CN116292783A - Eight-gear automatic transmission with stable transmission - Google Patents

Eight-gear automatic transmission with stable transmission Download PDF

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Publication number
CN116292783A
CN116292783A CN202310331941.2A CN202310331941A CN116292783A CN 116292783 A CN116292783 A CN 116292783A CN 202310331941 A CN202310331941 A CN 202310331941A CN 116292783 A CN116292783 A CN 116292783A
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CN
China
Prior art keywords
planetary gear
train unit
gear train
clutch
brake
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Pending
Application number
CN202310331941.2A
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Chinese (zh)
Inventor
杨文剑
肖鑫栋
丁华锋
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China University of Geosciences
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China University of Geosciences
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Priority to CN202310331941.2A priority Critical patent/CN116292783A/en
Publication of CN116292783A publication Critical patent/CN116292783A/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
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • 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
    • F16H57/082—Planet carriers
    • 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
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/04—Smoothing ratio shift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds

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

Abstract

The invention provides an eight-gear automatic transmission with stable transmission. The planetary gear system comprises a transmission shell, an input shaft, an output shaft, an 11-rod 2-degree-of-freedom separable planetary gear system and a torque transmission device, wherein the input shaft, the output shaft and the 11-rod 2-degree-of-freedom separable planetary gear system are arranged in the transmission shell, and the 11-rod 2-degree-of-freedom separable planetary gear system comprises four basic planetary gear system units which are sequentially arranged along the direction from the input shaft to the output shaft; the clutches in the torque transfer device are connected to the input shaft and the planetary gear set, the brakes in the torque transfer device are connected to the transmission housing and the planetary gear set, three combinations of each clutch and each brake are selectively engaged to establish eight forward speed ratios and one reverse speed ratio, 5,3,2,1.4,1,0.82,0.71,0.6, -4, respectively, between the input shaft and the output shaft. The automatic transmission is simple in structure, stable in step ratio between gears, smooth in gear shifting, high in transmission efficiency, simple to control and beneficial to reducing the size, weight and manufacturing cost of the automatic transmission.

Description

Eight-gear automatic transmission with stable transmission
Technical Field
The invention belongs to the technical field of vehicle transmission, and particularly relates to an eight-gear automatic transmission with stable transmission.
Background
Automatic transmissions are one of the core devices of automobiles, and are the focus of competition in countries around the world. The mechanism is a carrier for realizing the motion function of the automatic transmission, and the novel mechanism is designed and invented, so that the mechanism is a source spring and a foundation for developing the novel automatic transmission. The 8-gear automatic transmission mechanism mainly comprises a planetary gear train, a clutch and a brake. In the prior art, the transmission has better adaptability to the running road conditions, and can shift gears to run according to different resistances, so that the power output of the power device can be matched with the running road conditions to a certain extent, and the application is wider. The existing speed changer is generally provided with a plurality of groups of gear pairs which are meshed normally, the number of the gear pairs is the same as that of gears of the speed changer, and gear shifting is carried out through different control combinations of clutches and brakes. In patent CN103758977B an 8-speed automatic transmission is disclosed, in the mechanism they exhibit, 7 control elements are arranged, which increases the bulk of the whole automatic transmission. And the step between gear 1 and gear 2 shown therein is relatively large, with a large shift shock. The step ratio between the speed changer gears is reasonable, the gear shifting is smoother, and the oil consumption is relatively reduced.
Disclosure of Invention
The invention aims to overcome the defects in the prior art and provide the eight-gear automatic transmission with stable transmission.
In order to achieve the above purpose, the present invention adopts the following technical scheme:
the eight-gear automatic transmission with stable transmission comprises a transmission shell; the planetary gear system comprises a transmission shell, an input shaft, an output shaft and a torque transmission device, and further comprises an 11-rod 2-degree-of-freedom separable planetary gear system, wherein the 11-rod 2-degree-of-freedom separable planetary gear system comprises four basic planetary gear system units which are sequentially arranged along the direction from the input shaft to the output shaft, namely a first basic planetary gear system unit, a second basic planetary gear system unit, a third basic planetary gear system unit and a fourth basic planetary gear system unit, and each basic planetary gear system unit comprises a gear ring, a planetary gear, a planet carrier and a sun gear; the planet carrier of the first basic planetary gear train unit is fixedly connected with the planet carrier of the second basic planetary gear train unit; the gear ring of the first basic planetary gear train unit is fixedly connected with the sun gear of the second basic planetary gear train unit; the gear ring of the second basic planetary gear train unit is fixedly connected with the sun gear of the third basic planetary gear train unit; the planet carrier of the third basic planetary gear train unit is fixedly connected with the gear ring of the fourth basic planetary gear train unit; the gear ring of the third basic planetary gear train unit is fixedly connected with the planet carrier of the fourth basic planetary gear train unit, and the gear ring of the third basic planetary gear train unit and the planet carrier of the fourth basic planetary gear train unit are fixedly connected with the output shaft;
the torque transmitting device includes:
a first clutch connecting the input shaft to a ring gear of the first basic planetary gear train unit and a sun gear of the second basic planetary gear train unit, respectively;
a second clutch connecting the input shaft to the carrier of the first basic planetary gear train unit and the carrier of the second basic planetary gear train unit;
a third clutch connecting the input shaft to the carrier of the third basic planetary gear train unit and the ring gear of the fourth basic planetary gear train unit;
a first brake connected to a sun gear of the first basic planetary gear train unit;
a second brake connecting the carrier of the first basic planetary gear train unit and the carrier of the second basic planetary gear train unit;
a third brake connected to a sun gear of the fourth basic planetary gear train unit;
wherein three combinations of the first clutch, the second clutch, the third clutch, the first brake, the second brake, and the third brake are selectively engaged to establish eight forward gear ratios and one reverse gear ratio between the input shaft and the output shaft.
Further, the input shaft connects the sun gear of the second basic planetary gear train unit and the ring gear of the first basic planetary gear train unit through a third transmission member; the input shaft is connected with the planet carrier of the first basic planetary gear train unit and the planet carrier of the second basic planetary gear train unit through a second transmission member, and the gear ring of the second basic planetary gear train unit is connected with the sun gear of the third basic planetary gear train unit through a fourth transmission member; the input shaft is connected with the planet carrier of the third basic planetary gear train unit and the gear ring of the fourth basic planetary gear train unit through a fifth transmission member, the gear ring of the third basic planetary gear train unit and the planet carrier of the fourth basic planetary gear train unit are both connected with an output member, and the output member is connected with the output shaft.
Further, the first clutch is connected with the third transmission member, the second clutch is connected with the second transmission member, and the third clutch is connected with the fifth transmission member.
Further, the first brake is connected with the first transmission member; the second brakes are connected with the second transmission component; the third brake is connected with a sixth transmission member.
Further, eight gear ratios of the eight-gear automatic transmission are four reduction gears, one direct gear and three overdrive gears, respectively.
Further, a first gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the first brake, and the third brake;
establishing a second gear ratio between the input shaft and the output shaft by engaging the second clutch, the first brake, and the third brake;
establishing a three-speed gear ratio between the input shaft and the output shaft by engaging the first clutch, the second clutch, and the third brake;
establishing a fourth gear ratio between the input shaft and the output shaft by engaging the first clutch, the third clutch and the third brake;
establishing a five-speed gear ratio between the input shaft and the output shaft by engaging the first clutch, the second clutch, and the third clutch;
establishing a six-speed gear ratio between the input shaft and the output shaft by engaging the second clutch, the third clutch and the first brake;
establishing a seven speed gear ratio between the input shaft and the output shaft by engaging the first clutch, the third clutch and the first brake;
the first brake and the second brake are engaged by the third clutch to establish an eight speed gear ratio between the input shaft and the output shaft.
Further, a reverse gear ratio is established between the input shaft and the output shaft by engaging the first clutch, the second brake, and the third brake.
Further, the first clutch, the second clutch and the third clutch are all multi-plate wet clutches.
Further, the first brake, the second brake and the third brake are all multi-plate wet brakes.
Further, the first brake, the second brake, and the third brake are each fixed to the transmission housing.
Compared with the prior art, the technical scheme provided by the invention has the beneficial effects that:
(1) The eight-gear automatic transmission with stable transmission provided by the invention is composed of an 11-rod 2-degree-of-freedom planetary gear train, 3 clutches and 3 brakes, the structure is simple, the transmission ratio of each gear is reasonable, the step ratio between gears is within a reasonable range, the control elements are fewer, the transmission efficiency is high, the control of the clutches and the brakes is simple, and the mechanism has excellent comprehensive performance. The size, weight and manufacturing cost of the automatic transmission are advantageously reduced.
(2) The clutch and brake operating states are easy to control, and the single conversion principle is met, namely, when two adjacent gears are switched, only the operating state of one clutch or brake is required to be changed, so that the control difficulty of the transmission is reduced. The step ratio between each gear is stable, and gear shifting is smooth.
(3) According to the invention, only 6 control elements are used in the arrangement of the control elements, so that the dynamic property of the automobile is improved, the oil consumption is reduced, the speed ratio interval of adjacent gears is reduced, and the gear shifting is stable and quick in response; meanwhile, the smoothness of vehicle running is improved, meanwhile, the whole structure of the transmission is simplified, the weight is reduced, and energy conservation and consumption reduction are facilitated.
Drawings
FIG. 1 is a schematic illustration of a smooth-driving eight speed automatic transmission according to the present invention;
FIG. 2 is a logic diagram of the operation of an eight speed automatic transmission with smooth gear transmission according to the present invention.
In the figure: 1. a first basic planetary gear train unit; 11. a ring gear of the first basic planetary gear train unit; 12. a planetary gear of the first basic planetary gear train unit; 13. a carrier of the first basic planetary gear train unit; 14. a sun gear of the first basic planetary gear train unit; 2. a second basic planetary gear train unit; 21. a ring gear of the second basic planetary gear train unit; 22. a planetary gear of the second basic planetary gear train unit; 23. a carrier of the second basic planetary gear train unit; 24. a sun gear of the second basic planetary gear train unit; 3. a third basic planetary gear train unit; 31. a ring gear of the third basic planetary gear train unit; 32. a planetary gear of the third basic planetary gear train unit; 33. a carrier of the third basic planetary gear train unit; 34. a sun gear of the third basic planetary gear train unit; 4. a fourth basic planetary gear train unit; 41. a ring gear of a fourth basic planetary gear train unit; 42. planetary gears of the fourth basic planetary gear train unit; 43. a carrier of a fourth basic planetary gear train unit; 44. a sun gear of a fourth basic planetary gear train unit; 5. a torque transmitting device; 51. a first transmission member; 52. a second transmission member; 53. a third transmission member; 54. a fourth transmission member; 55. a fifth transmission member; 56. a sixth transmission member; 57. an output member; c1, a first clutch; c2, a second clutch; c3, a third clutch; b1, a first brake; b2, a second brake; b3, a third brake; 6. 11-bar 2 degree-of-freedom separable planetary gear train; 7. an input shaft; 8. an output shaft.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the present invention more apparent, embodiments of the present invention will be further described with reference to the accompanying drawings. The following presents a preferred one of a number of possible embodiments of the invention in order to provide a basic understanding of the invention, but is not intended to identify key or critical elements of the invention or to delineate the scope of the invention.
In the description of the present invention, unless explicitly stated or limited otherwise, the terms "fixedly connected" and "connected" should be interpreted in a broad sense, for example, as a fixed connection, as a removable connection, or as an integral connection, as a mechanical connection, as an electrical connection, as a direct connection, as an indirect connection via an intermediary, or as a communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Referring to fig. 1, an embodiment of the present invention provides an eight speed automatic transmission with smooth transmission, including a transmission case 9; and input shaft 7, output shaft 8, 11 mounted inside transmission housing 9, planetary gear train 6 and torque transmitting device 5 with degrees of freedom of lever 2 being separable.
The planetary gear train 6 in which the degree of freedom of the 11-bar 2 is separable includes four basic planetary gear train units, respectively a first basic planetary gear train unit 1, a second basic planetary gear train unit 2, a third basic planetary gear train unit 3, and a fourth basic planetary gear train unit 4, which are sequentially arranged in the direction of the input shaft 7 to the output shaft 8.
Each basic planetary gear train unit includes a ring gear, a planetary gear, a carrier, and a sun gear.
Specific:
the sun gear 14 of the first basic planetary gear train unit is in external meshed transmission with the planet gears 12 of the first basic planetary gear train unit, the planet gears 12 of the first basic planetary gear train unit are in internal meshed transmission with the ring gear 11 of the first basic planetary gear train unit, and the planet gears 12 of the first basic planetary gear train unit are rotatably supported on the planet carrier 13 of the first basic planetary gear train unit.
The sun gear 24 of the second basic planetary gear train unit is in external meshed transmission with the planet gears 22 of the second basic planetary gear train unit, the planet gears 22 of the second basic planetary gear train unit are in internal meshed transmission with the ring gear 21 of the second basic planetary gear train unit, and the planet gears 22 of the second basic planetary gear train unit are rotatably supported on the planet carrier 23 of the second basic planetary gear train unit.
The sun gear 34 of the third basic planetary gear train unit is in external meshed transmission with the planet gears 32 of the third basic planetary gear train unit, the planet gears 32 of the third basic planetary gear train unit are in internal meshed transmission with the ring gear 31 of the third basic planetary gear train unit, and the planet gears 32 of the third basic planetary gear train unit are rotatably supported on the planet carrier 33 of the third basic planetary gear train unit.
The sun gear 44 of the fourth basic planetary gear train unit is in external meshed transmission with the planet gears 42 of the fourth basic planetary gear train unit, the planet gears 42 of the fourth basic planetary gear train unit are in internal meshed transmission with the ring gear 41 of the fourth basic planetary gear train unit, and the planet gears 42 of the fourth basic planetary gear train unit are rotatably supported on the planet carrier 43 of the fourth basic planetary gear train unit.
The planet carrier 13 of the first basic planetary gear train unit is fixedly connected with the planet carrier 23 of the second basic planetary gear train unit; the gear ring 11 of the first basic planetary gear train unit is fixedly connected with the sun gear 24 of the second basic planetary gear train unit; the ring gear 21 of the second basic planetary gear train unit is fixedly connected with the sun gear 34 of the third basic planetary gear train unit; the carrier 33 of the third basic planetary gear train unit is fixedly connected with the ring gear 41 of the fourth basic planetary gear train unit; the ring gear 31 of the third basic planetary gear train unit and the carrier 43 of the fourth basic planetary gear train unit are fixedly connected, and the ring gear 31 of the third basic planetary gear train unit and the carrier 43 of the fourth basic planetary gear train unit are fixedly connected with the output shaft 8.
The torque transmitting devices include three clutches and three brakes. The three clutches are a first clutch C1, a second clutch C2 and a third clutch C3 respectively, and the three brakes are a first brake B1, a second brake B2 and a third brake B3 respectively.
A first clutch C1 connecting the input shaft 7 to the sun gear 24 of the second basic planetary gear unit and the ring gear 11 of the first basic planetary gear unit;
a second clutch C2 connecting the input shaft 7 to the carrier 13 of the first basic planetary gear train unit and the carrier 23 of the second basic planetary gear train unit;
a third clutch C3 connecting the input shaft 7 to the carrier 33 of the third basic planetary gear train unit and the ring gear 41 of the fourth basic planetary gear train unit;
a first brake B1 connected to the sun gear 14 of the first basic planetary gear train unit;
a second brake B2 connecting the carrier 13 of the first basic planetary gear train unit and the carrier 23 of the second basic planetary gear train unit;
a third brake B3 connected to the sun gear 44 of the fourth basic planetary gear train unit;
wherein three combinations of the first clutch C1, the second clutch C2, the third clutch C3, the first brake B1, the second brake B2 and the third brake B3 are selectively engaged to establish eight forward gear ratios and one reverse gear ratio between the input shaft 7 and the output shaft 8.
In the present embodiment, the input shaft 7 connects the sun gear 24 of the second basic planetary gear train unit and the ring gear 11 of the first basic planetary gear train unit through the third transmission member 53; the input shaft 7 is connected to the planet carrier 13 of the first basic planetary gear train unit and the planet carrier 23 of the second basic planetary gear train unit by a second transmission member 52, and the ring gear 21 of the second basic planetary gear train unit is connected to the sun gear 34 of the third basic planetary gear train unit by a fourth transmission member 54; the input shaft 7 is connected to the carrier 33 of the third basic planetary gear set unit and the ring gear 41 of the fourth basic planetary gear set unit via a fifth transmission member 55, the ring gear 31 of the third basic planetary gear set unit and the carrier 43 of the fourth basic planetary gear set unit are both connected to an output member 57, and the output member 57 is connected to the output shaft 8.
In this embodiment, the three clutches are structurally characterized in the transmission as follows: the first clutch C1 is connected to the third transmission member 53, the second clutch C2 is connected to the second transmission member 52, and the third clutch C3 is connected to the fifth transmission member 55.
In this embodiment, the three brakes are structurally characterized in the transmission as follows: the first brake B1 is connected with the first transmission member 51; the second brakes B2 are each connected with the second transmission member 52; the third brake B3 is connected with the sixth transmission member 56.
The input shaft 7 is connected through a first clutch C1, a second clutch C2, a third clutch C3, and a third transmission member 53, a second transmission member 52, and a fifth transmission member 55, respectively. The input shaft is connected with the generator through the hydraulic torque converter, and power provided by the generator is transmitted to the input shaft through the hydraulic torque converter.
The output shaft 7 is connected to the vehicle driving wheels through a differential mechanism, and transmits the output power to the vehicle driving wheels.
In the embodiment, the first clutch C1, the second clutch C2 and the third clutch C3 are all multi-plate wet clutches, and when the driving plate and the driven plate of the clutches are pressed under the action of hydraulic pressure, the clutches are engaged and are in a working state, and at the moment, the movable members connected with the two ends of the clutches are engaged and have the same rotating speed; on the contrary, when the clutch is in a non-working state, the movable components connected with the two ends of the clutch are separated and have different rotating speeds.
In this embodiment, the first brake B1, the second brake B2 and the third brake B3 are all multi-plate wet brakes for connecting the transmission member and the transmission housing, and when the brakes are in the operating state, the transmission member is engaged with the transmission housing, the transmission member cannot rotate, and the transmission member is in the braking state.
The eight forward gears established by the invention are respectively four deceleration gears, one direct gear and three overdrive gears, and the eight forward gears are specifically as follows:
by engaging the first clutch C1, the first brake B1 and the third brake B3, a first gear ratio is established between the input shaft 7 and the output shaft 8;
by engaging the second clutch C2, the first brake B1 and the third brake B3, a second gear ratio is established between the input shaft 7 and the output shaft 8;
by engaging the first clutch C1, the second clutch C2 and the third brake B3, a three-speed gear ratio is established between the input shaft 7 and the output shaft 8;
by engaging the first clutch C1, the third clutch C3 and the third brake B3, a fourth gear ratio is established between the input shaft 7 and the output shaft 8;
establishing a five-speed gear ratio between the input shaft 7 and the output shaft 8 by engaging the first clutch C1, the second clutch C2 and the third clutch C3;
by engaging the second clutch C2, the third clutch C3 and the first brake B1, a six-speed transmission ratio is established between the input shaft 7 and the output shaft 8;
by engaging the first clutch C1, the third clutch C3 and the first brake B1, a seven-speed transmission ratio is established between the input shaft 7 and the output shaft 8;
by engaging the third clutch C3, the first brake B1 and the second brake B2, an eight-speed gear ratio is established between the input shaft 7 and the output shaft 8.
The transmission of the present invention can also achieve reverse gear by engaging the first clutch C1, the second brake B2 and the third brake B3 to establish a reverse gear ratio between the input shaft 7 and the output shaft 8.
The gear ratio of an automatic transmission mechanism is the ratio of the rotational speeds of the input member and the output member. The automatic transmission mechanism in the present invention can realize 9 different gear ratios, namely 9 gears, including 8 forward gears and 1 reverse gear. Each gear can be realized by controlling the working states of the clutch and the brake.
Referring to fig. 1 and the operation logic table shown in fig. 2, the specific implementation process of the gear ratios of the transmission is as follows:
(1) The gear 1 is a deceleration gear, the transmission ratio is larger than 1, the first clutch C1, the first brake B1 and the third brake B3 are in an operating state, and other clutches and brakes are in a non-operating state. The third transmission member 53 rotates together with the input shaft as a whole due to the action of the clutch C1, and the third transmission member 53 is an input member. The first transmission member 51 and the sixth transmission member 56 are in a braking state due to the action of the first brake B1 and the third brake B3, and the rotational speed is 0. Power is transmitted from an input member (third transmission member) 53, and in the first basic planetary gear train unit 1, the third transmission member 53 drives the planetary gears 12 of the first basic planetary gear train unit 1 to rotate, thereby driving the second transmission member 52 to rotate; in the second basic planetary gear train unit 2, the third transmission member 53 and the second transmission member 52 jointly drive the planetary gears 22 of the second basic planetary gear train unit 2 to rotate, and further drive the fourth transmission member 54 to rotate; in the third basic planetary gear train unit 3, the fourth transmission member 54 drives the planetary gears 32 of the third basic planetary gear train unit 3 to rotate, and further drives the fifth transmission member 55 to rotate; in the fourth basic planetary gear train unit 4, the fifth transmission member 55 rotates the planetary gears 42 of the fourth basic planetary gear train unit 4, and at this time, the planetary gears 32 of the third basic planetary gear train unit 3 and the planetary gears 42 of the fourth basic planetary gear train unit 4 rotate together, thereby rotating the output member 57, and transmitting power to the output member 57. The rotational speed of the output member 57 is lower than the rotational speed of the input member (third transmission member) 53, in the lower 1 st gear.
(2) The gear 2 is a deceleration gear, the transmission ratio is larger than 1, the second clutch C2, the first brake B1 and the third brake B3 are in an operating state, and other clutches and brakes are in a non-operating state. The second transmission member 52 rotates together with the input shaft as a whole due to the action of the second clutch C2, and the second transmission member 52 is an input member. The first transmission member 51 and the sixth transmission member 56 are in a braking state due to the action of the first brake B1 and the second brake B3, and the rotational speed is 0. The power is transmitted from the input member (second transmission member) 52, and in the first basic planetary gear train unit 1, the second transmission member 52 drives the planetary gears 12 of the first basic planetary gear train unit 1 to rotate, and then drives the third transmission member 53 to rotate; in the second basic planetary gear train unit 2, the third transmission member 53 and the second transmission member 52 jointly drive the planetary gears 22 of the second basic planetary gear train unit 2 to rotate, and further drive the fourth transmission member 54 to rotate; in the third basic planetary gear train unit 3, the fourth transmission member 54 drives the planetary gears 32 of the third basic planetary gear train unit 3 to rotate, and further drives the fifth transmission member 55 to rotate; in the fourth basic planetary gear train unit 4, the fifth transmission member 55 rotates the planetary gears 42 of the fourth basic planetary gear train unit 4, and at this time, the planetary gears 32 of the third basic planetary gear train unit 3 and the planetary gears 42 of the fourth basic planetary gear train unit 4 rotate together, thereby rotating the output member 57, and transmitting power to the output member 57. The rotational speed of the output member 57 is lower than the rotational speed of the input member (second transmission member) 52, in gear 2, which is higher than the rotational speed of gear 1.
(3) The 3 rd gear is a deceleration gear, the transmission ratio is larger than 1, the first clutch C1, the second clutch C2 and the third brake B3 are in working states, and other clutches and brakes are in non-working states. Due to the action of the first clutch C1 and the second clutch C2, the third transmission member 53 and the second transmission member 52 are both input members, and power is simultaneously transmitted from the third transmission member 53 and the second transmission member 52 to drive the first basic planetary gear train unit 1 and the second basic planetary gear train unit 2 to integrally rotate, so that the fourth transmission member 54 is driven to rotate, and the rotation speed of the fourth transmission member is equal to that of the input shaft. The sixth transmission member 56 is in a braked state with a rotational speed of 0 due to the action of the third brake B3. In the third basic planetary gear train unit 3, the fourth transmission member 54 drives the planetary gears 32 of the third basic planetary gear train unit 3 to rotate, and further drives the fifth transmission member 55 to rotate; in the fourth basic planetary gear train unit 4, the fifth transmission member 55 rotates the planetary gears 42 of the fourth basic planetary gear train unit 4, and at this time, the planetary gears 32 of the third basic planetary gear train unit 3 and the planetary gears 42 of the fourth basic planetary gear train unit 4 rotate together, thereby rotating the output member 57, and transmitting power to the output member 57. The rotational speed of the output member 57 is smaller than the rotational speeds of the input member (third transmission member) 53 and the input member (second transmission member) 52, in 3 rd gear, which is higher than the 2 nd gear rotational speed.
(4) The 4 th gear is a deceleration gear, the transmission ratio is larger than 1, the first clutch C1, the third clutch C3 and the third brake B3 are in working states, and other clutches and brakes are in non-working states. The third transmission member 53 and the fifth transmission member 55 are both input members due to the action of the first clutch C1 and the third clutch C3, and power is transmitted simultaneously by the third transmission member 53 and the fifth transmission member 55. Due to the action of the third brake B3, the sixth transmission member 56 is in a braked state at a rotational speed of 0. In the fourth basic planetary gear train unit 4, the fifth transmission member 55 rotates the planetary gears 42 of the fourth basic planetary gear train unit 4, which in turn rotates the output member 57, transmitting power to the output member 57. The rotational speed of the output member 57 is lower than the rotational speed of the input member (fifth transmission member) 55, in 4 th gear, which is higher than the rotational speed of 3 rd gear.
(5) The 5 th gear is a direct gear, the transmission ratio is equal to 1, the first clutch C1, the second clutch C2 and the third clutch C3 are in working states, and other brakes are in non-working states. Because of the actions of the first clutch C1, the second clutch C2 and the third clutch C3, the third transmission member 53, the second transmission member 52 and the fifth transmission member 55 are input members, and power is transmitted by the third transmission member 53, the second transmission member 52 and the fifth transmission member 55 at the same time to drive the whole mechanism to rotate, so that the rotation speed of the input member and the rotation speed of the output member are the same, and the input member and the output member are in direct gear.
(6) And 6 is an overdrive gear, the transmission ratio is smaller than 1, the second clutch C2, the third clutch C3 and the first brake B1 are in working states, and the other clutches and brakes are in non-working states. The second transmission member 52 and the fifth transmission member 55 are the same as the input members due to the action of the second clutch C2 and the third clutch C3, and power is transmitted simultaneously by the second transmission member 52 and the fifth transmission member 55. The first transmission member 51 is in a braking state due to the action of the first brake B1, and the rotational speed is 0. In the first basic planetary gear train unit 1, the second transmission member 52 drives the planetary gears 12 of the first basic planetary gear train unit 1 to rotate, and further drives the third transmission member 53 to rotate; in the second basic planetary gear train unit 2, the third transmission member 53 and the second transmission member 52 jointly drive the planetary gears 22 of the second basic planetary gear train unit 2 to rotate, and further drive the fourth transmission member 54 to rotate; in the third basic planetary gear set unit 3, the fourth transmission member 54 and the fifth transmission member 55 together rotate the planetary gears 32 of the third basic planetary gear set unit 3, thereby rotating the output member 57, and transmitting power to the output member 57. The rotational speed of the output member 57 is greater than the rotational speeds of the input member (second transmission member) 52 and the input member (fifth transmission member) 55, in 6 th gear, where the rotational speed is high.
(7) And the 7 th gear is an overdrive gear, the transmission ratio is smaller than 1, the first clutch C1, the third clutch C3 and the first brake B1 are in working states, and the other clutches and brakes are in non-working states. The third transmission member 53 and the fifth transmission member 55 are the same as the input members due to the action of the first clutch C1 and the third clutch C3, and power is transmitted simultaneously by the third transmission member 53 and the fifth transmission member 55. The first transmission member 51 is in a braking state due to the action of the first brake B1, and the rotational speed is 0. In the first basic planetary gear train unit 1, the third transmission member 53 drives the planetary gears 12 in the first basic planetary gear train unit 1 to rotate, and further drives the second transmission member 52 to rotate; in the second basic planetary gear train unit 2, the third transmission member 53 and the second transmission member 52 jointly drive the planetary gears 22 of the second basic planetary gear train unit 2 to rotate, and further drive the fourth transmission member 54 to rotate; in the third basic planetary gear set unit 3, the fourth transmission member 54 and the fifth transmission member 55 together rotate the planetary gears 32 of the third basic planetary gear set unit 3, thereby rotating the output member 57, and transmitting power to the output member 57. The rotational speed of the output member 57 is greater than the rotational speeds of the input member (third transmission member) 53 and the input member (fifth transmission member) 55, in 7 th gear, which is higher than the 6 th gear rotational speed.
(8) And 8 th gear is an overdrive gear, the transmission ratio is smaller than 1, the third clutch C3, the first brake B1 and the second brake B2 are in working states, and the other clutches and brakes are in non-working states. The fifth transmission member 55 rotates together with the input shaft as a whole due to the action of the third clutch C3, and the fifth transmission member 55 is an input member. The first transmission member 51 and the second transmission member 52 are in a braking state due to the action of the first brake B1 and the second brake B2, and the rotational speed is 0. In the third basic planetary gear train unit 3, the fifth transmission member 55 rotates the planetary gears 32 of the third basic planetary gear train unit 3, which in turn rotates the output member 57, transmitting power to the output member 57. The rotational speed of the output member 57 is greater than the rotational speed of the input member (fifth transmission member) 55, in 8 th gear, which is higher than the 7 th gear rotational speed.
(9) The 9 th gear is the reverse gear, the first clutch C1, the second brake B2 and the third brake B3 are in an operating state, and other clutches and brakes are in a non-operating state. The third transmission member 53 rotates together with the input shaft as a whole due to the action of the first clutch C1, and the third transmission member 53 is an input member. The second transmission member 52 and the sixth transmission member 56 are in a braking state due to the action of the second brake B2 and the third brake B3, and the rotational speed is 0. In the second basic planetary gear train unit 2, the third transmission member 53 drives the planetary gears 22 of the second basic planetary gear train unit 2 to rotate, and further drives the fourth transmission member 54 to rotate; in the third basic planetary gear train unit 3, the fourth transmission member 54 drives the planetary gears 32 of the third basic planetary gear train unit 3 to rotate, and further drives the fifth transmission member 55 to rotate; in the fourth basic planetary gear train unit 4, the fifth transmission member 55 rotates the planetary gears 42 of the fourth basic planetary gear train unit 4, and at this time, the planetary gears 32 of the third basic planetary gear train unit 3 and the planetary gears 42 of the fourth basic planetary gear train unit 4 rotate together, thereby rotating the output member 57, and transmitting power to the output member 57. The rotational speed direction of the output member 57 is opposite to the rotational speed direction of the input member (third transmission member) 53, and is in reverse gear.
In the present invention, the characteristic parameter K of the basic planetary gear train unit is the gear ratio of the ring gear to the sun gear. The relation between the gear ratio and the characteristic parameter of each gear is shown in table 1.
In order to achieve higher transmission efficiency of each gear, 4 basic planets in the mechanismThe characteristic parameters of the wheel train units are K respectively 1 ＝1.5，K 2 ＝2.0、K 3 =1.5 and K 4 =2.5, the transmission ratio of each gear thus calculated is 5,3,2,1.4,1,0.82,0.71,0.6, -4, respectively. The implementation of each gear is summarized in fig. 2.
TABLE 1 relation between gear ratio and characteristic parameters
Figure BDA0004155177050000151
The clutch and brake operating states are easy to control, and the single conversion principle is met, namely, when two adjacent gears are switched, only the operating state of one clutch or brake is required to be changed, so that the control difficulty of the transmission is reduced. The step ratio between each gear is stable, and gear shifting is smooth.
The embodiments described above and features of the embodiments herein may be combined with each other without conflict.
The foregoing description of the preferred embodiments of the invention is not intended to limit the invention to the precise form disclosed, and any such modifications, equivalents, and alternatives falling within the spirit and scope of the invention are intended to be included within the scope of the invention.

Claims (10)

1. An eight-gear automatic transmission with stable transmission comprises a transmission shell (9); and an input shaft (7), an output shaft (8) and a torque transmission device (5) which are arranged in a transmission housing, and the planetary transmission device is characterized by further comprising an 11-bar 2 degree-of-freedom separable planetary gear train (6), wherein the 11-bar 2 degree-of-freedom separable planetary gear train (6) comprises four basic planetary gear train units which are sequentially arranged along the direction from the input shaft (7) to the output shaft (8) and are respectively a first basic planetary gear train unit (1), a second basic planetary gear train unit (2), a third basic planetary gear train unit (3) and a fourth basic planetary gear train unit (4), and each basic planetary gear train unit comprises a gear ring, a planetary gear, a planetary carrier and a sun gear; the planet carrier (13) of the first basic planetary gear train unit is fixedly connected with the planet carrier (23) of the second basic planetary gear train unit; the gear ring (11) of the first basic planetary gear train unit is fixedly connected with the sun gear (24) of the second basic planetary gear train unit; a gear ring (21) of the second basic planetary gear train unit is fixedly connected with a sun gear (34) of the third basic planetary gear train unit; the planet carrier (33) of the third basic planetary gear train unit is fixedly connected with the gear ring (41) of the fourth basic planetary gear train unit; the gear ring (31) of the third basic planetary gear train unit is fixedly connected with the planet carrier (43) of the fourth basic planetary gear train unit, and the gear ring (31) of the third basic planetary gear train unit and the planet carrier (43) of the fourth basic planetary gear train unit are fixedly connected with the output shaft (8);
the torque transmitting device includes:
a first clutch (C1) that connects the input shaft (7) to a ring gear (11) of the first basic planetary gear train unit and a sun gear (24) of the second basic planetary gear train unit, respectively;
a second clutch (C2) connecting the input shaft (7) to the carrier (13) of the first basic planetary gear train unit and the carrier (23) of the second basic planetary gear train unit;
a third clutch (C3) that connects the input shaft (7) to a carrier (33) of the third basic planetary gear train unit and a ring gear (41) of the fourth basic planetary gear train unit, respectively;
a first brake (B1) connected to a sun gear (14) of the first basic planetary gear train unit;
a second brake (B2) connecting the carrier (13) of the first basic planetary gear train unit and the carrier (23) of the second basic planetary gear train unit;
a third brake (B3) connected to a sun gear (44) of the fourth basic planetary gear train unit;
wherein three combinations of the first clutch (C1), the second clutch (C2), the third clutch (C3), the first brake (B1), the second brake (B2) and the third brake (B3) are selectively engaged to establish eight forward gear ratios and one reverse gear ratio between the input shaft (7) and the output shaft (8).
2. Eight speed automatic transmission according to claim 1, wherein said input shaft (7) connects the sun gear (24) of said second basic planetary gear set unit and the ring gear (11) of the first basic planetary gear set unit via a third transmission member (53); the input shaft (7) is connected with the planet carrier (13) of the first basic planetary gear train unit and the planet carrier (23) of the second basic planetary gear train unit through a second transmission member (52), and the gear ring (21) of the second basic planetary gear train unit is connected with the sun gear (34) of the third basic planetary gear train unit through a fourth transmission member (54); the input shaft (7) is connected to the planet carrier (33) of the third basic planetary gear train unit and the ring gear (41) of the fourth basic planetary gear train unit via a fifth transmission member (55), the ring gear (31) of the third basic planetary gear train unit and the planet carrier (43) of the fourth basic planetary gear train unit are both connected to an output member (57), and the output member (57) is connected to the output shaft (8).
3. Eight speed automatic transmission according to claim 2, wherein said first clutch (C1) is connected with said third transmission member (53), said second clutch (C2) is connected with said second transmission member (52), and said third clutch (C3) is connected with said fifth transmission member (55).
4. An eight speed automatic transmission according to claim 3, wherein said first brake (B1) is connected with a first transmission member (51); the second brake (B2) is connected with the second transmission member (52); the third brake (B3) is connected to a sixth transmission member (56).
5. The eight speed automatic transmission of claim 4, wherein eight speed ratios of said eight speed automatic transmission are four downshift gears, one direct gear and three overdrive gears, respectively.
6. The eight speed automatic transmission according to claim 5, wherein,
-establishing a first gear ratio between the input shaft (7) and the output shaft (8) by engaging the first clutch (C1), the first brake (B1) and the third brake (B3);
-establishing a second gear ratio between the input shaft (7) and the output shaft (8) by engaging the second clutch (C2), the first brake (B1) and the third brake (B3);
-establishing a three-gear transmission ratio between the input shaft (7) and the output shaft (8) by engaging the first clutch (C1), the second clutch (C2) and the third brake (B3);
-establishing a fourth gear ratio between the input shaft (7) and the output shaft (8) by engaging the first clutch (C1), the third clutch (C3) and the third brake (B3);
-establishing a five-speed transmission ratio between the input shaft (7) and the output shaft (8) by engaging the first clutch (C1), the second clutch (C2) and the third clutch (C3);
-establishing a six-speed transmission ratio between the input shaft (7) and the output shaft (8) by engaging the second clutch (C2), the third clutch (C3) and the first brake (B1);
-establishing a seven-speed transmission ratio between the input shaft (7) and the output shaft (8) by engaging the first clutch (C1), the third clutch (C3) and the first brake (B1);
-establishing an eight-speed transmission ratio between the input shaft (7) and the output shaft (8) by engaging the first brake (B1) and the second brake (B2) of the third clutch (C3).
7. Eight speed automatic transmission according to claim 6, characterized in that a reverse gear ratio is established between said input shaft (7) and said output shaft (8) by engaging said first clutch (C1), said second brake (B2) and said third brake (B3).
8. The eight speed automatic transmission according to claim 7, wherein the first clutch (C1), the second clutch (C2) and the third clutch (C3) are all multi-plate wet clutches.
9. The eight speed automatic transmission according to claim 8, wherein said first brake (B1), said second brake (B2) and said third brake (B3) are all multi-plate wet brakes.
10. Eight speed automatic transmission according to claim 9, wherein said first brake (B1), said second brake (B2) and said third brake (B3) are each fixed to said transmission housing (9).
CN202310331941.2A 2023-03-30 2023-03-30 Eight-gear automatic transmission with stable transmission Pending CN116292783A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202310331941.2A CN116292783A (en) 2023-03-30 2023-03-30 Eight-gear automatic transmission with stable transmission

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202310331941.2A CN116292783A (en) 2023-03-30 2023-03-30 Eight-gear automatic transmission with stable transmission

Publications (1)

Publication Number Publication Date
CN116292783A true CN116292783A (en) 2023-06-23

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202310331941.2A Pending CN116292783A (en) 2023-03-30 2023-03-30 Eight-gear automatic transmission with stable transmission

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Country Link
CN (1) CN116292783A (en)

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