a whole by a fixed connection manner such as spline connection or welding, and the first gear ring 11 is connected to the transmission case 4 by a first brake member B1; the first carrier 14 is connected with the second carrier 22 through a first torque transmitting member C1; the second carrier 22 is connected to the third carrier 33 through a second torque-transmitting member C2; the third carrier 33 is connected with the second sun gear 24 through a third torque transmitting member C3, and the third carrier 33 is connected to the transmission housing 4 through a second brake member B2; the first sun gear 15 and the transmission case 4 are fixedly connected into a whole; the second sun gear 24 is connected to the transmission input, and the third ring gear 31 is connected to the transmission output.
Therefore, the six-speed automatic transmission with three planetary rows according to the embodiment can realize six forward gears and one reverse gear, and the specific operating logic is shown in table 1, wherein K is a characteristic parameter of a planetary row, the numerical value is equal to the ratio of the tooth number of the ring gear to the tooth number of the sun gear, K1 corresponds to the characteristic parameter of the first planetary row 1, K2 corresponds to the characteristic parameter of the second planetary row 2, and K3 corresponds to the characteristic parameter of the third planetary row 3.
The specific gear transmission route is as follows:
(1) in gear 1, the second torque transfer member C2 and the second brake member B2 are closed, speed ratio i1 is K2 × K3. with the second brake member B2 braking, the third carrier 33 speed is zero, and the second torque transfer member C2 is closed so that the second carrier 22 speed is equal to the third carrier 33 speed, so the gear 1 transmission path is input by the second sun gear 24 → the second planetary gear set 23 → the second ring gear 21 → the third sun gear 34 → the third planetary gear set 32 → the third ring gear 31 for output, as shown in fig. 2.
(2) In the 2-gear stage, the second torque transmission member C2 and the first brake member B1 are closed, the speed ratio is i2 ═ K3 × (1+ K2)/(1+ K3), the first brake member B1 brakes, and the rotation speeds of the first ring gear 11, the second ring gear 21 and the third sun gear 34 are zero, so that the transmission route of the 2-gear stage is that the second sun gear 24 is input → the second planetary gear set 23 → the second planetary gear set 22 → the second torque transmission member C2 is closed → the third planetary gear set 33 → the third planetary gear set 32 → the third ring gear 31 is output, specifically, as shown in fig. 3, in the 2-gear stage, the first torque transmission member C1 is disconnected, and the rotation speed of the second ring gear 21 is zero, so that the first planetary gear stage 1 does not participate in transmission, and the churning oil loss is reduced, and the transmission efficiency is improved.
(3) In 3-gear, the first and second torque transmitting members C1 and C2 are closed, the speed ratio is i3 ═ K3 × (K1+ K2)/(K1 × K3+1) in which the first and second torque transmitting members C1 and C2 work, the second sun gear 24 input is transmitted to the second carrier 22 via the second planetary gear set 23, the three transmission paths are divided into ①, which is input by the second sun gear 24 → the second planetary gear set 23 → the second carrier 22 → the second torque transmitting member C2 closed → the third carrier 33 → the third planetary gear set 32 → the third ring gear 31 output, ②, which is input by the second sun gear 24 → the second planetary gear set 23 → the second carrier 22 → the second torque transmitting member C1 closed → the first carrier 14 → the first inner planetary gear set 13 and the first outer planetary gear set 12 → the first ring gear 21 → the third sun gear set 32 → the third ring gear set 32 → the third planetary gear set 31 → the third planetary gear set 32 → the third ring gear set 31 → the third planetary gear set 32 → the third planetary gear set 31 is specifically shown in fig. 3.
(4)4, gear 4: the second and third torque transmitting members C2 and C3 are closed, speed ratio i4 is 1, direct gear. Since the second torque transmitting member C2 and the third torque transmitting member C3 are simultaneously closed, the second planetary row 2 and the third planetary row 3 are directly output from the third ring gear 31 as a whole at the same speed, thereby realizing a direct gear, as shown in fig. 5.
(5) In gear 5, the first torque transfer member C1 and the third torque transfer member C3 are closed, the speed ratio is i5 ═ K1 × K3+ K2 × K3)/(K1 × K3+ K2 × K3+ K2+1), three transmission routes are split in this gear, ① is closed by the second sun gear 24 input → the third torque transfer member C3 is closed → the third carrier 33 → the third planetary gear set 32 → the third ring gear 31 is output, ② is input by the second sun gear 24 → the second planetary gear set 23 → the second ring gear 21 → the third sun gear 34 → the third planetary gear set 32 → the third ring gear 31 is output, ③ is input → the second sun gear 24 → the second planetary gear set 23 → the second carrier 22 → the first torque transfer member C1 is closed → the first carrier 14 → the first inner planetary gear set 13 and the first outer planetary gear set 12 → the first ring gear set 11 → the second ring gear 21 → the second planetary gear set 22 → the third ring gear set → the third planetary gear set 32, as shown in detail in fig. 6.
(6)6, gear 6: the first brake member B1 and the third torque transmitting member C3 are closed at a speed ratio of i6 — K3/(K3+ 1). The first brake component B1 brakes, and the rotation speed of the first ring gear 11, the second ring gear 21 and the third sun gear 34 is zero, so the transmission route is: input from the second sun gear 24 → closure of the third torque-transmitting member C3 → the third carrier 33 → the third set of planet gears 32 → the third ring gear 31 for output, as particularly shown in fig. 7. Under the condition of 6 gears, the first torque transmission component C1 is disconnected, the rotating speed of the second gear ring 21 is zero, so that the first planet row 1 does not participate in transmission, the oil stirring loss is reduced, and the transmission efficiency is improved.
(7) R-range, reverse gear is achieved when the second brake member B2 is closed with the first torque transfer member C1, the reverse gear ratio is-K3 × (K1+ K2)/(K1-1), in which gear the second brake member B2 brakes, the third carrier 33 rotates at zero speed, the first torque transfer member C1 engages, and the transmission route of R-range is divided into two, ① input by the second sun gear 24 → the second planetary gear set 23 → the second ring gear 21 → the third sun gear 34 → the third planetary gear set 32 → the third ring gear 31 outputs, ② input by the second sun gear 24 → the second planetary gear set 23 → the second carrier 22 → the first torque transfer member C1 is closed → the first carrier 14 → the first inner planetary gear set 13 and the first outer planetary gear set 12 → the first ring gear 11 → the second ring gear 21 → the third sun gear 34 → the third planetary gear set 32 → the third ring gear 31 outputs, as shown in particular in fig. 8.
In the process of executing each gear, the rotating speed of the first sun gear 15 needs to be zero, if the mode that the brake is used for connecting the first sun gear 15 with the transmission box body 4 is adopted, the brake keeps a closed state in the process of executing each gear, then, in the process of shifting, the brake can certainly cause direct impact on the transmission box body 4, the load bearing condition of the transmission box body 4 is influenced, so the problem that the brake directly impacts the transmission box body 4 in the process of shifting is avoided, and the load bearing condition of the transmission box body 4 is further improved.
In this embodiment, the derailleur input sets up with the derailleur output homonymy to make derailleur overall structure arrange more rationally, be convenient for the installation of the other parts of car. Of course, the transmission input and the transmission output may be arranged on opposite sides.
The first, second and third torque transmitting members C1, C2, C3 of the present embodiment are preferably clutches, such that the clutches can be nested for a particular design of construction, thereby making the planetary gear set of the transmission more compact. The clutch may be a multi-plate wet clutch or a dog clutch: the multi-plate wet clutch has the advantages of oil film protection, smooth and soft power transmission, long service life and the like; the dog clutch can transmit larger torque, has the characteristics of simple structure and small size, and can enable the whole transmission to be more compact in structure by using the dog clutch. In the present embodiment, the first brake member B1 and the second brake member B2 are preferably multi-disc wet brakes, which have the advantages of large braking torque, stable operation performance, long service life, strong fading and pollution resistance, maintenance-free performance, etc., of course, the first brake member B1 and the second brake member B2 may also be drum brakes, which have good self-braking effect, higher absolute braking force, and lower cost.
The first planet carrier 14, the second planet carrier 22 and the third planet carrier 33 are all provided with pin shafts, the first inner planet wheel set 13 and the first outer planet wheel set 12 are arranged on the pin shafts of the first planet carrier 14 through bearings, the second planet wheel set 23 is arranged on the pin shafts of the second planet carrier 22 through bearings, and the third planet wheel set 32 is arranged on the pin shafts of the third planet carrier 33 through bearings, so that the first inner planet wheel set 13, the first outer planet wheel set 12, the second planet wheel set 23 and the third planet wheel set 32 can freely rotate on the respective planet carrier and can also rotate along with the respective planet carrier. The bearing may be a rolling bearing or a sliding bearing.
In order to solve the same problem, the present invention also provides an automobile including the three-planetary-row six-speed automatic transmission in the above embodiment.
In conclusion, the three planetary rows are reasonably arranged and reasonably connected by adopting the three torque transmission members and the two braking members, so that six forward gears and one reverse gear are realized; the number of the braking components in the invention is less than that of the torque transmission components, so that the difficulty in processing and manufacturing the internal teeth on the transmission case body 4 can be reduced by adopting fewer braking components, the light weight of the transmission case body 4 is facilitated, and the whole transmission is more compact; in addition, the utilization rate of each braking component can be improved by using fewer braking components, so that the whole transmission is more compact; the use of more torque transmission components is beneficial to cutting off the connection relation among the planet rows under a specific gear, so that the redundant planet rows do not participate in transmission, the oil mixing loss of the belt rows is reduced, and the efficiency is improved; in addition, more torque transmitting members facilitate later multi-speed expansion by adding planetary rows or adding more manipulators; in addition, the direct fixed connection of the first sun gear 15 and the transmission case 4 can avoid direct impact on the transmission case 4 caused by adopting a brake in the gear shifting process, so that the load condition of the transmission case 4 is improved.
The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and substitutions can be made without departing from the technical principle of the present invention, and these modifications and substitutions should also be regarded as the protection scope of the present invention.
Claims (6)
1. A three planetary row six speed automatic transmission comprising: a first planet row, a second planet row and a third planet row; the first planet row comprises a first gear ring, a first inner planet wheel set, a first outer planet wheel set, a first sun gear and a first planet carrier, wherein the first inner planet wheel set and the first outer planet wheel set are meshed with each other; the second planet row comprises a second gear ring, a second planet wheel set, a second sun gear and a second planet carrier; the third planet row comprises a third gear ring, a third planet wheel set, a third sun gear and a third planet carrier;
the first gear ring, the second gear ring and the third sun gear are sequentially and fixedly connected into a whole, and the first gear ring is connected to a transmission box body through a first braking component;
the first carrier is connected with the second carrier by a first torque transfer member; the second carrier is connected with the third carrier through a second torque transfer member; the third planet carrier is connected with the second sun gear through a third torque transmitting member and the third planet carrier is connected with a transmission housing through a second brake member;
the second sun gear is connected with the input end of the transmission, and the third gear ring is connected with the output end of the transmission; the first sun gear is fixedly connected with the transmission box body;
the first, second and third torque transmitting members are clutches.
2. A three planetary row six speed automatic transmission as claimed in claim 1 wherein the transmission input is disposed on the same side as the transmission output.
3. A three planetary row six speed automatic transmission as claimed in claim 1 wherein the clutch is a multiplate wet clutch or a dog clutch.
4. A three planetary row six speed automatic transmission as claimed in claim 1, wherein the first and second brake members are drum brakes or multi-plate wet brakes.
5. The six-speed automatic transmission according to claim 1, wherein the first carrier, the second carrier, and the third carrier each have a pin, the first inner planetary gear set and the first outer planetary gear set are mounted on the pins of the first carrier by bearings, the second planetary gear set is mounted on the pins of the second carrier by bearings, and the third planetary gear set is mounted on the pins of the third carrier by bearings.
6. An automobile characterized by comprising a three-planetary-row six-speed automatic transmission according to any one of claims 1 to 5.
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| CN201710231750.3A CN106884936B (en) | 2017-04-11 | 2017-04-11 | Three-planet-row six-speed automatic transmission and automobile |
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Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN109296714B (en) * | 2017-07-25 | 2020-08-28 | 广州汽车集团股份有限公司 | Three-planet-row six-speed automatic transmission and automobile |
| CN107524767B (en) * | 2017-09-18 | 2019-09-10 | 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 |
| CN108194586B (en) * | 2017-12-29 | 2022-06-21 | 广州汽车集团股份有限公司 | Three-planet-row automatic transmission and vehicle |
| CN113864404A (en) * | 2020-06-30 | 2021-12-31 | 中国航发商用航空发动机有限责任公司 | Planetary gear box and star gear box |
| CN114508577A (en) * | 2022-02-23 | 2022-05-17 | 浙江吉利控股集团有限公司 | Double-planetary-row transmission and vehicle |
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| CN104696452A (en) * | 2013-12-09 | 2015-06-10 | 福特全球技术公司 | Multi-speed transmission |
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| US8066609B2 (en) * | 2008-05-02 | 2011-11-29 | Chrysler Group Llc | Electric variable transmission for hybrid electric vehicles with three forward modes, one reverse mode, and five fixed gears |
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|---|---|---|---|---|
| DE2141563A1 (en) * | 1971-08-19 | 1973-02-22 | Zahnradfabrik Friedrichshafen | ROTATING GEAR TRANSMISSION, IN PARTICULAR FOR MOTOR VEHICLES |
| DE102010063496A1 (en) * | 2010-12-20 | 2012-06-21 | Zf Friedrichshafen Ag | Multi-speed transmission in planetary construction |
| CN104696452A (en) * | 2013-12-09 | 2015-06-10 | 福特全球技术公司 | Multi-speed transmission |
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| Publication number | Publication date |
|---|---|
| CN106884936A (en) | 2017-06-23 |
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