Hybrid transmission, hybrid vehicle and control method of hybrid transmission

Abstract

The invention provides a hybrid power gearbox, a hybrid power automobile and a control method of the hybrid power gearbox. The hybrid power gearbox comprises an input shaft capable of being connected with an engine and an output shaft used for outputting power and further comprises a first motor and a second motor, a first compound planet row is arranged between the first motor and the second motor, and a second compound planet row is arranged between the second motor and the first compound planet row. A second compound planet row is arranged between the second motor and the output shaft, the first compound planet row comprises a first sub planet row and a second sub planet row, the first sub planet row is provided with a first sun gear, a first planet carrier and a first gear ring, and the second sub planet row is provided with a second sun gear, a second planet carrier and a second gear ring; the first sun gear and the second gear ring are connected or integrally arranged; the hybrid gearbox further comprises four brakes, the first brake is matched with the first gear ring, and the second brake is matched with the second sun gear. The third brake and the fourth brake are used for being matched with the second compound planet row. According to the scheme, the internal space arrangement can be optimized, and more working modes can be realized.

Description

Technical Field

[0001] The present invention relates to the technical field of power systems, and in particular to a hybrid transmission, a hybrid vehicle, and a control method for the hybrid transmission. Background Art

[0002] Hybrid transmissions are widely used in current vehicle models. The motor of a hybrid transmission can have a power generation mode and a driving mode. In the driving mode, it provides power together with the engine. In the power generation mode, it is driven by the engine to generate electricity, or it can recover energy for power generation.

[0003] There are many types of hybrid transmissions on the market, and relatively speaking, there are fewer types of longitudinal hybrid transmissions. Summary of the invention

[0004] The purpose of the present application is to provide a hybrid transmission, a hybrid vehicle and a control method for a hybrid transmission, which can optimize the internal space layout and realize more working modes.

[0005] The present application provides a hybrid transmission, comprising an input shaft that can be connected to an engine and an output shaft for outputting power, and also comprising a first motor and a second motor, wherein a first group of compound planetary rows is arranged between the first motor and the second motor, and a second group of compound planetary rows is arranged between the second motor and the output shaft, wherein the first group of compound planetary rows comprises a first sub-planetary row and a second sub-planetary row, wherein the first sub-planetary row comprises a first sun gear, a first planet carrier and a first ring gear, and the second sub-planetary row comprises a second sun gear, a second planet carrier and a second ring gear, and the first sun gear and the second ring gear are connected or integrally arranged;

[0006] The hybrid transmission also includes four brakes, namely a first brake, a second brake, a third brake and a fourth brake. The first brake cooperates with the first ring gear, and the second brake cooperates with the second sun gear. The third brake and the fourth brake are used to cooperate with the second group of compound planetary gears.

[0007] In a specific embodiment, the first sun gear has an outer ring gear and an inner ring gear, the outer ring gear is meshed with the first planet carrier, and the inner ring gear forms the second ring gear.

[0008] In a specific implementation, the first sun gear and the second ring gear are welded or connected by fasteners.

[0009] In a specific embodiment, the second group of compound planetary gears includes a third sub-planetary gear and a fourth sub-planetary gear, the third sub-planetary gear has a third sun gear, a third planetary carrier and a third ring gear, the fourth sub-planetary gear has a fourth sun gear, a fourth planetary carrier and a fourth ring gear, the third planetary carrier is connected to the fourth ring gear, and the fourth planetary carrier is connected to the third ring gear.

[0010] In a specific implementation, the third sun gear cooperates with the third brake, and the fourth ring gear cooperates with the fourth brake.

[0011] The present application also provides a hybrid vehicle, comprising the hybrid transmission described in any one of the above items.

[0012] The present application also provides a control method for a hybrid transmission, wherein an input shaft of the hybrid transmission is connected to an engine via a clutch, and at least one of the following modes is achieved by controlling the first brake, the second brake, the third brake, the fourth brake, and the clutch:

[0013] Series mode: the clutch is engaged, the first motor is in a generating condition, the second motor is in a driving condition, and the four brakes are disconnected;

[0014] Direct drive / parallel mode: engage the clutch, disengage two of the four brakes, and engage the other two;

[0015] Single-motor pure electric mode: the clutch is disconnected, the first motor is turned off, the second motor is in driving condition, the first brake and the second brake are disconnected, one of the third brake and the fourth brake is engaged, and the other is disconnected;

[0016] Dual-motor pure electric mode: The clutch is disconnected, the first motor and the second motor are both in driving condition, the second brake and the fourth brake are combined, or the second brake and the third brake are combined;

[0017] Energy recovery mode: the clutch is disconnected, the four brakes are disconnected, the first motor is turned off, and the second motor is in a power generation state.

[0018] The first group of compound planetary rows in the present application is equivalent to a small planetary row embedded in the sun gear of a large planetary row, that is, the first sub-planetary row is a large planetary row, the second sub-planetary row is a small planetary row, and the first sun gear serves as the second ring gear of the small planetary row. In this way, the first group of compound planetary rows in this embodiment has a shorter axial length, which can save axial space. Moreover, the transmission ratio range of the first group of compound planetary rows in this structural form is larger, which is convenient for adjustment. In addition, the hybrid transmission in the present application can also realize series mode, direct drive / parallel mode, single-motor pure electric mode, dual-motor pure electric mode, and energy recovery mode.

[0019] The hybrid vehicle and hybrid transmission control method provided in the present application have the same technical effects as the above-mentioned hybrid transmission. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] Figure 1 A schematic diagram of a hybrid transmission in an embodiment of the present application;

[0021] Figure 2 for Figure 1 Schematic diagram of the force transmission path of the hybrid transmission in series mode;

[0022] Figure 3 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in direct drive / parallel mode and in 1st gear;

[0023] Figure 4 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in direct drive / parallel mode and in 2nd gear;

[0024] Figure 5 for Figure 1 Schematic diagram of the power transmission path when the hybrid transmission is in direct drive / parallel mode and in 3rd gear;

[0025] Figure 6 for Figure 1 Schematic diagram of the power transmission path when the hybrid transmission is in direct drive / parallel mode and in 3rd gear;

[0026] Figure 7 for Figure 1 Schematic diagram of the power transmission path when the hybrid transmission is in single-motor pure electric mode and in 1st gear;

[0027] Figure 8 for Figure 1 Schematic diagram of the power transmission path when the hybrid transmission is in single-motor pure electric mode and in 2nd gear;

[0028] Fig. 9 for Figure 1 Schematic diagram of the power transmission path when the hybrid transmission is in dual-motor pure electric mode and in 1st gear;

[0029] Fig.10 for Figure 1 Schematic diagram of the power transmission path when the hybrid transmission is in dual-motor pure electric mode and in 2nd gear;

[0030] Fig.11 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in energy recovery mode and in 1st gear;

[0031] Fig.12 for Figure 1Schematic diagram of the force transmission path when the hybrid transmission is in energy recovery mode and in 2nd gear.

[0032] Figures 1 to 12 The reference numerals in the drawings are described as follows:

[0033] 11-first sun gear; 12-first planet carrier; 13-first ring gear;

[0034] 21- second sun gear; 22- second planet carrier; 23- second ring gear;

[0035] 31-third sun gear; 32-third planet carrier; 33-third ring gear;

[0036] 41- fourth sun gear; 42- fourth planet carrier; 43- fourth ring gear;

[0037] D-first brake; C-second brake; A-third brake; B-fourth brake;

[0038] in-input shaft; out-output shaft;

[0039] C0-clutch;

[0040] GS4-first sub-planetary gear; GS3-second sub-planetary gear; GS2-third sub-planetary gear; GS4-fourth sub-planetary gear;

[0041] P2-first motor; P2.5-second motor. DETAILED DESCRIPTION

[0042] In order to enable those skilled in the art to better understand the present application, the present application is further described in detail below in conjunction with the accompanying drawings and specific implementation methods.

[0043] Please refer to Figure 1 , Figure 1 is a schematic diagram of a hybrid transmission in an embodiment of the present application. It can be seen that: Figure 1 Shows half of the hybrid transmission structure, omitting and Figure 1 The other half of radial symmetry.

[0044] The hybrid transmission in this embodiment includes a first motor P2, a second motor P2.5, an input shaft in and an output shaft out, and also includes four brakes, namely a first brake D, a second brake C, a third brake A and a fourth brake B. The input shaft in is directly connected to the engine, specifically to the flywheel of the engine. The first motor P2 is connected to the input shaft in through a clutch C0, a compound planetary gear is provided between the first motor P2 and the second motor P2.5, defined as a first group of compound planetary gears, and a compound planetary gear is provided between the second motor P2.5 and the output shaft out, defined as a second group of compound planetary gears, and each group of compound planetary gears includes two sub-planetary gears.

[0045] like Figure 1 As shown, the first group of compound planetary rows includes a first sub-planetary row GS4 and a second sub-planetary row GS3, the first sub-planetary row GS4 includes a first sun gear 11, a first planet carrier 12, and a first ring gear 13, and the second sub-planetary row GS3 includes a second sun gear 21, a second planet carrier 22, and a second ring gear 23, wherein the first ring gear 13 is connected to the first brake D, the second sun gear 21 is connected to the second brake C, and the first sun gear 11 and the second ring gear 23 are connected or integrated. The hybrid transmission also includes a transmission shaft, the output end of the first group of compound planetary rows is the first sun gear 11, and the first sun gear 11 and the second ring gear 23 are both connected to the transmission shaft.

[0046] It should be emphasized that the first group of composite planetary rows in the present embodiment is equivalent to a small planetary row embedded in the sun gear of a large planetary row. Specifically, the first sub-planetary row GS4 is a large planetary row, the second sub-planetary row GS3 is a small planetary row, and the first sun gear 11 is the second gear ring 23 of the small planetary row, that is, the second gear ring 23 is embedded in the first sun gear 11. The two can be completely flush in the axial direction, or at least partially overlap. In this way, the first group of composite planetary rows has a shorter axial length, which can save axial space. The first sun gear 11 and the second gear ring 23 can be fixed by welding, or fastened by fasteners. The two can also be an integrated structure, that is, the first sun gear 11 has an outer gear ring and an inner gear ring. The outer gear ring is used to mesh with the first planet carrier 12, and the inner gear ring is used as the second gear ring 23. This is more convenient to process, the first sun gear 11 and the second gear ring 23 are highly integrated, and the structural stability is more reliable. At this time, combined with Figure 1 It is understood that when the first sun gear 11 and the second ring gear 23 are an integrated structure, the outer ring gear and the inner ring gear of the first sun gear 11 can share a base portion, and the outer ring gear and the inner ring gear are flush in the axial direction.

[0047] Let's look at the second group of compound planetary gears, which include the third sub-planetary gear GS2 and the fourth sub-planetary gear GS1, wherein the third sub-planetary gear GS2 includes the third sun gear 31, the third planetary carrier 32, and the third ring gear 33, and the fourth sub-planetary gear GS1 includes the fourth sun gear 41, the fourth planetary carrier 42, and the fourth ring gear 43. Among them, the third sun gear 31 is connected to the third brake A, the fourth ring gear 43 and the third planetary carrier 32 are connected to the fourth brake B, the transmission shaft is connected to the fourth sun gear 41, the third planetary carrier 32 is connected to the fourth ring gear 43 or is integrally arranged, and the fourth planetary carrier 42 is connected to the third ring gear 33 or is integrally arranged. The output end of the second group of compound planetary gears is the fourth planetary carrier 42, and the fourth planetary carrier 42 is connected to the output shaft out.

[0048] The structure of the second group of compound planetary gears is simpler than that of the first group of compound planetary gears. The structural dimensions of the two sub-planetary gears can be the same, except that the third gear ring 33 and the fourth planet carrier 42 are connected, and the third planet carrier 32 and the fourth gear ring 43 are connected. Relatively speaking, the first group of compound planetary gears has a larger transmission ratio adjustment range. At this time, the second group of compound planetary gears with a simple structure and a relatively small transmission ratio in the entire transmission system can meet the application requirements of the transmission ratio. Of course, the second group of compound planetary gears can also adopt other structural forms, such as the structure of the second group of compound planetary gears is the same as that of the first group of compound planetary gears.

[0049] It should be known that each sub-planetary gear has three planetary units, namely the sun gear, the ring gear and the planetary carrier. Each sub-planetary gear has two degrees of freedom. The two units of the two sub-planetary gears in each compound planetary gear are connected, so that the entire compound planetary gear still has two degrees of freedom. Each compound planetary gear is equipped with two brakes. Any brake can be combined to eliminate one degree of freedom, so that the compound planetary gear can realize power input and output.

[0050] In this embodiment, since two sets of compound planetary gears are provided, the hybrid transmission structure can realize multiple working modes by changing the connection state of each set of compound planetary gears with the brake, and the working state of the engine and the two motors. For understanding, please refer to the following Table 1, which shows the working mode and gear comparison of the hybrid transmission in this embodiment.

[0051] Table 1

[0052]

[0053]

[0054] As can be seen from the above table, the hybrid transmission in this embodiment has five operating modes, namely series mode, direct drive / parallel mode, single-motor pure electric mode, dual-motor pure electric mode, and energy recovery mode. The force transmission path of each mode is explained in turn below.

[0055] Series Mode:

[0056] like Figure 2 As shown, Figure 2 for Figure 1 Schematic diagram of the force transmission path of the hybrid transmission in series mode. The force transmission path is indicated by dotted arrows.

[0057] In this working mode, the clutch C0 is in the engaged ON state, the first motor P2 is in the power generation state, the second motor P2.5 is in the driving state, and the four brakes are all in the OFF disconnected state, that is, they are all in the non-braking state, and each unit of the two sets of compound planetary gears is not constrained. At this time, the power of the engine can be transmitted to the input shaft in through the clutch C0, and the input shaft in rotates to drive the first motor P2 to generate electricity, and the first planetary carrier 12 and the second planetary carrier 22 of the first set of compound planetary gears are idling. At the same time, the second motor P2.5 is connected to the transmission shaft, and the power of the second motor P2.5 is transmitted to the transmission shaft, and the transmission shaft then transmits the power to the fourth sun gear 41, the fourth planetary carrier 42, and the output shaft out in sequence.

[0058] Direct drive / parallel mode:

[0059] Please refer to Figure 3 , Figure 3 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in direct drive / parallel mode and in 1st gear. The force transmission path is indicated by dotted arrows.

[0060] 1st gear: the clutch C0 is in the ON state of engagement, the first motor P2 is in the power generation condition or in the OFF condition, the second motor P2.5 is in the driving condition or in the OFF condition, the second brake C and the fourth brake B are both in the ON working state, that is, in the braking state, the first brake D and the third brake A are both in the OFF disconnected state, that is, in the non-braking state, at this time, the second sun gear 21 in the first group of compound planetary gears is constrained by the second brake C, the first ring gear 13 is not constrained by the first brake D, the fourth ring gear 43 and the third planet carrier 32 in the second group of compound planetary gears are constrained by the fourth brake B, and the third sun gear 31 is not constrained by the third brake A. At this time, the second motor P2.5 can be driven in conjunction with the engine, or the second motor P2.5 is in the OFF state and driven by the engine alone.

[0061] Please refer to Figure 4 , Figure 4 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in direct drive / parallel mode and in 2nd gear. The force transmission path is indicated by dotted arrows.

[0062] 2nd gear: the clutch C0 is in the ON state of engagement, the first motor P2 is in the power generation condition or in the OFF condition, the second motor P2.5 is in the driving condition or in the OFF condition, the second brake C and the third brake A are both in the ON working state, that is, in the braking state, the fourth brake B and the first brake are both in the OFF disconnected state, that is, in the non-braking state, at this time, the second sun gear 21 in the first group of compound planetary gears is constrained by the second brake C, the first ring gear 13 is not constrained by the first brake D, the third sun gear 31 in the second group of compound planetary gears is constrained by the third brake A, and the fourth ring gear 43 and the third planet carrier 32 are not constrained by the fourth brake B. At this time, the second motor P2.5 can be driven in conjunction with the engine, or the second motor P2.5 is in the OFF state and driven by the engine alone.

[0063] Please refer to Figure 5 , Figure 5 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in direct drive / parallel mode and in 3rd gear. The force transmission path is indicated by dotted arrows.

[0064] 3rd gear: the clutch C0 is in the ON state of engagement, the first motor P2 is in the power generation condition or in the OFF condition, the second motor P2.5 is in the driving condition or in the OFF condition, the first brake D and the fourth brake B are both in the ON working state, that is, in the braking state, the second brake C and the third brake A are both in the OFF disconnected state, that is, in the non-braking state, at this time, the first ring gear 13 in the first group of compound planetary gears is constrained by the first brake D, the second sun gear 21 is not constrained by the second brake C, the fourth ring gear 43 and the third planet carrier 32 in the second group of compound planetary gears are constrained by the fourth brake B, and the third sun gear 31 is not constrained by the third brake A. At this time, the second motor P2.5 can be driven in conjunction with the engine, or the second motor P2.5 is in the OFF state and driven by the engine alone.

[0065] Please refer to Figure 6 , Figure 6 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in direct drive / parallel mode and in 3rd gear. The force transmission path is indicated by dotted arrows.

[0066] 4th gear: the clutch C0 is in the ON state of engagement, the first motor P2 is in the power generation condition or in the OFF condition, the second motor P2.5 is in the driving condition or in the OFF condition, the first brake D and the third brake A are both in the ON working state, that is, in the braking state, the second brake C and the fourth brake B are both in the OFF disconnected state, that is, in the non-braking state, at this time, the first ring gear 13 in the first group of compound planetary gears is constrained by the first brake D, the second sun gear 21 is not constrained by the second brake C, the third sun gear 31 in the second group of compound planetary gears is constrained by the third brake A, and the fourth ring gear 43 and the third planet carrier 32 are not constrained by the fourth brake B. At this time, the second motor P2.5 can be driven in conjunction with the engine, or the second motor P2.5 is in the OFF state and driven by the engine alone.

[0067] Single motor pure electric mode:

[0068] Please refer to Figure 7 , Figure 7 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in single-motor pure electric mode and in 1st gear. The force transmission path is indicated by dotted arrows.

[0069] Gear 1: The clutch C0 is in the disconnected OFF state, the engine provides no power, the first motor P2 is in the OFF state, the second motor P2.5 is in the driving state, and only the fourth brake B among the four brakes is in the ON working state. The fourth ring gear 43 and the third planetary carrier 32 in the second group of compound planetary gears are constrained by the fourth brake B, and the third sun gear 31 is not constrained by the third brake A.

[0070] Please refer to Figure 8 , Figure 8 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in single-motor pure electric mode and in 2nd gear. The force transmission path is indicated by dotted arrows.

[0071] Gear 2: The clutch C0 is in the disconnected OFF state, the engine provides no power, the first motor P2 is in the OFF state, the second motor P2.5 is in the driving state, and only the third brake A among the four brakes is in the ON working state. The third sun gear 31 in the second group of compound planetary gears is constrained by the third brake A, and the fourth ring gear 43 and the third planetary carrier 32 are not constrained by the fourth brake B.

[0072] Dual-motor pure electric mode:

[0073] Please refer to Fig. 9 , Fig. 9 for Figure 1Schematic diagram of the force transmission path when the hybrid transmission is in dual-motor pure electric mode and in 1st gear. The force transmission path is indicated by dotted arrows.

[0074] Gear 1: The clutch C0 is in the disconnected OFF state, the engine does not provide power, the first motor P2 and the second motor P2.5 are both in the driving condition, and among the four brakes, only the second brake C and the fourth brake B are in the ON working state. The second sun gear 21 in the first group of compound planetary gears is constrained by the second brake C, and the first ring gear 13 is not constrained by the first brake D. The fourth ring gear 43 and the third planetary carrier 32 in the second group of compound planetary gears are constrained by the fourth brake B, and the third sun gear 31 is not constrained by the third brake A.

[0075] Please refer to Fig.10 , Fig.10 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in dual-motor pure electric mode and in 2nd gear. The force transmission path is indicated by dotted arrows.

[0076] Gear 2: The clutch C0 is in the disconnected OFF state, the engine does not provide power, the first motor P2 and the second motor P2.5 are both in the driving condition, and among the four brakes, only the second brake C and the third brake A are in the ON working state. The second sun gear 21 in the first group of compound planetary gears is constrained by the second brake C, the first ring gear 13 is not constrained by the first brake D, the fourth ring gear 43 and the third planetary carrier 32 in the second group of compound planetary gears are not constrained by the fourth brake B, and the third sun gear 31 is constrained by the third brake A.

[0077] Energy recovery mode:

[0078] Please refer to Fig.11 and Fig.12 , Fig.11 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in energy recovery mode and in 1st gear. The force transmission path is indicated by dotted arrows; Fig.12 for Figure 1 Schematic diagram of the force transmission path when the hybrid transmission is in energy recovery mode and in 2nd gear. The force transmission path is indicated by dotted arrows.

[0079] Gear 1: In this operating mode, the clutch C0 is in the disconnected OFF state, the engine does not provide power, the first motor P2 is in the OFF shutdown condition, and among the four brakes, the fourth brake B is in the ON working state, the first brake C, the second brake D and the third brake A are all in the OFF disconnected state, and only the first motor P2 is in the generating condition.

[0080] Gear 2: In this operating mode, the clutch C0 is in the disconnected OFF state, the engine does not provide power, the first motor P2 is in the OFF shutdown condition, and among the four brakes, the third brake A is in the ON working state, the first brake C, the second brake D and the fourth brake B are all in the OFF disconnected state, and only the first motor P2 is in the generating condition.

[0081] The embodiment of the present application also provides a hybrid vehicle, including the above hybrid gearbox, which has the same technical effects as the above embodiment. The hybrid gearbox in this embodiment can be a longitudinal gearbox, that is, the hybrid gearbox and the engine are distributed longitudinally and can be arranged behind the engine.

[0082] Specific examples are used herein to illustrate the principles and implementation methods of the present application, and the description of the above embodiments is only used to help understand the method and core ideas of the present application. It should be pointed out that for ordinary technicians in this technical field, without departing from the principles of the present application, several improvements and modifications can be made to the present application, and these improvements and modifications also fall within the scope of protection of the claims of the present application.

Claims

1. A hybrid transmission, characterized in that: The invention comprises an input shaft that can be connected to an engine and an output shaft for outputting power, and also comprises a first motor and a second motor, a first group of compound planetary rows is arranged between the first motor and the second motor, a second group of compound planetary rows is arranged between the second motor and the output shaft, the first group of compound planetary rows comprises a first sub-planetary row and a second sub-planetary row, the first sub-planetary row comprises a first sun gear, a first planet carrier and a first ring gear, the second sub-planetary row comprises a second sun gear, a second planet carrier and a second ring gear, and the first sun gear and the second ring gear are connected or integrally arranged; The hybrid transmission also includes four brakes, namely a first brake, a second brake, a third brake and a fourth brake. The first brake cooperates with the first ring gear, and the second brake cooperates with the second sun gear. The third brake and the fourth brake are used to cooperate with the second group of compound planetary gears.

2. The hybrid transmission according to claim 1, characterized in that: The first sun gear has an outer ring gear and an inner ring gear, the outer ring gear is meshed with the first planet carrier, and the inner ring gear forms the second ring gear.

3. The hybrid transmission according to claim 1, characterized in that: The first sun gear and the second ring gear are welded or connected by fasteners.

4. The hybrid transmission according to any one of claims 1 to 3, characterized in that: The second group of compound planetary gears includes a third sub-planetary gear and a fourth sub-planetary gear, the third sub-planetary gear has a third sun gear, a third planetary carrier and a third ring gear, the fourth sub-planetary gear has a fourth sun gear, a fourth planetary carrier and a fourth ring gear, the third planetary carrier is connected to the fourth ring gear, and the fourth planetary carrier is connected to the third ring gear.

5. The hybrid transmission according to claim 4, characterized in that: The third sun gear cooperates with the third brake, and the fourth ring gear cooperates with the fourth brake.

6. A hybrid vehicle, characterized in that: Including the hybrid transmission described in any one of claims 1-5.

7. A control method for a hybrid transmission, wherein the input shaft of the hybrid transmission is connected to the engine through a clutch, characterized in that: By controlling the first brake, the second brake, the third brake, the fourth brake and the clutch, at least one of the following modes is achieved: Series mode: the clutch is engaged, the first motor is in a generating condition, the second motor is in a driving condition, and the four brakes are disconnected; Direct drive / parallel mode: the clutch is engaged, one of the first brake and the second brake is engaged and the other is disconnected; and one of the third brake and the fourth brake is engaged and the other is disconnected; Single-motor pure electric mode: the clutch is disconnected, the first motor is turned off, the second motor is in driving condition, the first brake and the second brake are disconnected, one of the third brake and the fourth brake is engaged, and the other is disconnected; Dual-motor pure electric mode: The clutch is disconnected, the first motor and the second motor are both in driving condition, the second brake and the fourth brake are combined, or the second brake and the third brake are combined; Energy recovery mode: the clutch is disconnected, the third brake and the fourth brake are disconnected, one of the first brake and the second brake is engaged and the other is disconnected, the first motor is disconnected, and the second motor is in a power generation state.

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