CN216343756U - Two-gear automatic transmission with internal gear output - Google Patents

Two-gear automatic transmission with internal gear output Download PDF

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Publication number
CN216343756U
CN216343756U CN202120545416.7U CN202120545416U CN216343756U CN 216343756 U CN216343756 U CN 216343756U CN 202120545416 U CN202120545416 U CN 202120545416U CN 216343756 U CN216343756 U CN 216343756U
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China
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gear
internal gear
clutch
output
brake
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CN202120545416.7U
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梁志伟
李想
张亮
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Yinchuan Weili Transmission Technology Co ltd
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Yinchuan Weili Transmission Technology Co ltd
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Abstract

The utility model provides a two grades of automatic gearbox of internal gear output, this derailleur include casing, input shaft, planetary drive subassembly, internal gear, clutch, stopper, secondary drive subassembly and differential mechanism, the input of input shaft is connected with actuating mechanism, its output with planetary drive subassembly is connected, and planetary drive subassembly passes through the clutch with internal gear fixed connection, planetary drive subassembly passes through the stopper with casing fixed connection, the internal gear with secondary drive subassembly's input is connected, secondary drive subassembly's output with differential mechanism connects, the power of actuating mechanism output passes through the input shaft and exports planetary drive subassembly and internal gear, and the rethread secondary drive subassembly exports to differential mechanism to realize high-speed shelves and low-speed two grades of variable speed. The clutch and the brake of the utility model work independently, thus realizing smooth and impact-free gear shifting process and no power interruption, and having simple structure and high power transmission efficiency.

Description

Two-gear automatic transmission with internal gear output
[ technical field ] A method for producing a semiconductor device
The utility model relates to a power transmission device of an electric automobile, in particular to a two-gear automatic transmission with internal gear output.
[ background of the utility model ]
A transmission system of a traditional new energy automobile (including a pure electric automobile, a hybrid electric automobile and the like) generally adopts a fixed speed ratio transmission, and the transmission mode has a simple structure and low cost. However, when a fixed-speed-ratio transmission is adopted, high requirements are provided for a driving motor, namely, high instantaneous torque is provided in a constant torque area, and high running speed is provided in a constant power area, so that the requirements of automobile acceleration, climbing and high-speed running are met. Meanwhile, the fixed speed ratio transmission has larger efficiency reduction amplitude of the driving motor under the load conditions of the highest speed and the lowest speed, and the loss of the motor, the electric control and the battery is seriously increased. When the motor reaches the limit speed, the motor cannot continuously rise, so the maximum speed is restricted. And when the automobile runs at high speed, the motor needs to keep extremely high rotating speed, and the noise control and the mileage continuation are not good.
Therefore, the two-gear automatic transmission is produced at the same time, the highest driving speed of the automobile is improved, the driving motor can work in a high-efficiency area all the time, and the system efficiency of the transmission with a relatively fixed speed ratio is higher, so that the automobile can obtain longer pure electric driving endurance mileage. In addition, the low-speed gear can have a better acceleration level when the automobile starts, and the high-speed gear reduces the working rotating speed of the motor while meeting the highest speed, so that the NVH performance of the whole automobile is improved. However, the existing two-gear automatic transmission has the problems of complex structure, low power transmission efficiency and easy power interruption in the gear shifting process.
[ summary of the utility model ]
The utility model aims to solve the problems and provides a two-gear automatic transmission which realizes smooth and impact-free gear shifting process, no power interruption, simple structure and high power transmission efficiency by controlling a clutch and a brake to work independently and outputs by an internal gear.
In order to achieve the above object, the present invention provides an internal gear output two-speed automatic transmission, which comprises a housing, an input shaft, a planetary transmission assembly, an internal gear, a clutch, a brake, a secondary transmission assembly and a differential mechanism, wherein the input end of the input shaft is connected with a driving mechanism, the output end of the planetary transmission mechanism is connected with the planetary transmission component which is fixedly connected with the internal gear through the clutch, the planetary transmission assembly is fixedly connected with the shell through the brake, the internal gear is connected with the input end of the secondary transmission assembly, the output end of the secondary transmission assembly is connected with the differential mechanism, and the power output by the driving mechanism is output to the planetary transmission assembly and the inner gear through the input shaft and then output to the differential mechanism through the secondary transmission assembly so as to realize two-gear speed change of a high gear and a low gear.
The planetary transmission assembly comprises a sun wheel, a planetary wheel and a planet carrier provided with the planetary wheel, the sun wheel is fixedly connected with the output end of the input shaft, and the planetary wheel is respectively meshed with the sun wheel and the inner gear.
The internal gear is connected with the input end of the secondary transmission component through a spline.
The clutch is a wet clutch and is provided with a steel sheet and a friction sheet, the steel sheet of the clutch is connected with the planet carrier through a spline, the friction sheet of the clutch is connected with the internal gear through the spline, and when the friction sheet of the clutch is contacted with the steel sheet to generate friction force, the planet carrier is fixedly connected with the internal gear, so that high-speed gear speed change is realized.
The brake is a wet brake, the brake is provided with a steel sheet and a friction sheet, the friction sheet of the brake is connected with the planet carrier through a spline, the steel sheet of the brake is connected with the shell through the spline, and when the friction sheet of the brake is contacted with the steel sheet to generate friction force, the planet carrier is fixedly connected with the shell, so that low-speed gear speed change is realized.
The secondary transmission assembly comprises a secondary driving wheel and a secondary driven wheel meshed with the secondary driving wheel, the secondary driving wheel is connected with the internal gear through a spline, and the secondary driven wheel is fixedly connected with the differential.
The differential mechanism comprises a planetary gear, a left driving half shaft and a right driving half shaft which are respectively connected with the planetary gear, and the secondary driven wheel is fixedly connected with the differential mechanism through bolts.
The driving mechanism is a motor and is connected with the input end of the input shaft through a spline.
The number of teeth of the sun gear is Z1The number of teeth of the internal gear is Z2The gear ratio a of the internal gear to the sun gear is Z2/Z1
Further, during low gear shifting, the clutch is not operated, the brake is operated, and the transmission ratio i of the planetary transmission assembly is1A; during high-speed gear shifting, the clutch works, the brake does not work, and the transmission ratio i of the planetary transmission assembly21 is ═ 1; when the reverse gear is changed, the clutch does not work, the brake works, and the transmission ratio i of the planetary transmission assembly1-a; and when the clutch is in a neutral position, the clutch and the brake do not work.
The contribution of the utility model is that the utility model effectively solves the problems of the prior two-gear automatic transmission. The utility model enables the power output by the driving mechanism to be output to the planetary transmission assembly and the internal gear through the input shaft and then to be output to the differential through the secondary transmission assembly by arranging the internal gear, so as to realize two-gear speed change of a high gear and a low gear. The clutch and the brake of the utility model work independently, thus realizing smooth and impact-free gear shifting process and no power interruption, and having simple structure and high power transmission efficiency.
[ description of the drawings ]
Fig. 1 is a schematic diagram of the present invention.
Fig. 2 is a schematic structural diagram of the present invention.
[ detailed description ] embodiments
The following examples are further illustrative and supplementary to the present invention and do not limit the present invention in any way.
Referring to fig. 1, the internal gear output two-speed automatic transmission of the present invention includes a housing 10, an input shaft 20, a planetary gear assembly 30, an internal gear 40, a clutch 50, a brake 60, a secondary transmission assembly 70, and a differential 80. The transmission is used for a transmission system of a new energy automobile, can realize smooth and impact-free gear shifting process and power interruption-free, and can improve the power transmission efficiency and the comfort of vehicle driving.
As shown in fig. 2, the housing 10 is hollow, and the input shaft 20, the planetary gear assembly 30, the ring gear 40, the clutch 50, the brake 60, the secondary transmission assembly 70, and the differential 80 are provided in the housing 10. For the convenience of assembling the transmission, the housing 10 may be formed by assembling a plurality of sub-housings, for example, the input shaft 20, the planetary gear assembly 30, the internal gear 40, the clutch 50, the brake 60, the secondary transmission assembly 70 and the differential 80 may be separately installed according to actual requirements, and then the plurality of sub-housings may be connected by bolts. The input shaft 20 is connected at its input end to the drive mechanism 90 and at its output end to the planetary transmission assembly 30. The driving mechanism 90 in this embodiment is a motor, and the driving mechanism 90 is connected to the input end of the input shaft 20 through a spline (not shown).
As shown in fig. 1 and 2, the planetary gear assembly 30 is connected to the output end of the input shaft 20, the internal gear 40, the clutch 50 and the brake 60, respectively, and is used to transmit the power output from the input shaft 20 to the internal gear 40 or the secondary transmission assembly 70. Specifically, the planetary transmission assembly 30 includes a sun gear 31, a plurality of planet gears 32 and a planet carrier 33, wherein the sun gear 31 is disposed in the middle of the planet carrier 33 and has the same axial direction as the input shaft 20, the sun gear 31 is fixedly connected to the output end of the input shaft 20, the plurality of planet gears 32 are disposed on the planet carrier 33 at equal intervals and are respectively meshed with the sun gear 31 and the inner gear 40. The number of the planet wheels 32 in this embodiment is three, and certainly, the number of the planet wheels 32 is not limited to this, and may be set according to actual needs. The carrier 33 is used for mounting the planet gears 32, and the carrier 33 is also connected to the clutch 50 and the brake 60, respectively. In the present embodiment, the three planet gears 32 are respectively mounted on the planet carrier 33 through planet shafts, and the planet carrier 33 is respectively connected with the clutch 50 and the brake 60 through splines.
As shown in fig. 1 and 2, the internal gear 40 is disposed at an outer periphery of the planetary gear assembly 30, and is connected to the planetary gear assembly 30, the clutch 50, and the secondary gear assembly 70, respectively, for transmitting power of the planetary gear assembly 30 to the secondary gear assembly 70. Specifically, as shown in fig. 2, the internal gear 40 is annular, and has the same axial direction as the input shaft 20, an internal gear ring is provided on the inner side of the internal gear 40 and is used for meshing with the planetary gears 32, and a connecting part is provided at one end of the internal gear 40 close to the driving mechanism 90 and is used for connecting with the secondary transmission assembly 70. In this embodiment, the connecting portion of the internal gear 40 is splined to the input of the secondary drive assembly 70. The end of the inner gear 40 remote from the drive mechanism 90 is splined to the clutch 50, so that the inner gear 40 is fixedly connected to the planetary gear set 30 via the clutch 50.
As shown in fig. 1 and 2, a clutch 50 is provided at an end of the carrier 33 remote from the drive mechanism 90, and the clutch 50 is connected to the carrier 33 and the internal gear 40, respectively, for fixedly connecting the carrier 33 and the internal gear 40. Specifically, the clutch 50 is a wet clutch, which is provided with a steel plate and a friction plate, wherein the steel plate of the clutch 50 is connected with the planet carrier 33 through a spline, the friction plate of the clutch 50 is connected with the internal gear 40 through a spline, when the clutch 50 works, a piston in the clutch 50 is pushed through the action of hydraulic oil, so that the friction plate and the steel plate of the clutch 50 are contacted to generate friction force, and the planet carrier 33 is fixedly connected with the internal gear 40, thereby realizing high-speed gear shifting.
As shown in fig. 1 and 2, a brake 60 is provided in the case 10, and the brake 60 is connected to the case 10 and the carrier 33, respectively, for fixedly connecting the carrier 33 to the case 10. Specifically, the brake 60 is a wet brake, which is provided with a steel disc and a friction disc, wherein the steel disc of the brake 60 is connected with the housing 10 through a spline, the friction disc is connected with the planet carrier 33 through a spline, when the brake 60 works, a piston in the brake 60 is pushed through the action of hydraulic oil, the friction disc and the steel disc of the brake 60 are contacted to generate friction force, so that the planet carrier 33 is fixedly connected with the housing 10, and low-speed gear shifting is realized.
As shown in fig. 1 and 2, a secondary transmission assembly 70 is provided in the housing 10, and is provided on the outer periphery of the input shaft 20 on the side close to the drive mechanism 90, and the secondary transmission assembly 70 is connected to the internal gear 40 and the differential 80, respectively, and transmits the power output from the internal gear 40 to the differential 80. Specifically, the secondary transmission assembly 70 includes a secondary driving wheel 71 and a secondary driven wheel 72, wherein the secondary driving wheel 71 is disposed on the outer periphery of the input shaft 20 and connected to the connecting portion of the internal gear 40 through a spline, and an external gear ring is disposed on the outer periphery of the secondary driving wheel 71 and engaged with the secondary driven wheel 72. The secondary driven wheel 72 is arranged at one end of the shell 10 close to the differential 80, one end of the secondary driven wheel is arranged on a tooth surface matched with the outer gear ring of the secondary driving wheel 71, and the other end of the secondary driven wheel is fixedly connected with the differential 80. In this embodiment, the secondary driven wheel 72 is fixedly connected to the differential 80 by bolts.
As shown in fig. 1 and 2, a differential 80 is disposed in the housing 10, and the differential 80 is connected to the secondary transmission assembly 70 and is used for rolling the left and right wheels at different rotation speeds when the vehicle is running in a curve or on an uneven road surface, i.e. ensuring that the wheels are driven by both sides to perform pure rolling motion. Specifically, the differential 80 includes a planetary gear 81, a left drive axle 82 and a right drive axle 83. The planetary gear 81 is fixedly connected to the secondary driven wheel 72, and the planetary gear 81 is further connected to a left driving axle 82 and a right driving axle 83, respectively.
As shown in fig. 1, the working principle of the present invention is: if the number of teeth of the sun gear 31 is Z1The number of teeth of the internal gear 40 is Z2The rotational speed of the sun gear is n1The rotating speed of the inner gear ring is n2The rotational speed of the planet carrier is n3(ii) a a is the number of teeth Z of the inner gear ring2Number of teeth Z with sun gear1Ratio of (a) to (Z)2/Z1
When the low gear is shifted, the clutch 50 is not operated, the brake 60 is operated, the piston in the brake 60 is pushed by the hydraulic oil, the friction plate and the steel plate of the brake 60 are contacted to generate friction force, and the planet carrier 33 is fixedly connected with the shell 10, at the moment, the transmission ratio i of the planetary transmission assembly 30 is1The power transmission route of the transmission is as follows: the motor, the input shaft, the sun gear, the internal gear, the secondary driving wheel, the secondary driven wheel, the left driving half shaft and the right driving half shaft.
When the high-speed gear is shifted, the clutch 50 works, the brake 60 does not work, the piston in the clutch 50 is pushed through the action of hydraulic oil, the friction plate and the steel sheet of the clutch 50 are contacted to generate friction force, and the planet carrier 33 is fixedly connected with the internal gear 40, at the moment, the transmission ratio i of the planetary transmission assembly 30 is1The power transmission route of the transmission is 1: the motor, the input shaft, the sun gear, the internal gear, the secondary driving wheel, the secondary driven wheel, the left driving half shaft and the right driving half shaft.
When the reverse gear is performed, the motor rotates reversely, the clutch 50 is not operated, the brake 60 is operated, and the transmission ratio i of the planetary transmission assembly 30 is realized1The power transmission route of the transmission is as follows: the motor, the input shaft, the sun gear, the internal gear, the secondary driving wheel, the secondary driven wheel, the left driving half shaft and the right driving half shaft.
When in neutral, neither the clutch 50 nor the brake 60 is active.
Therefore, the internal gear 40 is arranged, so that the power output by the driving mechanism 90 is output to the planetary transmission assembly 30 and the internal gear 40 through the input shaft 20, and is output to the differential 80 through the secondary transmission assembly 70, and two-gear speed change of a high gear and a low gear is realized. The utility model controls the clutch and the brake to work independently in a hydraulic mode, thereby realizing smooth and impact-free gear shifting process and no power interruption, and having simple structure and high power transmission efficiency.
Although the present invention has been described with reference to the above embodiments, the scope of the present invention is not limited thereto, and modifications, substitutions and the like of the above members are intended to fall within the scope of the claims of the present invention without departing from the spirit of the present invention.

Claims (10)

1. The two-gear automatic transmission with internal gear output is characterized by comprising a shell (10), an input shaft (20), a planetary transmission assembly (30), an internal gear (40), a clutch (50), a brake (60), a secondary transmission assembly (70) and a differential (80), wherein the input end of the input shaft (20) is connected with a driving mechanism (90), the output end of the input shaft is connected with the planetary transmission assembly (30), the planetary transmission assembly (30) is fixedly connected with the internal gear (40) through the clutch (50), the planetary transmission assembly (30) is fixedly connected with the shell (10) through the brake (60), the internal gear (40) is connected with the input end of the secondary transmission assembly (70), the output end of the secondary transmission assembly (70) is connected with the differential (80), and the power output by the driving mechanism (90) is output to the planetary transmission assembly (30) through the input shaft (20) And the inner gear (40) is output to a differential (80) through a secondary transmission assembly (70) so as to realize two-gear speed change of a high gear and a low gear.
2. An internal gear output two speed automatic transmission according to claim 1, wherein the planetary transmission assembly (30) comprises a sun gear (31), planet gears (32) and a planet carrier (33) carrying the planet gears (32), the sun gear (31) being fixedly connected to the output of the input shaft (20), the planet gears (32) being in mesh with the sun gear (31) and the internal gear (40), respectively.
3. An internal gear output two speed automatic transmission according to claim 1, wherein the internal gear (40) is splined to the input of the secondary drive assembly (70).
4. The internal gear output two-speed automatic transmission according to claim 2, wherein the clutch (50) is a wet clutch having a steel plate and a friction plate, the steel plate of the clutch (50) is connected to the carrier (33) by a spline, the friction plate of the clutch (50) is connected to the internal gear (40) by a spline, and when the friction plate of the clutch (50) is in contact with the steel plate to generate friction, the carrier (33) is fixedly connected to the internal gear (40), thereby realizing a high-speed gear shift.
5. An internal gear output two-speed automatic transmission according to claim 2, wherein the brake (60) is a wet brake provided with steel plates and friction plates, the friction plates of the brake (60) are connected with the carrier (33) through splines, the steel plates of the brake (60) are connected with the housing (10) through splines, and when the friction plates of the brake (60) are in contact with the steel plates to generate friction, the carrier (33) is fixedly connected with the housing (10), so that low-speed gear shifting is realized.
6. An internal gear output two-speed automatic transmission according to claim 1, wherein the secondary transmission assembly (70) comprises a secondary drive pulley (71) and a secondary driven pulley (72) engaged therewith, the secondary drive pulley (71) is connected with the internal gear (40) through splines, and the secondary driven pulley (72) is fixedly connected with the differential (80).
7. An internal gear output two-speed automatic transmission according to claim 6, wherein the differential (80) comprises a planetary gear (81) and a left driving half shaft (82) and a right driving half shaft (83) which are respectively connected with the planetary gear (81), and the secondary driven wheel (72) is fixedly connected with the differential (80) through bolts.
8. An internal gear output two speed automatic transmission according to claim 1, wherein the drive mechanism (90) is an electric motor, and the drive mechanism (90) is splined to the input end of the input shaft (20).
9. The internal gear output two-speed automatic transmission according to claim 2, wherein the number of teeth of the sun gear (31) is Z1SaidThe number of teeth of the internal gear (40) is Z2The gear ratio a of the internal gear (40) to the sun gear (31) is Z2/Z1
10. An internal gear output two speed automatic transmission as claimed in claim 9, wherein at low gear shift, the clutch (50) is not operated, the brake (60) is operated, and the planetary gear assembly (30) has a gear ratio i1A; during high-speed gear shifting, the clutch (50) is operated, the brake (60) is not operated, and the transmission ratio i of the planetary transmission assembly (30) is21 is ═ 1; when the reverse gear is changed, the clutch (50) is not operated, the brake (60) is operated, and the transmission ratio i of the planetary transmission assembly (30) is1-a; and when the clutch is in a neutral position, the clutch (50) and the brake (60) do not work.
CN202120545416.7U 2021-03-16 2021-03-16 Two-gear automatic transmission with internal gear output Active CN216343756U (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202120545416.7U CN216343756U (en) 2021-03-16 2021-03-16 Two-gear automatic transmission with internal gear output

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202120545416.7U CN216343756U (en) 2021-03-16 2021-03-16 Two-gear automatic transmission with internal gear output

Publications (1)

Publication Number Publication Date
CN216343756U true CN216343756U (en) 2022-04-19

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ID=81128467

Family Applications (1)

Application Number Title Priority Date Filing Date
CN202120545416.7U Active CN216343756U (en) 2021-03-16 2021-03-16 Two-gear automatic transmission with internal gear output

Country Status (1)

Country Link
CN (1) CN216343756U (en)

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