CN219969396U - Hybrid system and vehicle - Google Patents

Abstract

The utility model discloses a hybrid system and a vehicle. The first motor and the engine are arranged at intervals and are in transmission connection with the first input shaft; a first clutch is arranged between the planet carrier and the first input shaft to control the connection or disconnection of the planet carrier and the first input shaft, and at least two planet assemblies are arranged on the planet carrier at intervals and are in transmission connection with the planet carrier and the first input shaft; the at least two brake components and the at least two planetary components are arranged in a one-to-one correspondence mode, the brake components comprise a gear ring and a brake, the gear ring is arranged on the outer side of the planetary components and meshed with the planetary components, and the brake selectively locks the gear ring. Therefore, the power transmission route is controlled through the first clutch and the brake, multi-gear multi-mode hybrid driving can be realized, multiple sets of speed ratios are provided, and the requirements of low-speed starting power performance and high-speed cruising economy can be simultaneously met.

Description

Hybrid system and vehicle

Technical Field

The utility model relates to the technical field of vehicles, in particular to a hybrid system and a vehicle.

Background

Along with the increasing requirements of the state on the economy and the emission of automobiles, the research and development investment of various large main engine factories and part factories on the hybrid power transmission architecture is also increased, and the popular hybrid power architecture in the market at present is a transverse DHT (hybrid power dedicated transmission) and is relatively few.

In the related art, the single gear DHT has a small speed ratio under the pure electric high-speed running condition, and in order to maintain a high vehicle speed, the motor rotation speed must be increased, so that the power consumption is increased, the system efficiency is reduced, and the economical efficiency is reduced.

Disclosure of Invention

The present utility model aims to solve at least one of the technical problems existing in the prior art. Therefore, the utility model provides a hybrid system, and a vehicle with the hybrid system can realize multi-gear and multi-mode hybrid driving and improve economy.

The utility model further provides a vehicle.

A mixing system according to an embodiment of the present utility model includes: an engine; the first input shaft is in transmission connection with the engine; the first motor is arranged at intervals with the engine and is in transmission connection with the first input shaft; a first clutch is arranged between the planet carrier and the first input shaft to control the connection or disconnection of the planet carrier and the first input shaft; the planetary assemblies are arranged on the planet carrier at intervals and are in transmission connection with the planet carrier and the first input shaft; at least two brake components, at least two brake components and at least two planetary components correspond to each other and set up, brake components includes: a ring gear disposed outside of and in engagement with the planetary assembly, and a brake that selectively locks the ring gear.

Therefore, the power transmission route is controlled through the first clutch and the brake, multi-gear multi-mode hybrid driving can be realized, multiple sets of speed ratios are provided, and the requirements of low-speed starting power performance and high-speed cruising economy can be simultaneously met.

According to some embodiments of the utility model, the first input shaft comprises: the planetary gear transmission device comprises a first shaft body, a second shaft body and a second clutch, wherein the engine is in transmission connection with the first shaft body, the planet carrier is in transmission connection with the second shaft body through the first clutch, and the first shaft body is in transmission connection with the second shaft body through the second clutch.

According to some embodiments of the utility model, the planetary assembly is two, both of which include: the sun gear and the second shaft body coaxially rotate, and the planet wheel is sleeved on the planet carrier and meshed between the sun gear and the gear ring.

According to some embodiments of the utility model, the first motor is disposed on the first shaft.

According to some embodiments of the utility model, the first motor is disposed on the second shaft.

According to some embodiments of the utility model, the first motor is disposed on the planet carrier.

According to some embodiments of the utility model, the planet carrier is provided with a first output shaft; and, the mixing system further comprises: the transmission shaft is in transmission connection with the first output shaft and in transmission connection with the first differential mechanism.

According to some embodiments of the utility model, further comprising: the second differential mechanism is arranged on the rear axle and is in transmission connection with the first output shaft.

According to some embodiments of the utility model, further comprising: a rear axle assembly, the rear axle assembly comprising: the second motor is arranged on the second input shaft and is in transmission connection with the second input shaft.

A vehicle according to an embodiment of the second aspect of the utility model includes the hybrid system.

Additional aspects and advantages of the utility model will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the utility model.

Drawings

The foregoing and/or additional aspects and advantages of the utility model will become apparent and may be better understood from the following description of embodiments taken in conjunction with the accompanying drawings in which:

FIG. 1 is a schematic diagram of a front axle of a hybrid system according to an embodiment of the utility model;

FIG. 2 is a schematic diagram of a rear axle of a hybrid system according to an embodiment of the utility model;

FIG. 3 is a schematic diagram II of a front axle of a hybrid system according to an embodiment of the utility model;

FIG. 4 is a schematic diagram II of a rear axle of a hybrid system according to an embodiment of the utility model;

FIG. 5 is a shift logic schematic of a hybrid system according to an embodiment of the present utility model;

FIG. 6 is a schematic diagram of a front axle of an alternative embodiment of a hybrid system in accordance with an embodiment of the present utility model;

FIG. 7 is a schematic diagram of a rear axle of an alternative embodiment of a hybrid system in accordance with an embodiment of the utility model;

FIG. 8 is a schematic diagram of an alternative embodiment second front axle of a hybrid system in accordance with an embodiment of the utility model;

FIG. 9 is a schematic diagram of an alternative embodiment second rear axle of the hybrid system in accordance with an embodiment of the present utility model;

FIG. 10 is a schematic diagram of an alternative embodiment III of a hybrid system in accordance with an embodiment of the utility model;

FIG. 11 is a schematic diagram of an alternate embodiment fourth front axle of a hybrid system in accordance with an embodiment of the utility model;

FIG. 12 is a schematic diagram of an alternate embodiment fourth rear axle of the hybrid system in accordance with an embodiment of the utility model;

FIG. 13 is a schematic diagram of an alternative embodiment fifth front axle of a hybrid system in accordance with an embodiment of the utility model;

FIG. 14 is a schematic diagram of an alternative embodiment fifth rear axle of the hybrid system in accordance with an embodiment of the utility model;

FIG. 15 is a schematic diagram of an alternative embodiment sixth front axle of a hybrid system in accordance with an embodiment of the utility model;

FIG. 16 is a schematic diagram of an alternative embodiment sixth rear axle of a hybrid system in accordance with an embodiment of the utility model;

fig. 17 is a schematic diagram of an alternative embodiment seven of a hybrid system in accordance with an embodiment of the utility model.

Reference numerals:

100. a mixing system;

10. an engine;

20. a first input shaft; 21. a first clutch; 22. a first shaft body; 23. a second shaft body; 24. a second clutch;

30. a first motor;

40. a planet carrier; 41. a first output shaft; 42. a first output drive gear; 43. a first output driven gear;

50. a first planetary assembly; 51. a second planetary assembly; 52. a first sun gear; 53. a first planet; 54. a second sun gear; 55. a second planet wheel;

60. a brake assembly; 61. a first ring gear; 62. a second ring gear; 63. a first brake; 64. a second brake;

70. a transmission shaft; 71. a first differential; 72. a main reduction driving gear; 73. a driving and subtracting driven gear;

80. a second differential;

90. a rear axle assembly; 91. a second input shaft; 92. a second output shaft; 93. a second motor; 94. a second output drive gear; 95. the second output driven gear.

Detailed Description

Embodiments of the present utility model will be described in detail below, by way of example with reference to the accompanying drawings.

A hybrid system 100 according to an embodiment of the present utility model is described below with reference to fig. 1-17, and a vehicle is also proposed.

Referring to fig. 1 and 3, a hybrid system 100 in accordance with an embodiment of the present utility model includes an engine 10, a first input shaft 20, a first electric machine 30, a planet carrier 40, at least two planetary assemblies, and at least two brake assemblies 60.

First, the first input shaft 20 is in driving connection with the engine 10, and the first motor 30 is disposed at a distance from the engine 10 and in driving connection with the first input shaft 20. The engine 10 is provided in the front axle, and may be used as a power input source, a charging source, or no function, that is, as shown in fig. 5, the engine 10 does not generate driving force when the vehicle is in the electric-only mode, and the engine 10 may directly supply driving force to the vehicle or may supply power to the vehicle when the vehicle is in the hybrid mode.

Specifically, through the transmission connection between the engine 10 and the first motor 30 by the first input shaft 20, the first motor 30 and the engine 10 are arranged at intervals, when the vehicle is in the hybrid four-wheel drive mode, power is transmitted to the first input shaft 20 through the engine 10, driving force is directly provided for the vehicle, when the vehicle is in the series range-extending mode, power is transmitted to the first input shaft 20 through the engine 10, and then transmitted to the first motor 30 to charge a battery, and the battery discharges to generate driving force for the vehicle, so that the multi-mode hybrid driving can be realized, the whole vehicle is strong in power and high in trafficability.

And a first clutch 21 is arranged between the planet carrier 40 and the first input shaft 20 to control connection or disconnection of the planet carrier 40 and the first input shaft 20, and at least two planet assemblies are arranged on the planet carrier 40 at intervals and are in transmission connection with the planet carrier 40 and the first input shaft 20. That is, the first clutch 21 is provided between the carrier 40 and the first input shaft 20, and can control connection or disconnection of the carrier 40 and the first input shaft 20, and at least two planetary assemblies are provided on the carrier 40 at intervals, the two planetary assemblies being divided into a first planetary assembly 50 and a second planetary assembly 51, the two planetary assemblies being in driving connection with the carrier 40 and the first input shaft 20. According to the characteristics of the planetary gear, any two elements are combined together, and the whole planetary gear is integrated, so that the connection and disconnection of the planetary carrier 40 and the first input shaft 20 are controlled through the first clutch 21, a power transmission route can be controlled, multi-gear driving is realized, and the requirements of low-speed starting dynamic property and high-speed cruising economy can be simultaneously met.

Specifically, referring to fig. 5, when the vehicle is in the four-wheel drive mode 2, the first clutch 21 is engaged, the carrier 40 is connected to the first input shaft 20, and therefore, the two carrier 40 assemblies and the carrier 40 are also connected together, the power transmission does not pass through the split planetary rows, and the power is directly transmitted downward after being transmitted to the first input shaft 20 by the first motor 30. And when the vehicle is in the hybrid four-drive mode 2 gear, the first clutch 21 is combined, the planet carrier 40 is connected with the first input shaft 20, the two planet carrier 40 assemblies are also connected with the planet carrier 40, the power transmission path of the first motor 30 is the same as that of the pure four-drive mode 2 gear, the power of the engine 10 is transmitted to the first input shaft 20, and the power is directly transmitted downwards without being split through a planet row.

And at least two brake assemblies 60 and at least two planetary assemblies are arranged in a one-to-one correspondence, the brake assemblies 60 comprise a gear ring and a brake, the gear ring is arranged on the outer side of the planetary assemblies and is meshed with the planetary assemblies, and the brake selectively locks the gear ring. That is, at least two brake assemblies 60 and at least two planetary assemblies are provided in one-to-one correspondence, the brake assemblies 60 include a ring gear and a brake, wherein the ring gear is located at the outer side of the planetary assemblies, and the brake is divided into a first brake 63 and a second brake 64, the ring gear is divided into a first ring gear 61 and a second ring gear 62, and the ring gear is braked and disconnected by the brake, so that different gear outputs of the transmission can be realized.

Specifically, referring to FIG. 5, when the vehicle is in the four-wheel drive mode 1, the second brake 64 is engaged with the second ring gear 62, power is transmitted from the first electric machine 30 to the first input shaft 20, to the second planetary assembly 51, to the carrier 40, and when the vehicle is in the four-wheel drive mode 3, the first brake 63 is engaged with the first ring gear 61, power is transmitted from the first electric machine 30 to the first input shaft 20, to the first planetary assembly 50, and to the carrier 40. Likewise, when the vehicle is in the hybrid four-drive mode 1 gear, the second brake 64 is engaged with the second ring gear 62, the power transmission path of the first motor 30 is the same as that of the pure four-drive mode 1 gear, the power of the engine 10 is transmitted to the first input shaft 20 and then to the second planetary assembly 51 and then to the carrier 40, when the vehicle is in the hybrid four-drive mode 3 gear, the first brake 63 is engaged with the first ring gear 61, the power transmission path of the first motor 30 is the same as that of the pure four-drive mode 3 gear, the power of the engine 10 is transmitted to the first input shaft 20 and then to the first planetary assembly 50 and then to the carrier 40.

Therefore, the power transmission route is controlled through the first clutch 21 and the brake, multi-gear multi-mode hybrid driving can be realized, multiple sets of speed ratios are provided, and the requirements of low-speed starting power performance and high-speed cruising economy can be simultaneously met.

Referring to fig. 1 and 3, the first input shaft 20 includes a first shaft body 22, a second shaft body 23, and a second clutch 24, the engine 10 is in driving connection with the first shaft body 22, the carrier 40 is in driving connection with the second shaft body 23 through the first clutch 21, and the first shaft body 22 is in driving connection with the second shaft body 23 through the second clutch 24. That is, the engine 10 is connected to the first shaft 22, the first shaft 22 is connected to the second clutch 24, the second clutch 24 is connected to the second shaft 23, the second shaft 23 is connected to the first clutch 21, and the first clutch 21 is connected to the carrier 40. Wherein the second clutch 24 can control the connection and disconnection of the first input shaft 20 and the second input shaft 91, that is, the connection and disconnection of the engine 10 and the second input shaft 91, multi-mode hybrid driving can be realized.

Specifically, referring to FIG. 5, when the vehicle is in the four-wheel-drive-only mode, the second clutch 24 is disengaged and the engine 10 is not engaged in the transmission operating process. When the vehicle is in the hybrid four-wheel drive mode, the engine 10 also serves as a power input source, and the second clutch 24 is engaged, so that power is transmitted from the engine 10 to the first shaft 22, then to the second clutch 24, and then to the second shaft 23. And, when the vehicle is in the series range-extending mode, the second clutch 24 is engaged, power is transmitted to the first shaft 22 via the engine 10, then transmitted to the second clutch 24, then transmitted to the second shaft 23, and then transmitted to the first motor 30 to charge the battery, so that the battery is discharged to generate power, and the power is continuously transmitted through the first motor 30.

Referring to fig. 3, there are two planetary assemblies, each including a sun gear and a planetary gear, the sun gear and the second shaft 23 coaxially rotate, and the planetary gear is sleeved on the planet carrier 40 and meshed between the sun gear and the ring gear. That is, there are two planetary assemblies composed of a sun gear and a planet gear, the first planetary assembly 50 includes a first sun gear 52 and a first planet gear 53, and the second planetary assembly 51 includes a second sun gear 54 and a second planet gear 55.

Wherein the first planet gears 53 mesh with the first sun gear 52 and the first ring gear 61 simultaneously, and the second planet gears 55 mesh with the second sun gear 54 and the second ring gear 62 simultaneously.

And, the first planetary gears 53 are sleeved on the planetary carrier 40, and the second planetary gears 55 are sleeved on the planetary carrier 40.

And, the first sun gear 52 and the second sun gear 54 are fixedly connected with the first input shaft 20, so that in the power transmission process of the hybrid system 100, a specific transmission path of the first input shaft 20 to the planetary assembly is that the first input shaft 20 is transmitted to the first sun gear 52, then to the first planet gears 53 and then to the planet carrier 40, or alternatively, the first input shaft 20 is transmitted to the second sun gear 54, then to the second planet gears 55 and then to the planet carrier 40.

And, the first sun gear 52, the first planet gears 53, the first ring gear 61 and the planet carrier 40 form a first planet row, the second sun gear 54, the second planet gears 55, the second ring gear 62 and the planet carrier 40 form a second planet row, and compared with the traditional parallel shaft type structure, the first planet row and the second planet row have small structural space size and large bearing torque.

Referring to fig. 6, a first motor 30 is provided on the first shaft body 22. That is, in an alternative embodiment of the present utility model, the first motor 30 may be further disposed on the first shaft body 22, where the first motor 30 is located between the engine 10 and the second clutch 24, and the disconnection and connection of the first shaft body 22 and the second shaft body 23 are controlled by the second clutch 24, so that the disconnection and connection of the engine 10 and the first motor 30 cannot be controlled, and thus, the vehicle with the four-wheel drive architecture has only a hybrid mode, and when the second clutch 24 is combined, the engine 10 and the first motor 30 operate simultaneously to jointly provide power for the vehicle, or the engine 10 provides power for the first motor 30, and the first motor 30 provides driving force.

When the first motor 30 is disposed on the first shaft 22, a longitudinal frame structure or a transverse frame structure may be adopted.

Referring to fig. 8, the first motor 30 is disposed on the second shaft body 23. That is, in an alternative embodiment of the present utility model, the first motor 30 may also be provided on the second shaft body 23, with the first motor 30 being located between the second clutch 24 and the first clutch 21, the first output shaft 41 being connected to the rear axle, and the rear axle 90 being provided with no motor, so that the front axle and the rear axle assembly 40 of the four-wheel drive vehicle are driven by the first motor 30 together.

When the first motor 30 is disposed on the second shaft 23, a vertical frame structure or a horizontal frame structure may be adopted.

Referring to fig. 10, the first motor 30 is provided on the carrier 40. That is, in an alternative embodiment of the present utility model, the first motor 30 may be further disposed on the carrier 40, and at this time, the second clutch 24 only controls connection between the engine 30 and the second shaft 23, so as to switch between the pure mode and the hybrid mode, the first clutch 21 controls connection and disconnection between the carrier 40 and the first input shaft 20, so as to switch between different modes, and the first motor 30 provides driving force for the vehicle.

And, when the first motor 30 is disposed on the planet carrier 40, a longitudinal frame structure may be adopted or a transverse frame structure may be adopted.

Referring to fig. 1 and 3, a first output shaft 41 is provided on the carrier 40. The first output shaft 41 includes a first output driving gear 42 and a first output driven gear 43, the first output driving gear 42 and the first output driven gear 43 are meshed with each other, and the first output shaft 41 and the first output driven gear 43 are fixedly connected with the carrier 40.

And, the hybrid system 100 further includes a drive shaft 70 and a first differential 71, the drive shaft 70 being drivingly connected to the first output shaft 41 and being drivingly connected to the first differential 71. The transmission shaft 70 further includes a main reduction driving gear 72 and a main reduction driven gear 73, the main reduction driving gear 72 is meshed with the main reduction driven gear 73, the transmission shaft 70 is fixedly connected with the first output driven gear 43 and the main reduction driving gear 72, and the differential is fixedly connected with the main reduction driven gear 73.

Then, during the power transmission of the hybrid system 100, the power may be transmitted from the planet carrier 40 to the first output shaft 41, to the first output driving gear 42, to the first output driven gear 43, to the transmission shaft 70, to the main reduction driving gear 72, to the main reduction driven gear 73, and to the differential, and of course, when the entire planet row is integrated, that is, in the 2-gear in the pure or hybrid mode, the power is transmitted to the first input shaft 20, then directly to the first output shaft 41, to the first output driving gear 42, to the first output driven gear 43, to the transmission shaft 70, to the main reduction driving gear 72, to the main reduction driven gear 73, and to the differential.

Referring to fig. 10 and 17, the hybrid system 100 further includes a second differential 80, the second differential 80 being disposed on the rear axle and in driving connection with the first output shaft 41. That is, in an alternative embodiment of the present utility model, a second differential 80 is also included, the second differential 80 being located in the rear axle and being in driving connection with the first output shaft 41 such that power may be transmitted from the first output shaft 41 to the second differential 80.

Referring to fig. 2 and 4, the hybrid system 100 further includes a rear axle assembly 90, the rear axle assembly 90 including a second input shaft 91, a second output shaft 92, and a second motor 93, the second motor 93 being disposed on the second input shaft 91 and the second output shaft 92 being drivingly connected. The second input shaft 91 further includes a second output driving gear 94 and a second output driven gear 95, the second output driving gear 94 is meshed with the second output driven gear 95, the second output driving gear 94 and the second motor 93 are fixedly connected with the second input shaft 91, and the second output driven gear 95 is fixedly connected with the second output shaft 92.

Specifically, by providing the second input shaft 91, the second output shaft 92, and the second motor 93, the power transmission path of the rear axle assembly 90 is such that power is transmitted to the second input shaft 91 via the second motor 93, then to the second output driving gear 94, then to the second output driven gear 95, and then to the second output shaft 92.

The hybrid system 100 further includes other modes of starting the engine 10, idle charging, and braking energy recovery, wherein the power transmission path for starting the engine 10 is that power is transmitted from the first motor 30 to the second shaft 23, then to the second clutch 24, then to the first shaft 22, and then to the engine 10.

The power transmission path for idle charging is that power is transmitted from the engine 10 to the first shaft 22, to the second clutch 24, to the second shaft 23, and to the first motor 30. The power transmission path for braking energy recovery is the reverse transmission of a pure four-driving-force path.

And, the four-wheel drive and the four-wheel drive modes are all provided with R gear, and the power transmission path of the R gear reverses the first motor 30 and the second motor 93, and the other is unchanged.

Also, in the embodiment of the present utility model, that is, the first motor 30 is located between the second clutch 24 and the first clutch 21, a longitudinal frame structure may be adopted or a transverse frame structure may be adopted.

A vehicle according to an embodiment of the second aspect of the utility model includes a hybrid system 100.

In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present utility model and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present utility model.

In the description of the present specification, reference to the terms "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the utility model. In this specification, schematic representations of the above terms do not necessarily refer to the same embodiments or examples.

While embodiments of the present utility model have been shown and described, it will be understood by those of ordinary skill in the art that: many changes, modifications, substitutions and variations may be made to the embodiments without departing from the spirit and principles of the utility model, the scope of which is defined by the claims and their equivalents.

Claims (10)

1. A hybrid system, comprising:

an engine (10);

-a first input shaft (20), said first input shaft (20) being in driving connection with said engine (10);

the first motor (30) is arranged at intervals with the engine (10) and is in transmission connection with the first input shaft (20);

a planet carrier (40), a first clutch (21) is arranged between the planet carrier (40) and the first input shaft (20) to control the connection or disconnection of the planet carrier (40) and the first input shaft (20);

at least two planetary assemblies, at least two of which are arranged on the planet carrier (40) at intervals and are in transmission connection with the planet carrier (40) and the first input shaft (20);

at least two brake assemblies (60), at least two brake assemblies (60) and at least two planetary assemblies are arranged in a one-to-one correspondence, and the brake assemblies (60) comprise: a ring gear disposed outside of and in engagement with the planetary assembly, and a brake that selectively locks the ring gear.

2. The hybrid system according to claim 1, wherein the first input shaft (20) comprises: the planetary gear transmission device comprises a first shaft body (22), a second shaft body (23) and a second clutch (24), wherein the engine (10) is in transmission connection with the first shaft body (22), the planet carrier (40) is in transmission connection with the second shaft body (23) through the first clutch (21), and the first shaft body (22) is in transmission connection with the second shaft body (23) through the second clutch (24).

3. The hybrid system of claim 2, wherein the planetary assemblies are two, each of the planetary assemblies comprising: the sun gear and the second shaft body (23) rotate coaxially, and the planet gears are sleeved on the planet carrier (40) and meshed between the sun gear and the gear ring.

4. The hybrid system according to claim 2, wherein the first motor (30) is arranged on the first shaft body (22).

5. A hybrid system according to claim 2, wherein the first motor (30) is arranged on the second shaft body (23).

6. A hybrid system according to claim 2, wherein the first motor (30) is arranged on the planet carrier (40).

7. A hybrid system according to claim 1, wherein the planet carrier (40) is provided with a first output shaft (41); the method comprises the steps of,

the mixing system further comprises: the transmission shaft (70) is in transmission connection with the first output shaft (41) and is in transmission connection with the first differential (71), and the transmission shaft (70) is in transmission connection with the first differential (71).

8. The hybrid system as set forth in claim 7, further comprising: and the second differential mechanism (80) is arranged on the rear axle and is in transmission connection with the first output shaft (41).

9. The hybrid system as set forth in claim 7, further comprising: a rear axle assembly (90), the rear axle assembly (90) comprising: the device comprises a second input shaft (91), a second output shaft (92) and a second motor (93), wherein the second motor (93) is arranged on the second input shaft (91) and is in transmission connection with the second input shaft (91) and the second output shaft (92).

10. A vehicle, characterized by comprising: the hybrid system of any one of claims 1-9.