10-speed AT automatic transmission

Abstract

The present invention discloses a 10-speed AT automatic transmission, comprising an input shaft, a first planetary gear mechanism connected to the input shaft, a second planetary gear mechanism, a first clutch connected to the first planetary gear mechanism and the second planetary gear mechanism, a second clutch and a fifth clutch connected to the second planetary gear mechanism and the input shaft, a third clutch and a fourth clutch connected to the first planetary gear mechanism and the second planetary gear mechanism, and a first brake and a second brake connected to the second planetary gear mechanism, wherein the second planetary gear mechanism is a Ravina-type planetary gear mechanism. The 10-speed AT automatic transmission of the present invention only needs to use a simple planetary gear mechanism and a Ravina-type planetary gear mechanism to realize 10 gears, has relatively few transmission elements, is compactly arranged, has a small space, has obvious cost advantages, and reduces the space occupied by the transmission.

Description

Technical Field

[0001] The invention belongs to the technical field of automobile gearboxes, and in particular to a 10-speed AT automatic gearbox. Background Art

[0002] The times are developing and technology is advancing. In the field of automatic transmissions, it is required that the transmissions have many gears, high transmission efficiency and compact structure, so that the car has the advantages of low fuel consumption and good driving performance. The existing 10-speed AT automatic transmission has the disadvantages of complex structure and long power transmission route, resulting in large size, occupying more space, high cost and low power transmission efficiency. Summary of the invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides a 10-speed AT automatic transmission, the purpose of which is to save space.

[0004] In order to achieve the above-mentioned purpose, the technical solution adopted by the present invention is: a 10-speed AT automatic transmission, including an input shaft, a first planetary gear mechanism connected to the input shaft, a second planetary gear mechanism, a first clutch connected to the first planetary gear mechanism and the second planetary gear mechanism, a second clutch and a fifth clutch connected to the second planetary gear mechanism and the input shaft, a third clutch and a fourth clutch connected to the first planetary gear mechanism and the second planetary gear mechanism, and a first brake and a second brake connected to the second planetary gear mechanism, and the second planetary gear mechanism is a Ravina type planetary gear mechanism.

[0005] The first planetary gear mechanism includes a first sun gear, a first planet carrier connected to the input shaft, a first planetary gear and a second planetary gear arranged on the first planet carrier, and a first ring gear meshing with the second planetary gear, the first planetary gear is located between the second planetary gear and the first sun gear, and the first planetary gear is meshed with the second planetary gear and the first sun gear.

[0006] The first sun gear is fixed, the first clutch and the third clutch are connected to the first ring gear, and the fourth clutch is connected to the first planet carrier.

[0007] The second planetary gear mechanism includes a second sun gear, a third sun gear, a compound planet carrier, a third planetary gear meshing with the second sun gear, a second ring gear meshing with the third planetary gear, a fourth planetary gear meshing with the third sun gear, a fifth planetary gear meshing with the fourth planetary gear and a third ring gear meshing with the fifth planetary gear, and the third planetary gear, the fourth planetary gear and the fifth planetary gear are arranged on the compound planet carrier.

[0008] The first clutch is connected to the third sun gear, the second clutch is connected to the input shaft and the compound planetary carrier, the third clutch and the fourth clutch are connected to the second sun gear, the fifth clutch is connected to the third ring gear, the first brake is connected to the second sun gear and the transmission housing, and the second brake is connected to the compound planetary carrier and the transmission housing.

[0009] The third planetary gear, the fourth planetary gear and the fifth planetary gear are all provided in plurality, and the fourth planetary gear and the fifth planetary gear are in the same layer.

[0010] The 10-speed AT automatic transmission of the present invention has the following beneficial effects:

[0011] (1) To achieve 10 gears, only a simple planetary gear mechanism and a Ravina-type planetary gear mechanism are needed. The transmission elements are relatively few, the arrangement is compact, the space is small, the cost advantage is obvious, and the space occupied by the transmission is reduced;

[0012] (2) Each gear position only requires two actuators, the shifting logic is clear, and the transmission route is relatively short.

[0013] (3) It has 10 forward gears, which is an advantage in terms of the number of gears;

[0014] (4) Compared with the traditional 8-speed transmission, only one actuator needs to be added, the space does not need to be increased, and the cost increase is limited. Therefore, compared with the existing 10-speed transmission, the cost advantage is obvious. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] This specification includes the following drawings, which show the following contents:

[0016] Figure 1 It is a structural schematic diagram of a 10-speed AT automatic transmission of the present invention;

[0017] Figure 2 It is a schematic diagram of the working state of each component of the 10-speed AT automatic transmission of the present invention at each gear position;

[0018] Figure 3 This is the power transmission route in third gear;

[0019] Figure 4 This is the power transmission route in fourth gear;

[0020] Figure 5 This is the power delivery roadmap in fifth gear;

[0021] Figure 6 This is the power delivery route in sixth gear;

[0022] Figure 7This is the power delivery roadmap in seventh gear;

[0023] Figure 8 It is the power delivery roadmap in eighth gear;

[0024] Marked in the figure: C1, first clutch; C2, second clutch; C3, third clutch; C4, fourth clutch; C5, fifth clutch; B1, first brake; B2, second brake; R1, first ring gear; PC1, first planetary carrier; S1, first sun gear; P1, first planetary gear; P2, second planetary gear; PC2, compound planetary carrier; S2; second sun gear; S3, third sun gear; P3, third planetary gear; P4, fourth planetary gear; P5, fifth planetary gear; R2, second ring gear; R3, third ring gear. DETAILED DESCRIPTION

[0025] The specific implementation methods of the present invention are further explained in detail below by describing the embodiments with reference to the accompanying drawings, with the aim of helping those skilled in the art to have a more complete, accurate and in-depth understanding of the concept and technical solution of the present invention and facilitating its implementation.

[0026] like Figure 1 As shown, the present invention provides a 10-speed AT automatic transmission, including a transmission housing, an input shaft, a first planetary gear mechanism connected to the input shaft, a second planetary gear mechanism, a first clutch C1 connected to the first planetary gear mechanism and the second planetary gear mechanism, a second clutch C2 and a fifth clutch C5 connected to the second planetary gear mechanism and the input shaft, a third clutch C3 and a fourth clutch C4 connected to the first planetary gear mechanism and the second planetary gear mechanism, and a first brake B1 and a second brake B2 connected to the second planetary gear mechanism, and the second planetary gear mechanism is a Ravina type planetary gear mechanism.

[0027] Specifically, if Figure 1As shown, the first planetary gear mechanism includes a first sun gear S1, a first planet carrier PC1 fixedly connected to the input shaft, a first planetary gear P1 and a second planetary gear P2 arranged on the first planet carrier PC1, and a first ring gear R1 meshed with the second planetary gear P2, the first planetary gear P1 is located between the second planetary gear P2 and the first sun gear S1, and the first planetary gear P1 is meshed with the second planetary gear P2 and the first sun gear S1. The first sun gear S1 is fixedly arranged and is always in a fixed state, the first clutch C1 and the third clutch C3 are connected to the first ring gear R1, and the fourth clutch C4 is connected to the first planet carrier PC1. The first planetary gear P1 is located between the first sun gear S1 and the second planetary gear P2, the diameter of the first planetary gear P1 is smaller than the diameter of the second planetary gear P2, and the first planetary gear P1 and the second planetary gear P2 are rotatably arranged on the first planet carrier PC1.

[0028] like Figure 1 As shown, the second planetary gear mechanism includes a second sun gear S2, a third sun gear S3, a compound planet carrier PC2, a third planetary gear P3 meshing with the second sun gear S2, a second ring gear R2 meshing with the third planetary gear P3, a fourth planetary gear P4 meshing with the third sun gear S3, a fifth planetary gear P5 meshing with the fourth planetary gear P4, and a third ring gear R3 meshing with the fifth planetary gear P5, and the third planetary gear P3, the fourth planetary gear P4, and the fifth planetary gear P5 are rotatably arranged on the compound planet carrier PC2. Multiple third planetary gears P3, fourth planetary gears P4, and fifth planetary gears P5 are arranged, the fourth planetary gears P4 and the fifth planetary gears P5 are in the same layer, all third planetary gears P3 are in another layer, the diameter of the fourth planetary gear P4 is smaller than the diameter of the fifth planetary gear P5, and the fourth planetary gear P4 is located between the third sun gear S3 and the fifth planetary gear P5. Each third planetary gear P3 is coaxially arranged with a fifth planetary gear P5 and rotates synchronously. The input shaft is a power input component of the gearbox, and the second ring gear R2 is a power output component of the gearbox.

[0029] like Figure 1As shown, the first clutch C1 is connected to the first ring gear R1 and the third sun gear S3, and the first clutch C1 is used to control the engagement and disengagement between the third sun gear S3 and the first ring gear R1, and the third sun gear S3 and the first ring gear R1 are coaxially arranged. The second clutch C2 is connected to the compound planet carrier PC2 and the input shaft, and the second clutch C2 is used to control the engagement and disengagement between the compound planet carrier PC2 and the input shaft. The third clutch C3 is connected to the first ring gear R1 and the second sun gear S2, and the third clutch C3 is used to control the engagement and disengagement between the first ring gear R1 and the second sun gear S2, and the first ring gear R1 is coaxially arranged with the first sun gear S1, the second sun gear S2 and the third sun gear S3. The fourth clutch C4 is connected to the first planet carrier PC1 and the second sun gear S2, and the fourth clutch C4 is used to control the engagement and disengagement between the first planet carrier PC1 and the second sun gear S2. The fifth clutch C5 is connected to the third ring gear R3 and the input shaft, and the fifth clutch C5 is used to control the engagement and disengagement between the third ring gear R3 and the input shaft. The third ring gear R3 is coaxially arranged with the second ring gear R2 and the input shaft. The first brake B1 is connected to the second sun gear S2 and the transmission housing, and the first brake B1 is used to brake the second sun gear S2. The second brake B2 is connected to the compound planet carrier PC2 and the transmission housing, and the second brake B2 is used to brake the compound planet carrier PC2.

[0030] like Figure 1 and Figure 2 As shown, when the gearbox is in the first gear, the first clutch C1 and the second brake B2 are working, the first clutch C1 is in the engaged state, the second brake B2 is in the braking state, the first clutch C1 connects the third sun gear S3 with the first ring gear R1, the third sun gear S3 and the first ring gear R1 can rotate synchronously, and at the same time the second brake B2 keeps the compound planet carrier PC2 stationary, and the compound planet carrier PC2 cannot rotate.

[0031] The power transmission route when the gearbox is in the first gear is: input shaft → first planet carrier PC1 (first sun gear S1 is fixed) → first ring gear R1 → third sun gear S3 (compound planet carrier PC2 is fixed) → second ring gear R2 → output.

[0032] When the gearbox is in the first gear, after the input shaft rotates, the power of the input shaft is transmitted to the second ring gear R2 through the first planetary carrier PC1, the second planetary gear P2, the first ring gear R1, the third sun gear S3, the fourth planetary gear P4, the fifth planetary gear P5 and the third planetary gear P3 in sequence, and finally the power is output by the second ring gear R2.

[0033] like Figure 1 and Figure 2As shown, when the gearbox is in the second gear, the first clutch C1 and the first brake B1 are working, the first clutch C1 is in the engaged state, the first brake B1 is in the braking state, the first clutch C1 connects the third sun gear S3 with the first ring gear R1, the third sun gear S3 and the first ring gear R1 can rotate synchronously, and at the same time the first brake B1 keeps the second sun gear S2 stationary, and the second sun gear S2 cannot rotate.

[0034] The power transmission route when the gearbox is in the second gear is: input shaft → first planetary carrier PC1 (first sun gear S1 is fixed) → first ring gear R1 → third sun gear S3 (second sun gear S2 is fixed) → second ring gear R2 → output.

[0035] When the gearbox is in the second gear, after the input shaft rotates, the power of the input shaft is transmitted to the second ring gear R2 through the first planetary carrier PC1, the second planetary gear P2, the first ring gear R1, the third sun gear S3, the fourth planetary gear P4, the compound planetary carrier PC2 and the third planetary gear P3 in sequence, and finally the power is output by the second ring gear R2.

[0036] like Figure 1 and Figure 2 As shown, when the gearbox is in the third gear, the first clutch C1 and the third clutch C3 are working, the first clutch C1 and the third clutch C3 are in the engaged state, the first clutch C1 connects the first ring gear R1 and the third sun gear S3, the first ring gear R1 and the third sun gear S3 can rotate synchronously, and at the same time the third clutch C3 connects the first ring gear R1 and the second sun gear S2, the first ring gear R1 and the second sun gear S2 can rotate synchronously, the power is in accordance with Figure 3 route delivery.

[0037] When the gearbox is in the third gear, after the input shaft rotates, the power of the input shaft is transmitted to the second planetary gear mechanism through the first planetary carrier PC1, the second planetary gear P2, and the first ring gear R1 in sequence, causing the second ring gear R2 to rotate, and finally the power is output by the second ring gear R2.

[0038] like Figure 1 and Figure 2 As shown, when the gearbox is in the fourth gear, the first clutch C1 and the fourth clutch C4 are working, the first clutch C1 and the fourth clutch C4 are in the engaged state, the first clutch C1 connects the third sun gear S3 with the first ring gear R1, the third sun gear S3 and the first ring gear R1 can rotate synchronously, and at the same time the fourth clutch C4 connects the first planet carrier PC1 with the second sun gear S2, the first planet carrier PC1 and the second sun gear S2 can rotate synchronously, the power is in accordance with Figure 4 route delivery.

[0039] When the gearbox is in the fourth gear, after the input shaft rotates, the power of the input shaft is divided into two paths. One path is transmitted to the second ring gear R2 through the first planetary carrier PC1, the second planetary gear P2, the first ring gear R1, the third sun gear S3, the fourth planetary gear P4, the fifth planetary gear P5 and the third planetary gear P3 in sequence. The other path is transmitted to the second ring gear R2 through the second sun gear S2 and the third planetary gear P3 in sequence. Finally, the power is output by the second ring gear R2.

[0040] like Figure 1 and Figure 2 As shown, when the gearbox is in the fifth gear, the first clutch C1 and the second clutch C2 are working, the first clutch C1 and the second clutch C2 are in the engaged state, the first clutch C1 connects the third sun gear S3 with the first ring gear R1, the third sun gear S3 and the first ring gear R1 can rotate synchronously, and at the same time, the second clutch C2 connects the compound planetary carrier PC2 with the input shaft, the compound planetary carrier PC2 and the input shaft can rotate synchronously, and the power is in accordance with Figure 5 route delivery.

[0041] When the gearbox is in fifth gear, after the input shaft rotates, the power of the input shaft is divided into two paths. One path is transmitted to the second ring gear R2 via the first planetary carrier PC1 (the first sun gear S1 is fixed), the second planetary gear P2, the first ring gear R1 and the third sun gear S3 in sequence. The other path is transmitted to the second ring gear R2 via the compound planetary carrier PC2 and the third planetary gear P3 in sequence. Finally, the power is output by the second ring gear R2.

[0042] like Figure 1 and Figure 2 As shown, when the gearbox is in the sixth gear, the first clutch C1 and the fifth clutch C5 are working, the first clutch C1 and the fifth clutch C5 are in the engaged state, the first clutch C1 connects the third sun gear S3 with the first ring gear R1, the third sun gear S3 and the first ring gear R1 can rotate synchronously, and at the same time the fifth clutch C5 connects the third ring gear R3 with the input shaft, the third ring gear R3 and the input shaft can rotate synchronously, and the power is in accordance with Figure 6 route delivery.

[0043] When the gearbox is in the sixth gear, after the input shaft rotates, the power of the input shaft is divided into two paths. One path is transmitted to the second ring gear R2 through the third ring gear R3, the fifth planetary gear P5 and the third planetary gear P3 in sequence, and the other path is transmitted to the second ring gear R2 through the first planetary carrier PC1 (the first sun gear S1 is fixed), the first ring gear R1 and the third sun gear S3 in sequence. Finally, the power is output by the second ring gear R2.

[0044] like Figure 1 and Figure 2As shown, when the gearbox is in the seventh gear, the second clutch C2 and the fifth clutch C5 are working, the second clutch C2 and the fifth clutch C5 are in the engaged state, the second clutch C2 connects the compound planetary carrier PC2 and the input shaft, the compound planetary carrier PC2 and the input shaft can rotate synchronously, and the fifth clutch C5 connects the third ring gear R3 and the input shaft, the third ring gear R3 and the input shaft can rotate synchronously, and the power is in accordance with Figure 7 route delivery.

[0045] When the gearbox is in the seventh gear, after the input shaft rotates, the power of the input shaft is divided into two paths. One path is transmitted to the second ring gear R2 through the third ring gear R3, the fifth planetary gear P5 and the third planetary gear P3 in sequence, and the other path is transmitted to the second ring gear R2 through the compound planetary carrier PC2 and the third planetary gear P3 in sequence. Finally, the power is output by the second ring gear R2.

[0046] like Figure 1 and Figure 2 As shown, when the gearbox is in the eighth gear, the third clutch C3 and the fifth clutch C5 are working, the third clutch C3 is in the engaged state, the fifth clutch C5 is in the brake state, the third clutch C3 connects the first ring gear R1 with the second sun gear S2, the first ring gear R1 and the second sun gear S2 can rotate synchronously, and the fifth clutch C5 connects the third ring gear R3 with the input shaft, the third ring gear R3 and the input shaft can rotate synchronously, and the power is in accordance with Figure 8 route delivery.

[0047] When the gearbox is in the eighth gear, after the input shaft rotates, the power of the input shaft is divided into two paths. One path is transmitted to the second ring gear R2 through the first planetary carrier PC1, the second planetary gear P2, the first ring gear R1, the second sun gear S2 and the third planetary gear P3 in sequence. The other path is transmitted to the second ring gear R2 through the third ring gear R3 and the third planetary gear P3 in sequence. Finally, the power is output by the second ring gear R2.

[0048] like Figure 1 and Figure 2 As shown, when the gearbox is in the ninth gear, the fifth clutch C5 and the first brake B1 are working, the fifth clutch C5 is in the engaged state, the first brake B1 is in the braking state, the fifth clutch C5 connects the third ring gear R3 and the input shaft, the third ring gear R3 and the input shaft can rotate synchronously, and at the same time the first brake B1 keeps the second sun gear S2 stationary, and the second sun gear S2 cannot rotate.

[0049] When the gearbox is in the ninth gear, the power transmission route is: input shaft → third ring gear R3 (second sun gear S2 is fixed) → second ring gear R2 → output.

[0050] When the gearbox is in the ninth gear, after the input shaft rotates, the power of the input shaft is transmitted to the second ring gear R2 through the third ring gear R3, the compound planetary carrier PC2 and the third planetary gear P3 in sequence, and finally the power is output by the second ring gear R2.

[0051] like Figure 1 and Figure 2 As shown, when the gearbox is in the tenth gear, the fifth clutch C5 and the second brake B2 are working, the fifth clutch C5 is in an engaged state, the second brake B2 is in a braking state, the fifth clutch C5 connects the third ring gear R3 and the input shaft, the third ring gear R3 and the input shaft can rotate synchronously, and at the same time the second brake B2 keeps the compound planetary carrier PC2 stationary, and the compound planetary carrier PC2 cannot rotate.

[0052] When the gearbox is in the tenth gear, the power transmission route is: input shaft → third ring gear R3 (rear planetary carrier fixed) → second ring gear R2 → output.

[0053] When the gearbox is in the tenth gear, after the input shaft rotates, the power of the input shaft is transmitted to the second ring gear R2 through the third ring gear R3, the fifth planetary gear P5 and the third planetary gear P3 in sequence, and finally the power is output by the second ring gear R2.

[0054] like Figure 1 and Figure 2 As shown, when the gearbox is in the first reverse gear, the third clutch C3 and the second brake B2 are working, the third clutch C3 is in an engaged state, the second brake B2 is in a braking state, the third clutch C3 connects the first ring gear R1 and the second sun gear S2, the first ring gear R1 and the second sun gear S2 can rotate synchronously, and at the same time the second brake B2 fixes the compound planet carrier PC2, and the compound planet carrier PC2 cannot rotate.

[0055] The power transmission route when the gearbox is in the first reverse gear is: input shaft → first planet carrier PC1 (first sun gear S1 is fixed) → first ring gear R1 → second sun gear S2 (compound planet carrier PC2 is fixed) → second ring gear R2 → output.

[0056] When the gearbox is in the first reverse gear, after the input shaft rotates, the power of the input shaft is transmitted to the second ring gear R2 through the first planetary carrier PC1, the first ring gear R1, the second sun gear S2 and the third planetary gear P3 in sequence, and finally the power is output by the second ring gear R2.

[0057] like Figure 1 and Figure 2As shown, when the gearbox is in the second reverse gear, the fourth clutch C4 and the second brake B2 are working, the fourth clutch C4 is in an engaged state, the second brake B2 is in a braking state, the fourth clutch C4 connects the input shaft with the second sun gear S2, the input shaft, the first planet carrier PC1 and the second sun gear S2 can rotate synchronously, and at the same time the second brake B2 fixes the compound planet carrier PC2, and the compound planet carrier PC2 cannot rotate.

[0058] The power transmission route when the gearbox is in the second reverse gear is: input shaft → second sun gear S2 (fixed by compound planet carrier PC2) → second ring gear R2 → output.

[0059] When the gearbox is in the second reverse gear, after the input shaft rotates, the power of the input shaft is transmitted to the second ring gear R2 through the first planetary carrier PC1, the second sun gear S2 and the third planetary gear P3 in sequence, and finally the power is output by the second ring gear R2.

[0060] The present invention is described above by way of example in conjunction with the accompanying drawings. Obviously, the specific implementation of the present invention is not limited to the above-mentioned methods. As long as various non-substantial improvements are made using the method concept and technical solution of the present invention; or the above concept and technical solution of the present invention are directly applied to other occasions without improvement, they are all within the protection scope of the present invention.

Claims

1. 10-speed AT automatic transmission, including input shaft, characterized by: It also includes a first planetary gear mechanism connected to the input shaft, a second planetary gear mechanism, a first clutch connected to the first planetary gear mechanism and the second planetary gear mechanism, a second clutch and a fifth clutch connected to the second planetary gear mechanism and the input shaft, a third clutch and a fourth clutch connected to the first planetary gear mechanism and the second planetary gear mechanism, and a first brake and a second brake connected to the second planetary gear mechanism, wherein the second planetary gear mechanism is a Ravina-type planetary gear mechanism; The first planetary gear mechanism comprises a first sun gear, a first planet carrier connected to the input shaft, a first planetary gear and a second planetary gear arranged on the first planet carrier, and a first ring gear meshed with the second planetary gear, the first planetary gear is located between the second planetary gear and the first sun gear, and the first planetary gear is meshed with the second planetary gear and the first sun gear; The first sun gear is fixed, the first clutch and the third clutch are connected to the first ring gear, and the fourth clutch is connected to the first planet carrier; The second planetary gear mechanism comprises a second sun gear, a third sun gear, a compound planet carrier, a third planetary gear meshed with the second sun gear, a second ring gear meshed with the third planetary gear, a fourth planetary gear meshed with the third sun gear, a fifth planetary gear meshed with the fourth planetary gear, and a third ring gear meshed with the fifth planetary gear, the third planetary gear, the fourth planetary gear and the fifth planetary gear are arranged on the compound planet carrier, the fourth planetary gear is located between the third sun gear and the fifth planetary gear, and each third planetary gear is coaxially arranged with a fifth planetary gear and rotates synchronously; The first clutch is connected to the third sun gear, the second clutch is connected to the input shaft and the compound planetary carrier, the third clutch and the fourth clutch are connected to the second sun gear, the fifth clutch is connected to the third ring gear, the first brake is connected to the second sun gear and the transmission housing, the first brake is used to brake the second sun gear, the second brake is connected to the compound planetary carrier and the transmission housing, and the second brake is used to brake the compound planetary carrier.

2. The 10-speed AT automatic transmission according to claim 1, characterized in that: The third planetary gear, the fourth planetary gear and the fifth planetary gear are all provided in plurality, and the fourth planetary gear and the fifth planetary gear are in the same layer.

3. The 10-speed AT automatic transmission according to claim 1, characterized in that: The diameter of the fourth planetary gear is smaller than the diameter of the fifth planetary gear.

4. The 10-speed AT automatic transmission according to claim 1, characterized in that: The third sun gear and the first ring gear are coaxially arranged.

5. The 10-speed AT automatic transmission according to claim 1, characterized in that: The first ring gear is coaxially arranged with the first sun gear, the second sun gear and the third sun gear.

6. The 10-speed AT automatic transmission according to claim 1, characterized in that: When the gearbox is in the first gear, the first clutch and the second brake work, the first clutch is in an engaged state, the second brake is in a braking state, the first clutch connects the third sun gear with the first ring gear, the third sun gear rotates synchronously with the first ring gear, and the second brake keeps the compound planet carrier stationary, so that the compound planet carrier cannot rotate.

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