CN106915240B

CN106915240B - Power driving system and vehicle with same

Info

Publication number: CN106915240B
Application number: CN201510991351.8A
Authority: CN
Inventors: 廉玉波; 凌和平; 翟震; 郑峰; 徐友彬
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2015-12-25
Filing date: 2015-12-25
Publication date: 2020-08-07
Anticipated expiration: 2035-12-25
Also published as: WO2017107847A1; CN106915240A

Abstract

The invention discloses a power driving system and a vehicle. The power drive system includes: power coupling device, power coupling device includes: the first sun gear, the first planet carrier and the first gear ring as well as the second sun gear, the second planet carrier and the second gear ring are coaxially connected; a middle shaft arranged to be linked with the first gear ring and the second gear ring; an engine configured to selectively engage the intermediate shaft; a first motor generator, a second motor generator and a third motor generator, the first motor generator being linked with the first sun gear, the second motor generator being linked with the second sun gear, the third motor generator being provided to be selectively linked with the engine; a first braking device for directly or indirectly braking the intermediate shaft. The power driving system of the invention realizes the differential function on the premise of canceling the traditional mechanical differential, and has rich transmission modes.

Description

Power driving system and vehicle with same

Technical Field

The invention relates to the technical field of automobiles, in particular to a power driving system and a vehicle with the same.

Background

In a related art concerning a transmission for a vehicle, which is known to the inventors, the transmission is provided with a pair of differential mechanisms having a sun gear, a planetary carrier, and an annular gear, and a pair of motors. The engine is input to the sun gears of the differential mechanisms after being shifted by the intermediate transmission structure. The pair of motors input driving forces to the ring gears of the pair of differential mechanisms, respectively. The transmission device cancels the traditional mechanical differential element and utilizes two groups of planetary gear mechanisms to realize the coupling of the power of two motors and an engine.

However, the transmission device is suitable for working vehicles (such as snow sweeper), the motor output mechanism is a worm gear mechanism, unidirectional motor power transmission is realized through self-locking, only the unidirectional motor power transmission is acted on steering differential when the vehicle is bent, and working conditions such as pure electric, hybrid power and parking power generation cannot be realized.

Disclosure of Invention

The present invention is directed to solving, at least to some extent, one of the above-mentioned problems in the prior art.

The invention provides a power driving system, which realizes a differential function on the premise of canceling a traditional mechanical differential and has abundant transmission modes.

The invention also provides a vehicle which is provided with the power driving system.

A power drive system according to an embodiment of the present invention includes: a power coupling device, the power coupling device comprising: the planetary gear set comprises a first sun gear, a first planet carrier, a first gear ring, a second sun gear, a second planet carrier and a second gear ring, wherein the first gear ring is coaxially connected with the second gear ring; an intermediate shaft arranged to be linked with the first and second gear rings; an engine configured to selectively engage the intermediate shaft; a first motor generator, a second motor generator and a third motor generator, the first motor generator being linked with the first sun gear, the second motor generator being linked with the second sun gear, the third motor generator being provided to be selectively linked with the engine; a first braking device for directly or indirectly braking the intermediate shaft.

The power driving system according to the embodiment of the invention realizes the differential function on the premise of canceling the traditional mechanical differential, and has rich transmission modes.

According to another aspect embodiment of the invention, the vehicle comprises the power driving system in the above embodiment.

Drawings

FIG. 1 is a schematic illustration of a power drive system according to an embodiment of the present invention;

FIG. 2 is a partial schematic view of the power drive system of FIG. 1, illustrating primarily the power coupling portion;

FIG. 3 is a schematic illustration of a power drive system according to another embodiment of the present invention;

FIG. 4 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

5-15 are partial schematic views of a power drive system according to an embodiment of the present invention, a schematic portion of which may be used as a vehicle rear drive;

fig. 16-17 are schematic views of a vehicle according to an embodiment of the invention.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the drawings are illustrative and intended to be illustrative of the invention and are not to be construed as limiting the invention.

In the description of the present invention, it is to 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", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention.

Furthermore, the terms "first", "second" and "first" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of the present invention, "a plurality" means at least two, e.g., two, three, etc., unless specifically limited otherwise.

In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically connected, electrically connected or can communicate with each other; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.

A power drive system 1000 according to an embodiment of the present invention will be described below with reference to the drawings, the power drive system 1000 being applied to a vehicle 10000 such as a hybrid vehicle 10000, the power drive system 1000 being capable of serving as a power source of the vehicle 10000 and providing power required for normal running of the vehicle 10000.

The power drive system 1000 is described in detail below in connection with the embodiments of fig. 1-4.

Referring to fig. 1 in conjunction with fig. 2, a power drive system 1000 according to an embodiment of the present invention may include a power coupling device 100, an intermediate shaft 61, a first motor generator 51, a second motor generator 52, a third motor generator 53, an engine 54, and a first brake device 41.

The power coupling apparatus 100 will be described in detail first with reference to the accompanying drawings.

Referring to fig. 2, the power coupling device 100 includes a first sun gear 11, a first carrier 14 and a first ring gear 13, a second sun gear 21, a second carrier 24 and a second ring gear 23. Among them, the first sun gear 11, the first carrier 14, and the first ring gear 13 may constitute a main body portion of the planetary gear mechanism 1, and the second sun gear 21, the second carrier 24, and the second ring gear 23 may constitute a main body portion of the planetary gear mechanism 2.

The first planetary gears 12 are mounted on a first carrier 14 and are arranged between the first sun gear 11 and the first ring gear 13, and the first planetary gears 12 are meshed with the first sun gear 11 and the first ring gear 13, respectively. The first planetary gears 12 may be mounted on the first carrier 14 by a planetary gear shaft, and the first planetary gears 12 may be plural and uniformly spaced along the circumferential direction of the first sun gear 11, for example, in view of power transmission stability and manufacturing cost, the first planetary gears 12 may be three and uniformly spaced outside the first sun gear 11, and adjacent two first planetary gears 12 are spaced by about 120 °.

The first planetary gear 12 meshes with the first sun gear 11 in an external engagement manner. The first planetary gears 12 mesh with the first ring gear 13 in an inner mesh manner, that is, teeth are formed on the inner circumferential surface of the first ring gear 13, and the first planetary gears 12 mesh with the teeth on the inner circumferential surface of the first ring gear 13. The first planetary gear 12 can rotate on the axis of the planetary gear shaft, and can also revolve around the first sun gear 11.

Similarly, referring to fig. 2, the second planet gears 22 are mounted on a second planet carrier 24 and are arranged between the second sun gear 21 and the second ring gear 23, the second planet gears 22 being in mesh with the second sun gear 21 and the second ring gear 23, respectively. The second planetary gears 22 may be mounted on the second planet carrier 24 through a planetary gear shaft, the second planetary gears 22 may be multiple and evenly distributed along the circumferential direction of the second sun gear 21, for example, in view of power transmission stability and manufacturing cost, the second planetary gears 22 may be three and evenly distributed on the outer side of the second sun gear 21, and adjacent two second planetary gears 22 are spaced by about 120 °.

The second planetary gears 22 mesh with the second sun gear 21 in an external manner. The second planetary gears 22 mesh with the second ring gear 23 in an inner mesh manner, that is, teeth are formed on the inner circumferential surface of the second ring gear 23, and the second planetary gears 22 mesh with the teeth on the inner circumferential surface of the second ring gear 23. The second planetary gear 22 may rotate on the axis of the planetary gear shaft or may revolve around the second sun gear 21.

The first gear ring 13 and the second gear ring 23 are coaxially connected, so that the first gear ring 13 and the second gear ring 23 act synchronously, that is, the motion states of the first gear ring 13 and the second gear ring 23 are kept consistent at any moment, for example, the first gear ring 13 and the second gear ring 23 rotate at the same speed and in the same direction. As an embodiment, the first ring gear 13 and the second ring gear 23 may be formed as an integral structure, thereby constituting a common ring gear 1323 and being common to both the planetary gear mechanisms 1, 2.

In other embodiments, as shown in fig. 1 to 4, the power coupling device 100 may further include a power transmission portion 3, the power transmission portion 3 is coaxially linked with the first ring gear 13 and the second ring gear 23, in other words, the power transmission portion 3 is coaxially arranged with the first ring gear 13 and the second ring gear 23, and the power transmission portion 3 is capable of being linked with the first ring gear 13 and the second ring gear 23 so as to move synchronously.

Of course, it should be understood that there are many ways to achieve the same motion state (e.g., same direction and same speed rotation) of the first ring gear 13 and the second ring gear 23, and the first ring gear 13 and the second ring gear are integrated to form the common ring gear 1323 as described herein. Alternatively, the first ring gear 13 and the second ring gear 23 may be connected by other means, such as by the power transmission portion 3 described above, and the power transmission portion 3 is fixed to the first ring gear 13 and the second ring gear 23 by the ring gear connecting portion 31. Furthermore, the above two ways can be combined, that is, as shown in the embodiment of fig. 1 to 3, the first ring gear 13 and the second ring gear 23 are not only integrated to form the common ring gear 1323, but also the first ring gear 13 and the second ring gear 23 are fixed with the central power transmission portion 3 through the ring gear connecting portion 31.

It should be noted that the above-mentioned "linkage" may be understood as a linkage movement of a plurality of members (for example, two members), and in the case of linkage of two members, when one member moves, the other member also moves.

For example, in some embodiments of the present invention, a gear in communication with a shaft may be understood such that when the gear rotates, the shaft in communication therewith will also rotate, or when the shaft rotates, the gear in communication therewith will also rotate.

As another example, a shaft is coupled to a shaft is understood to mean that when one of the shafts rotates, the other shaft coupled thereto will also rotate.

As another example, gears may be understood to be geared with one gear so that when one gear rotates, the other gear that is geared with it will also rotate.

Of course, it should be understood that the two parts of the linkage may be relatively stationary with one part being relatively stationary, and the other part being relatively stationary therewith.

Referring to fig. 1 and 3, the intermediate shaft 61 is provided to be interlocked with the first ring gear 13 and the second ring gear 23. The manner in which the intermediate shaft 61 is linked with the first and second ring gears 13, 23 will be described below in connection with specific embodiments.

The engine 54 is configured to selectively engage the intermediate shaft 61, wherein when the engine 54 engages the intermediate shaft 61, power transmission is enabled between the engine 54 and the intermediate shaft 61, the engine 54 is coupled to the intermediate shaft 61, when the engine 54 does not engage the intermediate shaft 61, the engine 54 is disconnected from the intermediate shaft 61, and the engine 54 and the intermediate shaft 61 are not in motion in a related manner.

The first motor generator 51 is coupled to the first sun gear 11, and if the first motor generator 51 and the first sun gear 11 can be coaxially connected, the first motor generator 51 can be located at one end of the first sun gear 11.

The second motor generator 52 is linked with the second sun gear 21, and if the second motor generator 52 and the second sun gear 21 can be coaxially connected, the second motor generator 52 can be located at one end of the second sun gear 21.

The third motor generator 53 is provided to be selectively interlocked with the engine 54, the engine 54 is engaged with the third motor generator 53 when the engine 54 is interlocked with the third motor generator 53, power can be transmitted between the engine 54 and the third motor generator 53, and the engine 54 is not associated with the third motor generator 53 when the engine 54 is disconnected from the third motor generator 53.

Therefore, the power driving system 1000 according to the embodiment of the present invention has at least four power sources, i.e. three motors and engines, so that the transmission mode and the transmission efficiency of the power driving system 1000 are greatly enriched, and the specific typical operating conditions will be described in detail below with reference to the specific embodiment, which will not be described herein.

Here, it should be noted that in the description of the present invention regarding "motor generator", if not specifically stated, the motor generator may be understood as a motor having a function of a generator and a motor.

The first brake device 41 is provided to brake the intermediate shaft 61, and the first brake device 41 may directly brake the intermediate shaft 61 or may indirectly brake the intermediate shaft 61. It is to be understood that in the context of the present invention, the term "braking" is to be understood broadly, i.e. to mean either direct braking or indirect braking, when one component (e.g. a brake or brake, etc.) is braking another component.

When the first braking device 41 brakes the intermediate shaft 61, since the intermediate shaft 61 is linked with the first gear ring 13 and the second gear ring 23, braking of the first gear ring 13 and the second gear ring 23 is also achieved by the braking action of the first braking device 41. In other words, in these embodiments, the first brake device 41 indirectly achieves the braking action on the first ring gear 13 and the second ring gear 23 through the braking action on the intermediate shaft 61. It will of course be appreciated that the first braking device 41 may also be arranged to brake the first ring gear 13 and the second ring gear 23 directly, thus indirectly braking the intermediate shaft 61.

The first and second

planetary carriers

14 and 24 of the power coupling device 100 may serve as power output ends of the power coupling device 100, so that when the first brake device 41 brakes the intermediate shaft 61, the first motor generator 51 may output the generated power to the corresponding wheel, for example, the left wheel 73, through the first planetary carrier 14, and the second motor generator 52 may output the generated power to the corresponding wheel, for example, the right wheel 74, through the second planetary carrier 24.

At this time, the

wheels

73 and 74 on both sides are associated with the first motor generator 51 and the second motor generator 52, respectively, and the rotational speeds of the two wheels can be independently controlled by controlling the rotational speeds of the first motor generator 51 and the second motor generator 52, thereby realizing the differential principle.

For example, when the vehicle 10000 runs on a flat road surface and advances in a straight line, the first motor generator 51 and the second motor generator 52 may output power at the same rotational speed, so that the rotational speeds obtained by the respective wheels are theoretically equal by the decelerating action of the respective planetary gear mechanisms, thereby ensuring that the vehicle 10000 can smoothly travel in a straight line.

For another example, when the vehicle 10000 runs on an uneven road or turns, the rotation speeds of the wheels on both sides theoretically have a rotation speed difference, taking a left turn as an example, the turning radius of the left wheel 73 is smaller and the turning radius of the right wheel 74 is larger, in order to ensure that the wheels roll with the ground, the rotation speed of the left wheel 73 is smaller than the rotation speed of the right wheel 74, at this time, the output rotation speed of the first motor generator 51 may be smaller than the output rotation speed of the second motor generator 52, and the specific rotation speed difference may be indirectly calculated by the steering angle of the steering wheel, for example, the driver rotates the steering wheel counterclockwise (turns left) by a certain angle, the controller of the vehicle 10000 may calculate the turning radius of the vehicle 10000 based on the steering angle, after the turning radius of the vehicle 10000 is determined, the relative rotation speed difference between the wheels on both sides may also be determined, at this time, the controller may control the first motor generator 51 and the second motor generator 52 to output power at the matched rotation speeds respectively, the speed difference between the two wheels can be matched with the speed difference required by the wheels, so that the two wheels can obtain expected speeds after the speed reduction action of the two planetary gear mechanisms, and the pure rolling turning running is realized.

The above description has been given by taking the first motor generator 51 and the second motor generator 52 as the motors as an example, but it is needless to say that the first motor generator 51 and the second motor generator 52 may also operate as generators, for example, to recover the wheel braking energy.

In particular, when the engine 54 is disconnected from the intermediate shaft 61 and the third motor generator 51 is engaged with the engine 54 at this time to be interlocked with the engine 54, the engine 54 can drive the third motor generator 53 to generate power, whereby the power transmission path is short and the charging efficiency is high, and it is understood that the wheels are disconnected from the engine 54 at this time, if the vehicle is in a parking state at this time, the parking power generation function is realized, or the first motor generator 51 and the second motor generator 52 function as motor-driven wheels, the running power generation function is realized at this time.

In addition, when the engine 54 is engaged with the intermediate shaft 61 and the third motor generator 51 is also engaged with the engine 54, the engine 54 and the three motors can be mixed, at this time, the three motors, particularly the third motor generator 53, can adjust the rotating speed of the engine 54, compensate the torque of the engine 54, enable the engine 54 to be in the optimal working range, improve the fuel economy, and the first motor generator 51 and the second motor generator 52 can adaptively and frequently change the rotating speed, thereby realizing the transient regulation of the rotating speed of the wheels, and improving the dynamic property, the stability and the safety of the vehicle.

It will be appreciated that the planetary gear mechanisms 1 and 2 described above may employ the same gear ratio, for example, two planetary gear mechanisms may employ the same gear ratio with the sun gear as the power input and the planet carriers (first planet carrier 14 and second planet carrier 24) as the power output. That is, the numbers of teeth of the first sun gear 11 and the second sun gear 21, the numbers of teeth of the first planetary gear 12 and the second planetary gear 22, and the numbers of teeth (internal teeth) of the first ring gear 13 and the second ring gear 23 may be respectively the same.

In summary, according to the power drive system 1000 of the embodiment of the present invention, the braking action of the first braking device 41 can realize the pure electric mode or the braking energy recovery mode of the first motor generator 51 and the second motor generator 52, and the output rotation speeds of the first motor generator 51 and the second motor generator 52 are controlled individually, so that the wheels on both sides can obtain different torques, and the differential function can be realized. When the braking action of the first braking device 41 is released, the third motor generator 53 and the engine 54 may also intervene and be coupled with the first motor generator 51 and the second motor generator 52 to output power to the outside, so as to significantly improve the dynamic performance and the passing performance of the power driving system 1000.

In addition, since the power of the first motor generator 51 and the power of the second motor generator 52 are respectively input from the first sun gear 11 and the second sun gear 21, the power of the engine 54 is input from the first ring gear 13 and the second ring gear 23, and the power of the power coupling device 100 is finally output from the first planet carrier 14 and the second planet carrier 24, the power is input and output in a mode that the first motor generator 51 and the second motor generator 52 can obtain a better transmission speed ratio under different working conditions, and the driving efficiency of the first motor generator 51 and the second motor generator 52 when serving as motors and the power generation efficiency when serving as generators are improved.

The specific transmission relationship among the engine 54, the third motor generator 53, and the intermediate shaft 61 will be described in detail below with reference to the embodiment.

Referring to fig. 1 and 3, clutches are provided between the engine 54 and the third motor generator 53 and between the engine 54 and the intermediate shaft 61, that is, the engagement and disengagement of the engine 54 and the third motor generator 53 may be achieved by one clutch, and the engagement and disengagement of the engine 54 and the intermediate shaft 61 may be achieved by the other clutch.

In order to reduce the number of parts, reduce the manufacturing cost, and improve the module integration, the engine 54 and the third motor generator 53, and the two clutches between the engine 54 and the intermediate shaft 61, for example, the dual clutch 42, may be integrated.

Referring to fig. 1 and 3, the dual clutch 42 includes: a first engaging portion 421, a second engaging portion 422, and a third engaging portion 423, wherein the first engaging portion 421 and the second engaging portion 422 may be two driven discs of the dual clutch 42, and the third engaging portion 423 may be a housing of the dual clutch 42, at least one of the two driven discs being selectively engageable with the housing, that is, at least one of the first engaging portion 421 and the second engaging portion 422 may be selectively engageable with the third engaging portion 423. Of course, both driven disks may also be completely disconnected from the housing, i.e. both the first 421 and second 422 engagement portions are in a disconnected state from the third engagement portion 423.

The motor 54 is linked with the third engagement portion 423, e.g., the motor 54 is coaxially connected with the third engagement portion 423, and the intermediate shaft 61 is linked with the first engagement portion 421, e.g., the intermediate shaft 61 may be coaxially connected with the first engagement portion 421.

The third motor generator 53 is linked with the second coupling portion 422. referring to the embodiment of fig. 1, the third motor generator 53 is linked with the second coupling portion 422 through a gear mechanism, which may include a gear 531 and a gear 532, the gear 532 may be coaxially connected with the second coupling portion 422, the gear 532 is idly sleeved on the intermediate shaft 61, the gear 531 is fixed on the motor shaft of the third motor generator 53, the gear 531 is meshed with the gear 532, wherein a hollow shaft 533 may be disposed between the second coupling portion 422 and the gear 532, and the hollow shaft 533 is idly sleeved on the intermediate shaft 61. In the embodiment of fig. 1, the third motor generator 53 is located on one side of the double clutch 42.

Referring to the embodiment of fig. 3-4, the third motor generator 53 is arranged coaxially with the dual clutch 42, and the dual clutch 42 is located inside the third motor generator 53, that is, the third motor generator 53 is located radially outside the dual clutch 42, and as a preferred embodiment, the dual clutch 42 is housed inside a housing of the third motor generator 53, more specifically, the dual clutch 42 is housed inside a rotor of the third motor generator 53. In this embodiment, the connection structure of the third motor generator 53 and the second engagement portion 422 may still adopt the corresponding structure in the embodiment of fig. 1, and the description thereof is omitted. For the motor arrangement in the embodiments of fig. 3 and 4, the axial size of the power driving system 1000 can be greatly reduced, and the requirement of the power driving system 1000 for the axial arrangement space is reduced.

The transmission between the intermediate shaft 61 and the first and second ring gears 13, 23 will be described in detail with reference to the embodiment of fig. 1.

In this embodiment, as shown in fig. 1 and 3, the intermediate shaft 61 is linked with the first ring gear 13 and the second ring gear 23 via an intermediate transmission 62. For the intermediate transmission 62, one skilled in the art can flexibly design based on spatial layout requirements, transmission ratio requirements, transmission reliability requirements, and the like.

As an alternative embodiment, the intermediate transmission 62 may be a gear transmission, the gear transmission 62 comprising an intermediate shaft fixed gear 621 and an external tooth portion 622. The external teeth 622 are coaxially linked with the first ring gear 13 and the second ring gear 23, in other words, the external teeth 622 are coaxially arranged with the first ring gear 13 and the second ring gear 23, and the external teeth 622 and the first ring gear 13 and the second ring gear 23 can be linked to move synchronously, i.e., rotate in the same direction and at the same speed. Alternatively, the external teeth portion 622, the first ring gear 13, and the second ring gear 23 may be formed as an integral structure, with the external teeth portion 622 being located on the outer peripheral surface of the common ring gear 1323.

An intermediate shaft fixed gear 621 is fixedly provided on the intermediate shaft 61, and the intermediate shaft fixed gear 621 meshes with the external teeth portion 622. Thus, the intermediate transmission device 62 has a simple structure, reliable transmission, low requirement for spatial arrangement, easy implementation and effective control of manufacturing cost.

Of course, in other embodiments, the intermediate Transmission 62 may also be a belt Transmission, a chain Transmission, or a CVT (Continuously Variable Transmission, such as a Continuously Variable Transmission) Transmission, or the like.

In order to make the power drive system 1000 more compact and smaller, this can be improved by an integrated design of the components, for example, the power transmission unit 3 and the intermediate shaft 61 are manufactured as an integral structure, and further, the power transmission unit 3 and the intermediate shaft 61 can be constructed as the same component. In other words, in this embodiment, it can be understood that the intermediate shaft 61 is coaxially fixed with the first and second ring gears 13 and 23, such as by fixedly connecting the intermediate shaft 61 with the first and second ring gears 13 and 23 through the ring gear connecting portion 31.

Referring to fig. 3, at this time, the intermediate shaft 61 and the power transmission shaft 3 are the same component, the engine 51 and the shaft are coaxially arranged, and the third motor generator 53 is arranged at the radial outer side of the double clutch 42, so that the axial size and the radial size of the power driving system 1000 are greatly reduced by adopting the arrangement mode, the power driving system 1000 tends to be miniaturized, the occupied size is smaller, the requirement on the arrangement space is lower, meanwhile, the lightweight design is realized, the mass of the whole vehicle is reduced, and the fuel economy of the engine 54 is improved.

Referring to fig. 3 and 4, further, a first brake device 41 is disposed between the double clutch 42 and the power coupling device 100.

In some embodiments, the power transmission portion 3 may be configured as a power transmission shaft, the first ring gear 13 and the second ring gear 23 are integrated and the power transmission shaft 3 is fixed coaxially with the first ring gear 13 and the second ring gear 23. For example, referring to fig. 2 and as shown in fig. 1 and 3, the power transmission shaft 3 is connected to the common ring gear 1323 through the ring gear connecting portion 31, the ring gear connecting portion 31 may be a plurality of radial connecting arms, and both ends of each of the radial connecting arms are connected to the inner circumferential surface of the common ring gear 1323 and the outer circumferential surface of the power transmission shaft 3, respectively, but the ring gear connecting portion 31 may be configured in a ring shape, and the outer circumferential edge thereof is fixed to the inner circumferential surface of the common ring gear 1323, and the inner circumferential edge thereof is fixed to the outer circumferential. In the embodiment of fig. 1 and 3, the power transmission shaft 3 is arranged parallel to the intermediate shaft 61, whereas in the embodiment of fig. 4, the power transmission shaft 3 is the same component as the intermediate shaft 61.

As for the first braking device 41, in some embodiments, as shown in fig. 1, the first braking device 41 may be configured to directly brake the intermediate shaft 61, thereby indirectly braking the first and second gear rings 13 and 23. In the embodiment of fig. 4, the intermediate shaft 61 is the same as the power transmission shaft 3, so that the first braking device 41 is equivalent to directly and simultaneously braking the two shafts.

Since the first planet carrier 14 and the second planet carrier 24 can be used as power output ends of the power driving system 1000, gears can be arranged on the planet carriers so that the planet carriers can output power outwards. As shown in fig. 2, in one embodiment, the first carrier 14 is provided with a first carrier output gear 141 coaxially, and the second carrier 24 is provided with a second carrier output gear 241 coaxially. Further, since the first carrier output gear 141 is located radially outside the first carrier 14 and the second carrier output gear 241 is located radially outside the second carrier 24, the first carrier 14 and the second carrier 24 have relatively large radial dimensions, and the two output gears 141, 241 are respectively arranged radially outside the respective carriers, so that the two output gears 141, 241 have relatively large rotation radii, which facilitates the cooperative transmission with the side gears 711, 721 on the

half shafts

71, 72 or the

half shafts

71, 72 of the vehicle 10000, and improves the reliability of the transmission.

Referring to fig. 1 in conjunction with the embodiment of fig. 2, power coupling device 100 has two planetary gear mechanisms 1, 2, while first motor generator 51 (rotor) and second motor generator 52 (rotor) are coaxially connected with first sun gear 11 and second sun gear 21, respectively. The stator of the first motor generator 51 and the stator of the second motor generator 52 are located outside the corresponding rotor, so as to be a preferred embodiment, the housings of the first motor generator 51 and the second motor generator 52 may form an integrated structure, and the two planetary gear mechanisms 1 and 2 are wrapped to form a common housing, that is, the common housing may be used as a large housing of the power coupling device 100, and the two planetary gear mechanisms 1 and 2, the two

motors

51 and 52 may be accommodated in the common housing, thereby reducing the number of components, making the structure of the power driving system 1000 more compact, the volume smaller, the processing and manufacturing more convenient, the manufacturing cost is greatly saved, the highly integrated design of the product is realized, the power driving system 1000 realizes efficient modular production, and the efficiency is greatly improved in the manufacturing and assembling links.

Of course, as a similar modification, the first sun gear 11, the first carrier 14, the first planet gears 12, and the first ring gear 13 may be housed inside the first motor generator 51, i.e., inside the casing of the first motor generator 51, and the second sun gear 21, the second planet gears 22, the second carrier 24, and the second ring gear 23 may be housed inside the second motor generator 52, e.g., inside the casing of the second motor generator 52.

From this, can realize the highly integrated design of product equally, make power drive system 1000 realize high-efficient modularization production, all promote efficiency, effective reduce cost greatly in manufacturing, assembly link.

The detailed construction and typical operating conditions of the power drive system 1000 in the embodiment of fig. 1 are described in detail below in conjunction with fig. 1.

Referring to fig. 1 (in conjunction with fig. 2), the planetary gear mechanism 1 and the planetary gear mechanism 2 are coaxially arranged.

The planetary gear mechanism 1 comprises a first sun gear 11, a first planet gear 12, a first planet carrier 14 and a first gear ring 13, wherein the first sun gear 11 is located at a middle position, the first planet gear 12 is respectively meshed with the first sun gear 11 and the first gear ring 13, the first planet gear 12 is installed on the first planet carrier 14, a first planet carrier output gear 141 is coaxially fixed on the first planet carrier 14, the first planet carrier output gear 141 is meshed with a side gear 711 on a left half shaft 71, and a left wheel 73 is connected to the outer side of the left half shaft 71.

The planetary gear mechanism 2 comprises a second sun gear 21, a second planet gear 22, a second planet carrier 24 and a second ring gear 23, the second sun gear 21 is located at the middle position, the second planet gear 22 is respectively meshed with the second sun gear 21 and the second ring gear 23, the second planet gear 22 is installed on the second planet carrier 24, a second planet carrier output gear 241 is coaxially fixed on the second planet carrier 24, the second planet carrier output gear 241 is meshed with a side gear 721 on the right half shaft 72, and the right side wheel 74 is connected to the outer side of the right half shaft 72.

The number of teeth of each kinematic pair in the planetary gear mechanism 1 and the corresponding kinematic pair in the planetary gear mechanism 2 may be the same, so that the transmission ratios obtained when the planetary gear mechanism 1 and the planetary gear mechanism 2 transmit power according to the same transmission path are the same.

The first ring gear 13 and the second ring gear 23 may be formed as an integral structure to constitute a common ring gear 1323, the common ring gear 1323 is coaxially fixed to the power transmission shaft 3, and a ring gear connecting portion 31 may be provided between the common ring gear 1323 and the power transmission shaft 3 for connection.

An intermediate shaft fixed gear 621 is fixedly arranged on the intermediate shaft 61, and the intermediate shaft fixed gear 621 is in meshing transmission with an external gear portion 622 fixed on the common gear ring 1323.

The first braking device 41 is a brake and is used to brake the intermediate shaft 61, thereby achieving an indirect braking action on the common ring gear 1323 formed by the first ring gear 13 and the second ring gear 23.

The first motor generator 51 is coaxially fixed with the first sun gear 11, the first motor generator 51 is coaxially sleeved on the power transmission shaft 3 with the first sun gear 11, the second motor generator 52 is coaxially fixed with the second sun gear 21, and the second motor generator 52 is coaxially sleeved on the power transmission shaft 3 with the second sun gear 21.

The left end of the intermediate shaft 61 is coaxially connected to the first engaging portion 421 of the dual clutch 42, a gear 531 is fixedly provided on the motor shaft of the third motor generator 53, the gear 531 is engaged with a gear 532, the gear 532 is coaxially connected to the second engaging portion 422 through a hollow shaft 533, and the gear 532 and the hollow shaft 533 are loosely fitted over the intermediate shaft 61. The motor 54 is coaxially connected to the third engaging portion 423.

Wherein the first and second engaging portions 421 and 422 may be two driven discs of the dual clutch 42, the third engaging portion 423 may be a housing of the dual clutch 42, and the third engaging portion 423 may selectively engage at least one of the first and second engaging portions 421 and 422 (i.e., the housing of the dual clutch may selectively engage at least one of the two driven discs).

As can be seen from the structure of the embodiment in fig. 1, the power driving system 1000 eliminates the conventional mechanical differential, and can selectively input the power of the engine 54 and the power of the third motor generator 53 to the common ring gear 1323, and can also selectively lock the intermediate shaft 61 through the first braking device 41 to achieve the purpose of braking the common ring gear 1323, so that the sun gears of the planetary gear mechanisms on both sides are respectively and independently connected to the first motor generator 51 and the second motor generator 52, and finally the planet carriers of the two sets of planetary gear mechanisms are used as power output ends to output power. That is, various driving conditions can be realized by the double clutch 42, the first brake device 41 and different operation modes and rotation speed adjustments of the three motor generators.

Pure electric working condition:

the engine 54 and the third motor generator 53 are not operated, and the double clutch 42 is in the disconnected state. The first brake device 41 brakes the intermediate shaft 61, so that the first ring gear 13 and the second ring gear 23 are indirectly braked. The first motor generator 51 and the second motor generator 52 each operate independently to drive the wheels on the corresponding side.

Mixing working conditions I:

the first engaging portion 421 engages with the third engaging portion 423 and the second engaging portion 422 disengages from the third engaging portion 423, the engine 54, the first motor generator 51, and the second motor generator 52 operate, and the third motor generator 53 does not operate. The power generated by the engine 54 is output to the power coupling device 100 through the intermediate shaft 61, where a part of the power of the engine 54 is output from the first carrier 14 to the left wheel 73 after being power-coupled to the first motor generator 51, and another part of the power of the engine 54 is output from the second carrier 24 to the right wheel 74 after being power-coupled to the second motor generator 52.

At this time, the first motor generator 51, the second motor generator 52 and the engine 54 are in a rotational speed coupling relationship, and when the vehicle speed needs to be changed constantly in a short time, the speed regulation can be completed through the first motor generator 51 and the second motor generator 52, so that the engine 54 can be ensured to work at a relatively high-efficiency rotational speed all the time, and the fuel economy of the engine 54 is improved.

A second mixed working condition:

the first engagement portion 421 and the second engagement portion 422 are all engaged with the third engagement portion 423 (i.e., the double clutch 42 is all engaged), and the engine 54, the first motor generator 51, the second motor generator 52, and the third motor generator 53 are all operated. The power output from the engine 54 is output to the power coupling device 100 through the intermediate shaft 61, the third motor generator 53 can be operated as a generator, that is, a part of the power from the engine 54 is used for generating power (the part of the power is transmitted to the third motor generator 53 through the dual clutch 42), and the obtained electric energy can be supplied to the first motor generator 51 and the second motor generator 52, that is, the first motor generator 51 and the second motor generator 52 are operated as motors and are output from the respective planetary carriers after being power coupled with the engine 54.

Or at this time, the third motor generator 53 may also be used as a motor to output power to supplement the torque of the engine 54 and adaptively regulate the speed of the engine 54, and at this time, the first motor generator 51 and the second motor generator 52 also work in the form of motors, and the power is coupled between the first planet carrier 14 and the second planet carrier 24 and then output to the respective wheels.

Because the three motor generators and the engine 54 are in a rotational speed coupling relationship, when the vehicle speed needs to be changed continuously in a short time, the speed regulation can be completed through the motors, for example, the speed regulation is performed through the third motor generator 53 in a motor mode, or the speed regulation is performed through the first motor generator 51 and the second motor generator 52, or the speed regulation can be performed through the three motors simultaneously, so that the engine 54 can be ensured to be driven to work at a high-efficiency rotational speed all the time, and the better fuel economy is realized.

The working condition of extended range:

in the electric-only operating condition, when the battery power is insufficient, the second engaging portion 422 engages the third engaging portion 423 and the first engaging portion 421 remains disconnected from the third engaging portion 423, the engine 54 is started, the engine 54 outputs power to drive the third motor generator 53 to generate power, and the first motor generator 51 and the second motor generator 52 are supplemented with necessary electric energy, which may also be referred to as driving power generation.

Parking power generation working condition one:

when the vehicle is in the parking state (e.g., braking the

wheels

73, 74 by the parking brake system), the second engagement portion 422 engages the third engagement portion 423 and the first engagement portion 421 is disengaged from the third engagement portion 423, and the engine 54 outputs the generated power to the third motor generator 53, thereby driving the third motor generator 53 to generate power. Accordingly, the power of the engine 54 can reach the third motor generator 53 via a short transmission chain, and the energy transmission loss is small, and the charging efficiency is high. It is understood that the first motor generator 51 and the second motor generator 52 do not operate at this time.

And a parking power generation working condition II:

when the vehicle is in a parking state, the

wheels

73 and 74 are braked by the parking brake system, so that the first carrier 14 and the second carrier 24 are braked, the first joint part 421 and the second joint part 422 are all jointed with the third joint part 423, part of the power of the engine 54 is output to the third motor generator 53, the other part of the power of the engine is output to the common ring gear 1323 through the intermediate shaft 61, and is transmitted to the first motor generator 51 through the first sun gear 11 by the common ring gear 1323, and is transmitted to the second motor generator 52 through the second sun gear 21, so that the first motor generator 51 and the second motor generator 52 are driven to generate power at the same time, in other words, under the working condition, the engine 54 simultaneously drives the three motors to generate power, thereby greatly improving the charging power, effectively shortening the charging time and realizing the quick charging function.

And a parking power generation working condition III:

when the vehicle is in the parking state, the

wheels

73, 74 are braked by the parking brake system, so that the first carrier 14 and the second carrier 24 are braked, the first engaging portion 421 engages the third engaging portion 423 and the second engaging portion 422 is disengaged from the third engaging portion 423, the power generated by the engine 54 is output to the common ring gear 1323 through the intermediate shaft 61, is transmitted to the first motor generator 51 by the common ring gear 1323 through the first sun gear 11, and is transmitted to the second motor generator 52 by the second sun gear 21, so that the first motor generator 51 and the second motor generator 52 are driven to generate power simultaneously.

Fig. 3 shows another embodiment of the power driving system 1000, and compared with the embodiment of fig. 1, the intermediate shaft 61 of the power driving system 1000 in the embodiment of fig. 3 is linked with the common gear ring 1323 through the intermediate transmission device 62, and the configuration and typical working conditions of the rest parts are substantially the same as those of the embodiment of fig. 1, and are not repeated here.

Fig. 4 shows another embodiment of the power driving system 1000, compared with the embodiment of fig. 1, the third motor generator 53 of the power driving system 1000 in the embodiment of fig. 4 is coaxially sleeved on the radial outer side of the dual clutch 42, the intermediate shaft 61 and the power transmission shaft 3 are the same component, that is, the intermediate shaft 61 is coaxially fixed with the first ring gear 13 and the second ring gear 23, and the configuration and typical working condition of the rest parts are substantially the same as those of the embodiment of fig. 1, and are not repeated here.

In summary, according to the power drive system 1000 of the embodiment of the present invention, the speed and torque regulation is performed by the first motor generator 51 and the second motor generator 52, and the two sets of planetary gear mechanisms are used for power coupling, so that the whole power drive system 1000 is made the simplest and the most compact. Such a series-parallel power drive system 1000 can not only realize independent control of the first motor generator 51 and the second motor generator 52 for the respective wheels, but also maximally ensure operation of the engine 54 in a rotation speed range with high fuel economy. And since the first motor generator 51 and the second motor generator 52 can independently control the corresponding wheels, the active safety and mobility of the vehicle 10000 system are significantly improved, and the maneuverability and driving feeling of the system are greatly improved. Meanwhile, the system has the functions of torque compensation and power generation of the engine 54 by the third motor generator 53, the requirements of each power source on the speed ratio are scientifically and reasonably met, mechanical control elements such as gear shifting are few, the structure is simple and compact, and the space utilization rate is high.

It will be appreciated that the power drive system 1000 described above may be used as a forward drive or a rear drive for a vehicle, preferably as a forward drive for a vehicle. When the power drive system 1000 is used as a forward drive, the drive system 100a shown in fig. 5 to 15 can be used as a backward drive to drive the vehicle to run together.

In short, the power coupling device 100 of the power driving system 1000 described above can drive a pair of front wheels of a vehicle, while the driving system 100a shown in fig. 5 to 15 can drive a pair of rear wheels of the vehicle. However, the present invention is not limited thereto, and for example, the power coupling device 100 may drive a pair of rear wheels of the vehicle, while the driving system 100a shown in fig. 5 to 15 may drive a pair of front wheels.

The following description will first be made in detail with respect to a drive system 100a shown in fig. 5-7 in conjunction with a specific embodiment.

As shown in fig. 5 to 7, the drive system 100a according to the embodiment of the invention may include a first planetary gear mechanism 1a, a second planetary gear mechanism 2a, a fourth motor generator 31a, a fifth motor generator 32a, a second brake device 63a, a third brake device 64a, and a power coupling device 65 a.

As shown in fig. 5 to 7, the first planetary gear mechanism 1a may be a single row planetary gear mechanism, and the first planetary gear mechanism 1a may include a third sun gear 11a, a third planet gear 12a, a third carrier 14a, and a third ring gear 13 a. The third planetary gears 12a are mounted on a third carrier 14a and disposed between the third sun gear 11a and the third ring gear 13a, and the third planetary gears 12a mesh with the third sun gear 11a and the third ring gear 13a, respectively. The third planetary gears 12a may be mounted on the third carrier 14a by a planetary gear shaft, and the third planetary gears 12a may be plural and uniformly spaced along the circumferential direction of the third sun gear 11a, and for example, in consideration of power transmission stability and manufacturing cost, the third planetary gears 12a may be three and uniformly spaced outside the third sun gear 11a, and adjacent two third planetary gears 12a are spaced by about 120 °.

The third planetary gear 12a meshes with the third sun gear 11a in an external engagement manner. The third planetary gears 12a mesh with the third ring gear 13a in such a manner that they mesh with each other, that is, teeth are formed on the inner peripheral surface of the third ring gear 13a, and the third planetary gears 12a mesh with the teeth on the inner peripheral surface of the third ring gear 13 a. The third planetary gear 12a may rotate around the axis of the planetary gear shaft or may revolve around the sun gear.

Similarly, as shown in fig. 5 to 7, the second planetary gear mechanism 2a may be a single row planetary gear mechanism, and the second planetary gear mechanism 2a may include a fourth sun gear 21a, a fourth planet gear 22a, a fourth carrier 24a, and a fourth ring gear 23 a. The fourth planetary gear 22a is mounted on the fourth carrier 24a and is disposed between the fourth sun gear 21a and the fourth ring gear 23a, and the fourth planetary gear 22a meshes with the fourth sun gear 21a and the fourth ring gear 23a, respectively. The fourth planetary gears 22a may be mounted on the fourth carrier 24a by a planetary gear shaft, and the fourth planetary gears 22a may be plural and evenly spaced along the circumferential direction of the fourth sun gear 21a, for example, in view of power transmission stability and manufacturing cost, the fourth planetary gears 22a may be three and evenly spaced outside the fourth sun gear 21a, and adjacent two fourth planetary gears 22a are spaced by about 120 °.

The fourth planetary gear 22a meshes with the fourth sun gear 21a in an external meshing manner. The fourth planetary gear 22a and the fourth ring gear 23a mesh with each other, that is, teeth are formed on the inner peripheral surface of the fourth ring gear 23a, and the fourth planetary gear 22a meshes with the teeth on the inner peripheral surface of the fourth ring gear 23 a. The fourth planetary gear 22a can rotate on the axis of the planetary gear shaft or revolve around the sun gear.

As a preferred embodiment, the third planetary gear 12a may include a first gear part 121a and a second gear part 122a that are coaxially arranged and synchronously rotate, the first gear part 121a being engaged with the third sun gear 11a, and the second gear part 122a being engaged with the third ring gear 13 a. The first gear part 121a and the second gear part 122a may be fixedly connected by the same shaft. The first gear part 121a may be a small gear part and the second gear part 122a may be a large gear part, that is, the number of teeth of the first gear part 121a is less than that of the second gear part 122a, so that when the power output by the fourth motor generator 31a is transmitted through the first gear part 121a and the second gear part 122a, the first gear part 121a and the second gear part 122a constitute a speed reduction mechanism, and a speed reduction and torque increase effect on the fourth motor generator 31a is achieved. Of course, alternatively, the first gear part 121a may be a large gear part and the second gear part 122a may be a small gear part.

Similarly, the fourth planetary gear 22a may include a third gear portion 221a and a fourth gear portion 222a that are coaxially arranged and synchronously rotate, the third gear portion 221a being meshed with the fourth sun gear 21a, and the fourth gear portion 222a being meshed with the fourth ring gear 23 a. The third gear 221a and the fourth gear 222a may be fixedly connected by the same shaft. The third gear portion 221a may be a small gear portion and the fourth gear portion 222a may be a large gear portion, that is, the number of teeth of the third gear portion 221a is less than that of the fourth gear portion 222a, so that when the power output by the fifth motor generator 32a is transmitted through the third gear portion 221a and the fourth gear portion 222a, the third gear portion 221a and the fourth gear portion 222a constitute a speed reduction mechanism, and a speed reduction and torque increase effect on the fifth motor generator 32a is achieved. Of course, alternatively, the third gear portion 221a may be a large gear portion and the fourth gear portion 222a may be a small gear portion.

As a preferred embodiment, the first gear portion 121a and the second gear portion 122a may be integrated to form a dual-toothed gear. Similarly, the third gear portion 221a and the fourth gear portion 222a may also be integrated to form a double-pinion gear. Therefore, the structure is simple and compact, and the transmission is reliable.

The third planet carrier 14a and the fourth planet carrier 24a can be used as power output ends of the driving system 100a, for example, the third planet carrier 14a and the fourth planet carrier 24a can output power from a power source, such as the fourth motor generator 31a and/or the fifth motor generator 32a, to the outside, such as the

wheels

41a and 42 a. Alternatively, when the power coupling device 100 drives the first pair of wheels, the third planet carrier 14a and the fourth planet carrier 24a may be linked with two

wheels

41a and 42a of the second pair of wheels, respectively, so that the third planet carrier 14a and the fourth planet carrier 24a may output the power of the driving system 100a to the second pair of

wheels

41a and 42a, so that the vehicle 10000 can run normally. The first pair of wheels is one of a pair of front wheels and a pair of rear wheels, and the second pair of wheels is the other of the pair of front wheels and the pair of rear wheels.

As shown in fig. 5 to 7, the fourth motor generator 31a is linked with the third sun gear 11a, and for example, the rotor of the fourth motor generator 31a may be coaxially connected with the third sun gear 11a, but is not limited thereto.

In the following description of the present invention, the term "linkage" is to be understood unless otherwise specified.

Similarly, the fifth motor generator 32a is linked with the fourth sun gear 21a, for example, but not limited to, the rotor of the fifth motor generator 32a may be coaxially connected with the fourth sun gear 21 a.

The second braking device 63a is provided for braking the third ring gear 13a, and the third braking device 64a is provided for braking the fourth ring gear 23 a. Alternatively, the second brake device 63a and the third brake device 64a may be brakes, but are not limited thereto.

The drive system 100a may comprise a first power take-off shaft 43a and a second power take-off shaft 44a, the first power take-off shaft 43a being arranged between the third planet carrier 14a and one wheel 41a of a second pair of wheels of the vehicle 10000, the second power take-off shaft 44a being arranged between the fourth planet carrier 24a and the other wheel 42a of the second pair of wheels, which may be a pair of front wheels, but may of course also be a pair of rear wheels.

As shown in fig. 5-7, the power coupling device 65a is configured to couple the first power output shaft 43a and the second power output shaft 44a, so that the first power output shaft 43a and the second power output shaft 44a form a rigid connection therebetween, and the first power output shaft 43a and the second power output shaft 44a can rotate in the same direction and at the same speed. That is, when the power engagement device 65a is in the engaged state, the first power output shaft 43a and the second power output shaft 44a are kept in the synchronous operation state, and when the power engagement device 65a is in the disengaged state, the first power output shaft 43a and the second power output shaft 44a can perform differential rotation, that is, the first power output shaft 43a and the second power output shaft 44a can rotate at different rotational speeds (may rotate at the same rotational speed, of course).

Here, it should be noted that the power coupling device 65a is used for coupling the first power output shaft 43a and the second power output shaft 44a, and it should be understood in a broad sense that the power coupling device 65a can directly couple or decouple the first power output shaft 43a and the second power output shaft 44a, but alternatively, the power coupling device 65a can indirectly couple or decouple the first power output shaft 43a and the second power output shaft 44a by coupling or decoupling other two components, such as the third planet carrier 14a and the fourth planet carrier 24a, which are connected with the first power output shaft 43a and the second power output shaft 44 a.

In a vehicle having the drive system 100a according to the embodiment of the invention, for example, when the vehicle 10000 runs on a flat road and advances in a straight line, the second brake device 63a and the third brake device 64a can brake the third ring gear 13a and the fourth ring gear 23a, respectively, and the fourth motor generator 31a and the fifth motor generator 32a can output power at the same rotational speed, so that the rotational speeds obtained for the respective wheels are theoretically equal by the decelerating action of the respective planetary gear mechanisms, thereby ensuring that the vehicle 10000 can smoothly travel in a straight line.

For another example, when the vehicle 10000 runs on an uneven road or turns, the second brake device 63a and the third brake device 64a can brake the third ring gear 13a and the fourth ring gear 23a, respectively, and at this time, the rotation speeds of the wheels on both sides theoretically have a rotation speed difference, taking a left turn as an example, the turning radius of the left wheel is smaller and the turning radius of the right wheel is larger, in order to ensure that the wheels roll with the ground, the rotation speed of the left wheel is smaller than the rotation speed of the right wheel, at this time, the output rotation speed of the fourth motor generator 31a can be smaller than the output rotation speed of the fifth motor generator 32a, and the specific rotation speed difference can be indirectly calculated by the steering angle of the steering wheel, for example, the driver rotates the steering wheel counterclockwise (turns to the left) by a certain angle, based on the steering angle, the controller of the vehicle 10000 can calculate the turning radius, and after the turning radius of the vehicle 10000 is determined, the relative rotation speed difference of the wheels on the two sides is also determined, and at this time, the controller can control the fourth motor generator 31a and the fifth motor generator 32a to output power outwards at matched rotation speeds respectively, so that the rotation speed difference between the fourth motor generator 31a and the fifth motor generator 32a can be matched with the rotation speed difference required by the wheels, and thus after the speed reduction action of the two planetary gear mechanisms, the two wheels can obtain expected rotation speeds, and thus pure rolling turning running is realized.

The fourth motor generator 31a and the fifth motor generator 32a have been described as examples of the electric motor, but it is needless to say that the fourth motor generator 31a and the fifth motor generator 32a may operate as electric generators. At this time, similarly, the second brake device 63a and the third brake device 64a can brake the third ring gear 13a and the fourth ring gear 23a, respectively, and the fourth motor generator 31a and the fifth motor generator 32a can be operated as generators, thereby recovering braking energy.

It will of course be appreciated that the first and second planetary gear mechanisms 1a, 2a described above may employ the same gear ratio, for example, the two planetary gear mechanisms may employ the same gear ratio with the sun gear as the power input and the planet carrier as the power output. That is, the numbers of teeth of the third sun gear 11a and the fourth sun gear 21a, the numbers of teeth of the third planetary gear 12a and the fourth planetary gear 22a, and the numbers of teeth (internal teeth) of the third ring gear 13a and the fourth ring gear 23a may be the same, respectively.

In particular, when the vehicle 10000 runs under poor road conditions, for example, when the vehicle 10000 runs on a relatively muddy or soft gravel road or sand, the vehicle 10000 may run into the soil to cause idling, that is, the vehicle 10000 slips (the slip and the cause of the slip are well known to those skilled in the art).

For the traditional differential with the self-locking function, after the wheel slips, only the differential needs to be controlled for self-locking, so that the difficulty removing capability of the vehicle 10000 can be improved to a certain extent at least.

Since the driving system 100a according to the embodiment of the present invention has a differential function, but has a structure that is greatly different from that of a conventional differential, a conventional differential self-locking structure cannot be used. In order to improve the trafficability of the vehicle 10000 and improve the adaptability of the vehicle 10000 to poor road conditions, the driving system 100a according to some embodiments of the present invention may further realize a self-locking function on the premise of realizing a differential function.

According to some embodiments of the present invention, as shown in fig. 5 to 7, when one-side wheel slip occurs in the vehicle, the power engagement device 65a engages the first power output shaft 43a with the second power output shaft 44a, and the second brake device 63a and the third brake device 64a brake the third ring gear 13a and the fourth ring gear 23a, respectively, whereby the fourth motor generator 31a and the fifth motor generator 32a can output the generated power from the non-slipping one-side wheel, improving the wheel slip phenomenon, and improving the passing ability of the vehicle.

In summary, according to the driving system 100a of the embodiment of the present invention, the braking action of the second braking device 63a and the third braking device 64a can realize the pure electric mode or the braking energy recovery mode of the fourth motor generator 31a and the fifth motor generator 32a, and the output rotation speeds of the fourth motor generator 31a and the fifth motor generator 32a can be controlled independently, so that the wheels on both sides can obtain different torques, and the differential function can be realized. In addition, the driving system 100a according to the embodiment of the invention has fewer parts, a compact and simple structure, small occupied volume and more convenient arrangement.

In particular, the drive system 100a according to the embodiment of the present invention may not be provided with the mechanical self-locking differential structure of the conventional power transmission system, but may perform the function of the conventional mechanical self-locking differential by the synchronization action of the power coupling device 65a, thereby making the structure of the power transmission system 100a according to the embodiment of the present invention more compact and lower in cost.

As an alternative embodiment, the power engagement device 65a may be a clutch. The clutch includes a driving portion 651a and a driven portion 652a engageable with and disengageable from each other, the driving portion 651a being connected to the first power output shaft 43a, and the driven portion 652a being connected to the second power output shaft 44 a.

Of course, the present invention is not limited thereto, and in other embodiments, the power engaging device 65a may be a synchronizer provided on one of the first power output shaft 43a and the second power output shaft 44a and for engaging the other.

As an alternative embodiment, the fourth motor generator 31a and the third sun gear 11a may be coaxially idly sleeved on the first power output shaft 43a, and the fifth motor generator 32a and the fourth sun gear 21a may be coaxially idly sleeved on the second power output shaft 44a, thereby making the structure of the driving system 100a more compact.

In addition, the fourth motor generator 31a and the fifth motor generator 32a may be distributed symmetrically left and right, such as symmetrically arranged about the power engagement device 65a, the first planetary gear mechanism 1a and the second planetary gear mechanism 2a may also be distributed symmetrically left and right, such as symmetrically arranged about the power engagement device 65a, and the fourth motor generator 31a and the fifth motor generator 32a may be respectively located on opposite outer sides of the first planetary gear mechanism 1a and the second planetary gear mechanism 2a, that is, for example, taking fig. 5 as an example, the fourth motor generator 31a is located on the outer side of the first planetary gear mechanism 1a, i.e., on the left side, and the fifth motor generator 32a is located on the outer side of the second planetary gear mechanism 2a, i.e., on the right side.

As an alternative embodiment, the first power output shaft 43a and the second power output shaft 44a may be half shafts, e.g. the first power output shaft 43a may be a left half shaft and the second power output shaft 44a may be a right half shaft.

The construction, connection and typical operation of the driving system 100a in the embodiment of fig. 5 will be described with reference to the accompanying drawings.

Referring to fig. 5, the drive system 100a shown in this embodiment mainly includes two single-row planetary gear mechanisms 1a, 2a, two

motor generators

31a, 32a, and

brake devices

63a, 64a and a power engagement device 65a, etc.

Specifically, the first planetary gear mechanism 1a on the left side includes a third sun gear 11a, a third planet gear 12a, and a third ring gear 13a, the third sun gear 11a is idly provided on the first power output shaft 43a, and the third sun gear 11a is connected to the fourth motor generator 31a, and the fourth motor generator 31a is also idly provided on the first power output shaft 43 a. The third planetary gears 12a are double pinion gears and are mounted on a third carrier 14a, and the third planetary gears 12a are meshed with the third sun gear 11a and the third ring gear 13a, respectively.

Similarly, the second planetary gear mechanism 2a on the right includes a fourth sun gear 21a, a fourth planet gear 22a, and a fourth ring gear 23a, the fourth sun gear 21a is idly provided on the second power output shaft 44a, and the fourth sun gear 21a is connected to the fifth motor generator 32a, and the fifth motor generator 32a is also idly provided on the second power output shaft 44 a. The fourth planetary gear 22a is a double pinion gear and is mounted on the fourth carrier 24a, and the fourth planetary gear 22a is meshed with the fourth sun gear 21a and the fourth ring gear 23a, respectively.

The second brake device 63a is for braking the third ring gear 13a, the third brake device 64a is for braking the fourth ring gear 23a, and the power engaging device 65a is provided between the first planetary gear mechanism 1a and the second planetary gear mechanism 2a and for selectively engaging the first power output shaft 43a and the second power output shaft 44 a.

The first power take-off shaft 43a is connected to the left hand wheel 41a and the third planet carrier 14a, and the second power take-off shaft 44a is connected to the right hand wheel 42a and the fourth planet carrier 24 a.

The following describes typical operating conditions of the drive system 100a in the embodiment of fig. 5.

Electric-only operating conditions (by means of the fourth and fifth motor-

generators

31a, 32 a):

the second brake device 63a brakes the third ring gear 13a and the third brake device 64a brakes the fourth ring gear 23a, and the power engaging device 65a is in the disengaged state. The fourth motor generator 31a and the fifth motor generator 32a may be operated as motors, respectively. Thus, the power generated by the fourth motor generator 31a is transmitted to the left wheel 41a via the third sun gear 11a, the third planetary gear 12a, the third carrier 14a, and the first power output shaft 43a, and the rotation speed of the fourth motor generator 31a changes in positive correlation with the rotation speed of the left wheel 41 a. The power generated by the fifth motor generator 32a is transmitted to the right wheel 42a via the fourth sun gear 21a, the fourth planetary gear 22a, the fourth carrier 24a, and the second power output shaft 44a, and the rotation speed of the fifth motor generator 32a and the rotation speed of the right wheel 42a change in positive correlation.

Since the fourth motor generator 31a and the fifth motor generator 32a are operated independently at this time, and they do not interfere with each other, the two motors can adaptively adjust the output rotation speed according to the torque required by the respective corresponding wheels, thereby implementing the differential function.

It is understood that in this operating condition, the fourth motor generator 31a and the fifth motor generator 32a may rotate clockwise or counterclockwise, thereby achieving electric-only forward or electric-only reverse.

And (3) a slipping working condition:

taking the left wheel 41a slipping as an example, the second brake device 63a brakes the third ring gear 13a and the third brake device 64a brakes the fourth ring gear 23a, the power engagement device 65a is engaged, and the power generated by the fourth motor generator 31a can be output to the right second planetary gear mechanism 2a by the engagement of the power engagement device 65a, and can be coupled with the power generated by the fifth motor generator 32a and output to the right non-slipping wheel 42 a.

Therefore, when the left wheel slips, the left fourth motor generator 31a can still output power from the wheel which does not slip on the right side, and the fourth motor generator 31a does not need to be reversed, so that the timeliness and the success rate of getting rid of the trouble are greatly improved.

Sliding in neutral gear:

the second brake device 63a, the third brake device 64a, and the power engagement device 65a are all in the disengaged state, and the fourth motor generator 31a and the fifth motor generator 32a are in the follow-up state.

Recovering braking energy:

the second brake device 63a brakes the third ring gear 13a and the third brake device 64a brakes the fourth ring gear 23a, the power engagement device 65a can be in an off state, and the braking energy is output to the corresponding motor generator through the respective power output shaft and the planetary gear mechanism, so as to drive the motor generator to generate electricity.

The drive system 100a in other embodiments is described below with reference to fig. 8-10.

As shown in fig. 8 to 10, a driving system 100a according to other embodiments of the present invention may include fourth and

fifth motor generators

31a and 32a, first and second

power output shafts

43a and 44a, sets of first and second planetary gear mechanisms 1a and 2a, and second and

third braking devices

63a, 64a and power engagement devices 65 a.

As shown in fig. 8 to 10, a plurality of sets of first planetary gear mechanisms 1a (a 1, a2 shown in fig. 8 to 10) are provided in series between the fourth motor generator 31a and the first power output shaft 43a, the plurality of sets of first planetary gear mechanisms 1a are provided so as to be able to output the power from the fourth motor generator 31a to the first power output shaft 43a through a speed change action, and since the plurality of sets of first planetary gear mechanisms 1a are provided in series, the plurality of sets of first planetary gear mechanisms 1a are able to sequentially perform a speed change action on the power during the output of the power of the fourth motor generator 31a to the first power output shaft 43a, and thus perform a multi-stage speed change function. For example, each of the first planetary gear mechanisms performs a speed reduction and torque increase action, and therefore the plurality of sets of first planetary gear mechanisms 1a form a multi-stage speed reduction effect, thereby increasing the output torque of the fourth motor generator 31 a.

Similarly, a plurality of sets of second planetary gear mechanisms 2a are arranged in series between the fifth motor generator 32a and the second power output shaft 44a, the plurality of sets of second planetary gear mechanisms 2a are arranged to be able to output the power from the fifth motor generator 32a to the second power output shaft 44a through a speed change action, and since the plurality of sets of second planetary gear mechanisms 2a are arranged in series, the plurality of sets of second planetary gear mechanisms 2a are able to sequentially perform a speed change action on the power of the fifth motor generator 32a during the output to the second power output shaft 44a, and perform a multi-step speed change function. For example, each of the second planetary gear mechanisms functions to reduce the speed and increase the torque, and therefore the plurality of sets of second planetary gear mechanisms 2a form a multi-stage speed reduction effect, thereby increasing the output torque of the fifth motor generator 32 a.

The plural sets of first planetary gear mechanisms 1a may be coaxially arranged, the plural sets of second planetary gear mechanisms 2a may also be coaxially arranged, and the central axes of the plural sets of first planetary gear mechanisms 1a and the plural sets of second planetary gear mechanisms 2a may be coincident.

The first power take-off shaft 43a may be connected to one wheel 41a of a second pair of wheels of the vehicle and the second power take-off shaft 44a may be connected to the other wheel 42a of the second pair of wheels, in which case the power coupling 100 is used to drive the first pair of wheels. Wherein the first pair of wheels is one of a pair of front wheels and a pair of rear wheels and the second pair of wheels is the remaining pair.

As shown in fig. 8 to 10, each of the first planetary gear mechanism 1a and the second planetary gear mechanism 2a may be a single row planetary gear mechanism, and the first planetary gear mechanism 1a may include a sun gear, a planet carrier, and a ring gear (a plurality of sets of the first planetary gear mechanisms 1a share the ring gear, i.e., the first shared ring gear 13 a).

The planet wheel is installed on the planet carrier and is arranged between the sun gear and the gear ring, and the planet wheel is respectively meshed with the sun gear and the gear ring. The planet wheels can be mounted on the planet carrier through a planet wheel shaft, the planet wheels can be a plurality of planet wheels and are uniformly distributed along the circumferential direction of the sun wheel at intervals, for example, the planet wheels can be three planet wheels and are uniformly distributed on the outer side of the sun wheel in consideration of the stability of power transmission and the manufacturing cost, and the interval between every two adjacent planet wheels is about 120 degrees.

The engagement mode of the planet wheel and the sun wheel is external engagement. The engagement between the planetary gear and the gear ring is inner engagement, that is, teeth are formed on the inner circumferential surface of the gear ring, and the planetary gear is engaged with the teeth on the inner circumferential surface of the gear ring. The planet wheel can rotate around the axis of the planet wheel shaft and can also revolve around the sun wheel.

Similarly, the second planetary gear mechanism 2a may also include a sun gear, planet gears, a planet carrier, and a ring gear (which is shared by multiple sets of second planetary gear mechanisms 2a, i.e., the second shared ring gear 23 a). Further, the relative positional relationship, the connection relationship, the action relationship, and the like between the respective members may be made in accordance with the first planetary gear mechanism 1a, and therefore, will not be described in detail here. Further, the connection relationship between the plurality of sets of first planetary gear mechanisms 1a, the plurality of sets of second planetary gear mechanisms 2a, and the like will be described in detail below with reference to specific embodiments.

As shown in fig. 8 to 10, the plurality of sets of first planetary gear mechanisms 1a share the same first common ring gear 13a, and the plurality of sets of second planetary gear mechanisms 2a share the same second common ring gear 23 a. Therefore, the driving system 100a has a more compact structure, a smaller volume and a more convenient arrangement.

The second brake device 63a is provided for braking the first common ring gear 13a, and the third brake device 64a is provided for braking the second common ring gear 23 a. Alternatively, the second brake device 63a and the third brake device 64a may be brakes, but are not limited thereto.

As shown in fig. 8-10, the power coupling device 65a is configured to couple the first power output shaft 43a and the second power output shaft 44a, so that the first power output shaft 43a and the second power output shaft 44a form a rigid connection therebetween, and the first power output shaft 43a and the second power output shaft 44a can rotate in the same direction and at the same speed. That is, when the power engagement device 65a is in the engaged state, the first power output shaft 43a and the second power output shaft 44a are kept in the synchronous operation state, and when the power engagement device 65a is in the disengaged state, the first power output shaft 43a and the second power output shaft 44a can perform differential rotation, that is, the first power output shaft 43a and the second power output shaft 44a can rotate at different rotational speeds (may rotate at the same rotational speed, of course).

Here, it should be noted that the power coupling device 65a is used for coupling the first power output shaft 43a and the second power output shaft 44a, and it should be understood in a broad sense, for example, the power coupling device 65a can directly couple or decouple the first power output shaft 43a and the second power output shaft 44a, but alternatively, the power coupling device 65a can indirectly couple or decouple the first power output shaft 43a and the second power output shaft 44a by coupling or decoupling other two components, such as the carrier a23 and the carrier B23, which are connected with the first power output shaft 43a and the second power output shaft 44 a.

In a vehicle having the drive system 100a according to the embodiment of the invention, for example, when the vehicle 10000 runs on a flat road and advances in a straight line, the second brake device 63a and the third brake device 64a can brake the first common ring gear 13a and the second common ring gear 23a, respectively, and the fourth motor generator 31a and the fifth motor generator 32a can output power at the same rotational speed, so that the rotational speeds obtained for the respective wheels are theoretically equal by the deceleration action of the respective sets of planetary gear mechanisms, thereby ensuring that the vehicle 10000 can smoothly travel in a straight line.

For another example, when the vehicle 10000 runs on an uneven road or turns, the second brake device 63a and the third brake device 64a can brake the first common ring gear 13a and the second common ring gear 23a respectively, and the rotational speeds of the wheels on both sides theoretically have a rotational speed difference, taking a left turn as an example, the turning radius of the left wheel is smaller and the turning radius of the right wheel is larger, in order to ensure that the wheels roll with the ground, the rotational speed of the left wheel is smaller than the rotational speed of the right wheel, and the output rotational speed of the fourth motor generator 31a can be smaller than the output rotational speed of the fifth motor generator 32a, and the specific rotational speed difference can be indirectly calculated by the steering angle of the steering wheel, such as the driver turns the steering wheel counterclockwise (turns left) by a certain angle, and the controller of the vehicle 10000 can calculate the turning radius based on the steering angle, after 10000 turning radii of the vehicle are determined, the relative rotation speed difference of the wheels on the two sides is also determined, at this time, the controller can control the fourth motor generator 31a and the fifth motor generator 32a to output power outwards at matched rotation speeds respectively, so that the rotation speed difference between the fourth motor generator 31a and the fifth motor generator 32a can be matched with the rotation speed difference required by the wheels, and after the deceleration action of the two groups of planetary gear mechanisms, the two wheels can obtain expected rotation speeds, so that pure rolling turning running is realized.

The fourth motor generator 31a and the fifth motor generator 32a have been described as examples of the electric motor, but it is needless to say that the fourth motor generator 31a and the fifth motor generator 32a may operate as electric generators. At this time, similarly, the second brake device 63a and the third brake device 64a can brake the first common ring gear 13a and the second common ring gear 23a, respectively, and the fourth motor generator 31a and the fifth motor generator 32a can be operated as generators, thereby recovering braking energy. That is, when the fourth motor generator 31a and the fifth motor generator 32a output power as motors or recover energy as generators to generate power, the second brake device 63a and the third brake device 64a are both in a braking state of braking the corresponding common ring gear, respectively, and the power engagement device 65a is in a disengaged state.

It will of course be appreciated that the sets of first planetary gear mechanisms 1a and the sets of second planetary gear mechanisms 2a described above may employ the same transmission ratio, that is, the two sets of planetary gear mechanisms may employ the same transmission ratio with the sun gear as the power input and the planet carrier as the power output. For example, the number of teeth of the sun gear a11 and the sun gear B11, the number of teeth of the planet gear a12 and the planet gear B12, the number of teeth of the sun gear a21 and the sun gear B21, the number of teeth of the planet gear a22 and the planet gear B22, and the number of teeth of the first common ring gear 13a and the second common ring gear 23a may be respectively the same.

According to some embodiments of the present invention, as shown in fig. 8 to 10, when one-side wheel slip occurs in the vehicle, the power engagement device 65a engages the first power output shaft 43a with the second power output shaft 44a, and the second brake device 63a and the third brake device 64a brake the first common ring gear 13a and the second common ring gear 23a, respectively, whereby the fourth motor generator 31a and the fifth motor generator 32a can output the generated power from the non-slipping one-side wheel, improving the wheel slip phenomenon, and improving the vehicle's passing ability.

As shown in fig. 8 to 10, the series connection of the plurality of sets of first planetary gear mechanisms 1a and the plurality of sets of second planetary gear mechanisms 2a will be described in detail. It is understood that the plurality of first planetary gear mechanisms 1a and the plurality of second planetary gear mechanisms 2a may be connected in series in the same manner, which enables the driving system 100a to have high symmetry, so that the center of gravity of the driving system 100a is more biased to the middle region of the driving system 100a or directly located in the middle region, thereby improving the stability of the vehicle and making the front-rear weight ratio more reasonable.

The sun gear a11 of the first planetary gear mechanism a1 of the plurality of first planetary gear mechanisms 1a is linked with the fourth motor generator 31a, e.g., the rotor of the fourth motor generator 31a may be coaxially connected with the sun gear a11,

Further, the carrier a23 of the last set of the first planetary gear mechanism a2 of the plurality of sets of the first planetary gear mechanism 1a is connected to the first power output shaft 43a as a shaft.

Similarly, the sun gear B11 of the first-group second planetary gear mechanism B1 of the plurality of groups of second planetary gear mechanisms 2a is linked with the fifth motor generator 32a, e.g., the rotor of the fifth motor generator 32a may be coaxially connected with the sun gear B11. The carrier B23 of the last set of the second planetary gear mechanism B2 in the plurality of sets of second planetary gear mechanisms 2a is connected, e.g., coaxially connected, to the second power output shaft 44 a.

In a further embodiment, the carrier a13 of the preceding set of first planetary gear mechanism a1 in the multiple set of first planetary gear mechanism 1a is connected to the sun gear a21 of the following set of planetary gear mechanism a2 as a shaft, and the carrier B13 of the preceding set of second planetary gear mechanism B1 in the multiple set of second planetary gear mechanism 2a is connected to the sun gear B21 of the following set of second planetary gear mechanism B2 as a shaft.

For example, as shown in fig. 8 to 10, the first planetary gear mechanism 1a and the second planetary gear mechanism 2a are each two sets, and the carrier a13 of the first-group first planetary gear mechanism a1 is connected to the sun gear a21 of the last-group (i.e., second-group) first planetary gear mechanism a 2. Likewise, the carrier B13 of the first group second planetary gear mechanism B1 is connected with the sun gear B21 of the last group (i.e., second group) second planetary gear mechanism B2.

It should be noted that although the above embodiment shows a possible series connection of planetary gear mechanisms, this possible embodiment is only an illustrative example, and should not be construed as a limitation to the scope of the present invention or to imply that the present invention must adopt the above series connection. After reading the above description, those skilled in the art can modify and/or combine the above series connection mode to form a new scheme, which should belong to the equivalent of the above series connection mode and fall into the protection scope of the present invention.

Further, it should be noted that, in the description of the present invention regarding "motor generator", if not specifically stated, the motor generator may be understood as an electric machine having a function of a generator and a motor.

As an alternative embodiment, the power engagement device 65a may be a clutch, as shown in fig. 8-9. The clutch includes a driving portion 651a and a driven portion 652a engageable with and disengageable from each other, the driving portion 651a being connected to the first power output shaft 43a, and the driven portion 652a being connected to the second power output shaft 44 a.

Of course, the present invention is not limited thereto, and in other embodiments, as shown in fig. 10, the power engagement device 65a may be a synchronizer provided on one of the first power output shaft 43a and the second power output shaft 44a and for engaging the other.

In addition, the fourth motor generator 31a and the fifth motor generator 32a may be distributed symmetrically left and right, such as symmetrically about the power engagement device 65a, the multiple sets of the first planetary gear mechanism 1a and the multiple sets of the second planetary gear mechanism 2a may also be distributed symmetrically left and right, such as symmetrically about the power engagement device 65a, and the fourth motor generator 31a and the fifth motor generator 32a may be respectively located on the opposite outer sides of the multiple sets of the first planetary gear mechanism 1a and the multiple sets of the second planetary gear mechanism 2a, that is, for example, taking fig. 8 as an example, the fourth motor generator 31a is located on the outer side of the multiple sets of the first planetary gear mechanism 1a, i.e., on the left side, and the fifth motor generator 32a is located on the outer side of the multiple sets of the second planetary gear mechanism 2 a.

The construction, connection and typical operation of the driving system 100a in the embodiment of fig. 8 will be described with reference to the accompanying drawings.

Referring to fig. 8, the drive system 100a shown in this embodiment mainly includes two single-row planetary gear mechanisms a1, a2 on the left side, two single-row planetary gear mechanisms B1, B2 on the right side, two

motor generators

31a, 32a, and

brake devices

63a, 64a and a power engagement device 65a, and the like.

Specifically, two first planetary gear mechanisms a1, a2 on the left side are arranged in series and share the same first common ring gear 13a, a sun gear a11 of a first-group first planetary gear mechanism a1 is coaxially connected with a fourth motor generator 31a, planet gears a12 of a first-group first planetary gear mechanism a1 are mounted on a planet carrier a13, planet gears a12 are respectively meshed with a sun gear a11 and the first common ring gear 13a, a planet carrier a13 is coaxially connected with a sun gear a21 of a second-group first planetary gear mechanism a2, planet gears a22 of a second-group first planetary gear mechanism a2 are mounted on a planet carrier a23, planet gears a22 are respectively meshed with a sun gear a21 and the first common ring gear 13a, a planet carrier a23 is coaxially connected with a first power output shaft 43a, and the first power output shaft 43a is connected with the left-side wheel 41 a. The first motor generator 43a, the sun gear a11 and the sun gear a21 are coaxially fitted on the first power output shaft 43a, and the first power output shaft 43a may be a left axle shaft.

The two second planetary gear mechanisms 2a on the right side are arranged in series and share the same second shared ring gear 23a, the sun gear B11 of the first group of second planetary gear mechanisms B1 is coaxially connected with the fifth motor generator 32a, the planet gear B12 of the first group of second planetary gear mechanisms B1 is mounted on the planet carrier B13, the planet gear B12 is respectively meshed with the sun gear B11 and the second shared ring gear 23a, the planet carrier B13 is coaxially connected with the sun gear B21 of the second group of second planetary gear mechanisms B2, the planet gear B22 of the second group of second planetary gear mechanisms B2 is mounted on the planet carrier B23, the planet gear B22 is respectively meshed with the sun gear B21 and the second shared ring gear 23a, the planet carrier B23 is coaxially connected with the second power output shaft 44a, and the second power output shaft 44a is connected with the right-side wheel 42 a. The fifth motor generator 32a, the sun gear B11 and the sun gear B21 are coaxially fitted on the second power output shaft 44a, and the second power output shaft 44a may be a right axle shaft.

The second brake device 63a is used for braking the first common ring gear 13a, the third brake device 64a is used for braking the second common ring gear 23a, and the power engaging device 65a is provided between the sets of the first planetary gear mechanism 1a and the sets of the second planetary gear mechanism 2a and is used for selectively engaging the first power output shaft 43a and the second power output shaft 44 a.

The following describes typical operating conditions of the drive system 100a in the embodiment of fig. 8.

Electric-only operating conditions (by means of the fourth and fifth motor-

generators

31a, 32 a):

the second brake device 63a brakes the first common ring gear 13a and the third brake device 64a brakes the second common ring gear 23a, with the power engagement device 65a in the disengaged state. The fourth motor generator 31a and the fifth motor generator 32a may be operated as motors, respectively. Thus, the power generated by the fourth motor generator 31a is output to the left wheel 41a by the deceleration action of the two sets of first planetary gear mechanisms 1a, and the rotation speed of the fourth motor generator 31a changes in positive correlation with the rotation speed of the left wheel 41 a. The power generated by the fifth motor generator 32a is output to the right-hand wheel 42a by the deceleration action of the two sets of second planetary gear mechanisms 2a, and the rotation speed of the fifth motor generator 32a changes in positive correlation with the rotation speed of the right-hand wheel 42 a.

And (3) a slipping working condition:

taking the left wheel 41a slipping as an example, the second brake device 63a brakes the first common ring gear 13a and the third brake device 64a brakes the second common ring gear 23a, the power engagement device 65a is engaged, and the power generated by the fourth motor generator 31a can be output to the second planetary gear mechanism on the right side by the engagement action of the power engagement device 65a, and can be coupled with the power generated by the fifth motor generator 32a at the carrier B23 to be output to the non-slipping wheel 42a on the right side.

Sliding in neutral gear:

Recovering braking energy:

the second brake device 63a brakes the first common ring gear 13a and the third brake device 64a brakes the second common ring gear 23a, the power coupling device 65a can be in the off state, and the braking energy is output to the corresponding motor generator through the respective power output shaft and the planetary gear mechanism, thereby driving the motor generator to generate electricity.

Further embodiments of drive system 100a are described in detail below with reference to fig. 11-15.

Referring to fig. 11 to 15, a power drive system 100a according to an embodiment of the present invention may include a first planetary gear mechanism 1a, a second planetary gear mechanism 2a, a fourth motor generator 31a, a fifth motor generator 32a, an intermediate transmission assembly 4b, and a second brake device 61 a.

Referring to fig. 11 to 15, the first planetary gear mechanism 1a may be a single row planetary gear mechanism, and the first planetary gear mechanism 1a may include a third sun gear 11a, a third planet gear 12a, a third carrier 14a, and a third ring gear 13 a. The third planetary gears 12a are mounted on a third carrier 14a and disposed between the third sun gear 11a and the third ring gear 13a, and the third planetary gears 12a mesh with the third sun gear 11a and the third ring gear 13a, respectively. The third planetary gears 12a may be mounted on the third carrier 14a by a planetary gear shaft, and the third planetary gears 12a may be plural and uniformly spaced along the circumferential direction of the third sun gear 11a, and for example, in consideration of power transmission stability and manufacturing cost, the third planetary gears 12a may be three and uniformly spaced outside the third sun gear 11a, and adjacent two third planetary gears 12a are spaced by about 120 °.

Similarly, referring to fig. 11 to 15, the second planetary gear mechanism 2a may be a single row planetary gear mechanism, and the second planetary gear mechanism 2a may include a fourth sun gear 21a, a fourth planet gear 22a, a fourth carrier 24a, and a fourth ring gear 23 a. The fourth planetary gear 22a is mounted on the fourth carrier 24a and is disposed between the fourth sun gear 21a and the fourth ring gear 23a, and the fourth planetary gear 22a meshes with the fourth sun gear 21a and the fourth ring gear 23a, respectively. The fourth planetary gears 22a may be mounted on the fourth carrier 24a by a planetary gear shaft, and the fourth planetary gears 22a may be plural and evenly spaced along the circumferential direction of the fourth sun gear 21a, for example, in view of power transmission stability and manufacturing cost, the fourth planetary gears 22a may be three and evenly spaced outside the fourth sun gear 21a, and adjacent two fourth planetary gears 22a are spaced by about 120 °.

As a preferred embodiment, as shown in fig. 11, the third planet gear 12a may include a first gear part 121a and a second gear part 122a coaxially arranged and synchronously rotating, the first gear part 121a being engaged with the third sun gear 11a, and the second gear part 122a being engaged with the third ring gear 13 a. The first gear part 121a and the second gear part 122a may be fixedly connected by the same shaft. The first gear part 121a may be a small gear part and the second gear part 122a may be a large gear part, that is, the number of teeth of the first gear part 121a may be less than that of the second gear part 122a, so that when the power output by the fourth motor generator 31a is transmitted through the first gear part 121a and the second gear part 122a, the first gear part 121a and the second gear part 122a constitute a speed reduction mechanism, and a speed reduction and torque increase effect on the fourth motor generator 31a is achieved. Of course, alternatively, the first gear part 121a may be a large gear part and the second gear part 122a may be a small gear part.

Similarly, as shown in fig. 11, the fourth planetary gear 22a may include a third gear portion 221a and a fourth gear portion 222a that are coaxially arranged and synchronously rotate, the third gear portion 221a being meshed with the fourth sun gear 21a, and the fourth gear portion 222a being meshed with the fourth ring gear 23 a. The third gear 221a and the fourth gear 222a may be fixedly connected by the same shaft. The third gear portion 221a may be a small gear portion and the fourth gear portion 222a may be a large gear portion, that is, the number of teeth of the third gear portion 221a may be less than that of the fourth gear portion 222a, so that when the power output by the fifth motor generator 32a is transmitted through the third gear portion 221a and the fourth gear portion 222a, the third gear portion 221a and the fourth gear portion 222a constitute a speed reduction mechanism, and a speed reduction and torque increase effect on the fifth motor generator 32a is achieved. Of course, alternatively, the third gear portion 221a may be a large gear portion and the fourth gear portion 222a may be a small gear portion.

The third planet carrier 14a and the fourth planet carrier 24a can be used as power output ends of the power driving system 100a, for example, the third planet carrier 14a and the fourth planet carrier 24a can output power from a power source, such as the fourth motor generator 31a and/or the fifth motor generator 32a, to the outside, such as the

wheels

41a and 42 a. Alternatively, the third planet carrier 14a and the fourth planet carrier 24a may be interlocked with two

wheels

41a, 42a of the second pair of wheels, respectively, so that the third planet carrier 14a and the fourth planet carrier 24a may output the power of the power driving system 100a to the

wheels

41a, 42a, so that the vehicle 10000 can run normally.

For example, the power coupling device 100 described above may drive a first pair of wheels, which is one of a front pair of wheels and a rear pair of wheels, and the third carrier 14a and the fourth carrier 24a may drive a second pair of wheels, respectively.

Referring to fig. 11 to 15, the fourth motor generator 31a is linked with the third sun gear 11a, for example, but not limited thereto, the rotor of the fourth motor generator 31a may be coaxially connected with the third sun gear 11 a.

Referring to fig. 11-15, the intermediate transmission assembly 4b is configured to be operatively associated with the third gear ring 13a and the fourth gear ring 23a, respectively, and the intermediate transmission assembly 4b may be disposed between the third gear ring 13a and the fourth gear ring 23a, with the third gear ring 13a, the intermediate transmission assembly 4b, and the fourth gear ring 23a being simultaneously actuated or relatively stationary.

The second braking device 61a is provided for braking the intermediate transmission assembly 4b, the third ring gear 13a and the fourth ring gear 23a also being indirectly braked when the second braking device 61a brakes the intermediate transmission assembly 4b, while the intermediate transmission assembly 4b, the third ring gear 13a and the fourth ring gear 23a are movable in relation to one another after the second braking device 61a releases the intermediate transmission assembly 4 b.

Therefore, when the second brake device 61a is in a braking state, the intermediate transmission assembly 4b, the third ring gear 13a and the fourth ring gear 23a are all braked, the power generated by the fourth motor generator 31a can be output from the third planet carrier 14a to the corresponding wheel, for example, the left wheel 41a, after passing through the third sun gear 11a and the third planet gears 12a, the power generated by the fifth motor generator 32a can be output from the fourth planet carrier 24a to the corresponding wheel, for example, the right wheel 42a, after passing through the fourth sun gear 21a and the fourth planet gears 22a, and the two motors respectively and independently control the rotating speeds of the corresponding wheels, so that the differential function is realized.

For example, when the vehicle 10000 runs on a flat road surface and advances in a straight line, the fourth motor generator 31a and the fifth motor generator 32a can output power at the same rotational speed, so that the rotational speeds obtained by the respective wheels are theoretically equal by the decelerating action of the respective planetary gear mechanisms, thereby ensuring that the vehicle 10000 can smoothly travel in a straight line.

For another example, when the vehicle 10000 runs on an uneven road or turns, the rotation speeds of the wheels on both sides theoretically have a rotation speed difference, taking a left turn as an example, the turning radius of the left wheel is smaller and the turning radius of the right wheel is larger, in order to ensure that the wheels roll with the ground, the rotation speed of the left wheel is smaller than the rotation speed of the right wheel, the output rotation speed of the fourth motor generator 31a may be smaller than the output rotation speed of the fifth motor generator 32a, and the specific rotation speed difference may be indirectly calculated by the steering angle of the steering wheel, for example, the driver rotates the steering wheel counterclockwise (turns left) by a certain angle, the controller of the vehicle 10000 may calculate the turning radius of the vehicle 10000 based on the steering angle, after the turning radius of the vehicle 10000 is determined, the relative rotation speed difference between the wheels on both sides is also determined, and at this time, the controller may control the fourth motor generator 31a and the fifth motor generator 32a to output power at matched rotation speeds respectively, the speed difference between the two wheels can be matched with the speed difference required by the wheels, so that the two wheels can obtain expected speeds after the speed reduction action of the two planetary gear mechanisms, and the pure rolling turning running is realized.

The fourth motor generator 31a and the fifth motor generator 32a have been described as examples of the electric motor, but it is needless to say that the fourth motor generator 31a and the fifth motor generator 32a may operate as electric generators. At this time, similarly, the second brake device 61a can still brake the intermediate transmission assembly 4b, and the fourth motor generator 31a and the fifth motor generator 32a can then operate as generators, thereby recovering braking energy.

It will of course be appreciated that the first and second planetary gear mechanisms 1a, 2a described above may employ the same gear ratio, that is to say that both planetary gear mechanisms may employ the same gear ratio, with the sun gear being the power input and the planet carrier being the power output. That is, the numbers of teeth of the third sun gear 11a and the fourth sun gear 21a, the numbers of teeth of the third planetary gear 12a and the fourth planetary gear 22a, and the numbers of teeth (internal teeth) of the third ring gear 13a and the fourth ring gear 23a may be the same, respectively.

In summary, according to the power drive system 100a of the embodiment of the present invention, the braking action of the second braking device 61a can realize the electric-only mode or the braking energy recovery mode of the fourth motor generator 31a and the fifth motor generator 32a, and the output rotation speeds of the fourth motor generator 31a and the fifth motor generator 32a are controlled individually, so that the wheels on both sides can obtain different torques, and the differential function can be realized. In addition, the power driving system 100a according to the embodiment of the invention has the advantages of fewer parts, compact and simple structure, small occupied volume and more convenient arrangement.

A power drive system 100a according to a further embodiment of the present invention will be described in detail with reference to fig. 11 to 15.

When the vehicle 10000 runs on a poor road condition, for example, the vehicle 10000 runs on a muddy or soft gravel road or sandy soil, the vehicle 10000 may be sunk into the soil to cause idle running, that is, the vehicle 10000 slips (the slip phenomenon and the cause of the slip phenomenon are well known to those skilled in the art).

Since the power driving system 100a according to the embodiment of the present invention has a differential function, but has a structure that is greatly different from that of a conventional differential, a conventional differential self-locking structure cannot be utilized. In order to improve the trafficability of the vehicle 10000 and improve the adaptability of the vehicle 10000 to poor road conditions, the power driving system 100a according to some embodiments of the present invention can further realize a self-locking function on the premise of realizing a differential function.

According to some embodiments of the present invention, as shown in fig. 14 and fig. 15, for example, the power driving system 100a further includes a third braking device 62a, where the third braking device 62a is configured to brake the third planet carrier 14a or the fourth planet carrier 24a, that is, under certain specific conditions, such as a skid of the vehicle 10000, the third braking device 62a can selectively brake the third planet carrier 14a or the fourth planet carrier 24a, and more specifically, the third braking device 62a brakes the planet carrier corresponding to the wheel on the skid side at the time.

Taking the example that the third planet carrier 14a and the fourth planet carrier 24a are respectively connected with two

wheels

41a, 42a in the second pair of wheels of the vehicle 10000, when one wheel slips, the third brake device 62a brakes the planet carrier corresponding to the wheel on the slipping side, so that the motor generator on the slipping side can output the generated power to the wheel on the other side through the intermediate transmission assembly 4b, and the power is coupled with the motor generator on the other side and then jointly outputs the coupled power to the wheel on the other side, namely the non-slipping wheel, thereby improving the ability of the vehicle 10000 to escape from the trouble.

Referring to fig. 14-15, if the left wheel 41a slips, the third brake device 62a brakes the left third planet carrier 14a, and according to the motion characteristics of the planetary gear mechanism, the power generated by the left fourth motor generator 31a can be output through the third ring gear 13a, and the third ring gear 13a is linked with the right fourth ring gear 23a through the intermediate transmission assembly 4b, so that the power generated by the fourth motor generator 31a can be transmitted to the right fourth ring gear 23a, and the right fifth motor generator 32a can also output power, and two parts of power are coupled at the right fourth planet carrier 24a and then output to the right non-slipping wheel 42a, that is, both motors can output power through the non-slipping wheel, thereby greatly improving the escaping capability of the vehicle 10000.

It will be appreciated that the second brake device 61a now releases the intermediate transmission assembly 4b, i.e. the second brake device 61a now does not brake the intermediate transmission assembly 4 b.

In some embodiments of the present invention capable of implementing a differential self-locking function, the third braking device 62a may be a parking braking system (not shown) of the vehicle 10000, and the parking braking system is configured to selectively and individually brake one wheel of a pair of wheels (linked with the third planet carrier 14a and the fourth planet carrier 24a) so as to implement a braking action on a planet carrier connected with the wheel. For example, the parking brake system may only brake the left planet carrier (e.g., the third planet carrier 14a) for the left wheel alone when the left wheel is slipping, or the parking brake system may only brake the right planet carrier (e.g., the fourth planet carrier 24a) for the right wheel alone when the right wheel is slipping.

Of course, the present invention is not limited thereto, for example, the third brake device 62a may also be a service brake system of the vehicle 10000, which realizes the differential self-locking function substantially identical to the parking brake system, and is not described in detail herein for the sake of brevity.

It should be noted that the parking brake system or the service brake system may be different from the parking brake system or the service brake system which is widely known and used in the prior art. Taking a parking brake system as an example for illustration, a parking brake system widely adopted in the prior art generally brakes a pair of wheels, such as a pair of rear wheels, at the same time (for example, brakes by pulling a brake shoe of the rear wheel through a cable), while a parking brake system according to an embodiment of the present invention needs to be able to achieve independent braking of two wheels of a pair of wheels, such as independent braking of a left rear wheel (in which case the right rear wheel may be in a non-braking state) or independent braking of a right rear wheel (in which case the left rear wheel may be in a non-braking state). Since the construction and operation of a conventional parking brake system are known to those skilled in the art, those skilled in the art should make only simple modifications and/or modifications to the conventional parking brake system, so that the parking brake system according to the embodiment of the present invention can selectively and individually brake two wheels of a pair of wheels, for example, the parking brake system has two subsystems, each subsystem individually corresponds to one wheel, for example, one subsystem can brake by pulling a left rear wheel brake shoe through a cable, and the other subsystem can brake by pulling a right rear wheel brake shoe through another cable (the cable is only used for illustration here, for example, any other available manner and its equivalent may be used, and of course, the cable may also be used in an electric manner).

For similar reasons, the service brake system may also be different from the widely adopted service brake system, and of course, when the skilled person knows the difference between the parking brake system of the embodiment of the present invention and the conventional parking brake system, the difference between the service brake system of the embodiment of the present invention and the conventional service brake system can be understood and realized, and therefore, the detailed description is omitted here.

In another embodiment, the power driving system 100a may also be implemented by providing other components with a braking function when implementing the differential self-locking function.

As shown in fig. 14, in some embodiments, the third brake device 62a is configured to selectively engage the third carrier 14a or the fourth carrier 24a to the housing of the power drive system 100a to effect a braking action on the third carrier 14a or the fourth carrier 24 a.

Further, as shown in fig. 15, the third brake device 62a may be two, such as the

third brake devices

621a and 622a, and correspond to the third planet carrier 14a and the fourth planet carrier 24a, respectively, that is, each planet carrier corresponds to one second brake device, and the two

third brake devices

621a and 622a can work independently and without interference with each other. Of course, as shown in fig. 14, the third carrier 14a and the fourth carrier 24a may share the same third brake device 62 a. Alternatively, the third brake device 62a may be a synchronizer, a brake, or the like, but is not limited thereto.

As described above, when the vehicle 10000 skids, the planet carrier corresponding to the wheel on the skidding side can be braked by the third brake device 62a, so that the purpose that the motor on the skidding side outputs power through the non-skidding wheel on the other side is achieved, and at this time, the motor on the skidding side and the motor on the non-skidding side may output power to the outside at the same time, so that each motor generator works in the form of a motor and rotates in the same direction all the time when the wheel on one side skids. Therefore, the two motors, particularly the motor on the slipping side, do not need to be reversed, so that the control strategy is simplified, the time for trapping the vehicle 10000 can be shortened, and the quick and efficient trapping removal is facilitated.

Of course, it is understood that both the motor generators may be rotated all the way in the same direction while the fourth motor generator 31a and the fifth motor generator 32a participate in driving the vehicle 10000 forward.

Like this, when the wheel moves ahead and goes into the relatively poor road conditions suddenly, if the wheel of one side skids, then brake the planet carrier that the wheel of the side of skidding corresponds through controlling third arresting gear 62a, make the motor generator of this side pass through intermediate drive subassembly 4b with power transmission to the opposite side rapidly, and with the direct output of the motor generator power coupling back of opposite side, in this period, because the motor of the one side of skidding need not the reversal, need not to stop promptly, the switching-over rotation again, consequently when the wheel phenomenon of skidding appears, two motors can carry out the power coupling fast, and drive the wheel of the one side of not skidding jointly, the ageing of vehicle 10000 getting rid of poverty has been improved greatly.

For the case of how to achieve a fast power coupling without commutation of the motor, a person skilled in the art should be able to design an intermediate transmission assembly 4b that meets the requirements based on the principles disclosed herein. The present invention is illustrated herein schematically in one particular embodiment, it being understood, of course, that the embodiment described below is illustrative only and should not be taken as a limitation on the scope of the present invention or as an indication that power drive system 100a must employ an intermediate transmission assembly 4b having the configuration described below. After reading the above-mentioned principles of the specification and the following detailed description, those skilled in the art should be able to modify and/or replace the technical features of the following embodiments and their equivalents, and the modified embodiments should also fall within the scope of the present invention.

For example, referring to fig. 11-15, the intermediate transmission assembly 4b may include an intermediate shaft 41b, the intermediate shaft 41b having an intermediate shaft first gear 42b and an intermediate shaft second gear 44b, wherein the intermediate shaft first gear 42b may be coupled to the third ring gear 13a via an intermediate idler gear 43b, and the intermediate shaft second gear 44b is coupled to the fourth ring gear 23 a. Of course, as a variant, alternatively, the counter second gear 44b can be linked to the fourth ring gear 23a by means of the intermediate idle gear 43b, and the counter first gear 42b is linked to the third ring gear 13 a.

The first intermediate shaft gear 42b and the second intermediate shaft gear 44b may be fixedly arranged on the intermediate shaft 41b, and the radial dimensions of the first intermediate shaft gear 42b and the second intermediate shaft gear 44b are preferably different, e.g. the radial dimension of the intermediate shaft gear meshing with the intermediate idle gear 43b is relatively small, as in the embodiment shown in fig. 11-15, the radial dimension of the first intermediate shaft gear 42b is smaller than the radial dimension of the second intermediate shaft gear 44 b. Therefore, the axial direction of the intermediate shaft 41b can be kept consistent with the axial direction of the power output shaft (half shaft) or the motor, and the reliability and the stability of transmission are improved.

Further, the third ring gear 13a and the fourth ring gear 23a are provided with

external teeth

131a and 231a on their outer peripheral surfaces, respectively, and the intermediate shaft first gear 42b is interlocked with the external teeth 131a of the third ring gear 13a through an intermediate idle gear 43b, and meshes with the external teeth 131a of the intermediate shaft first gear 42b and the third ring gear 13a, respectively, as with the intermediate idle gear 43 b. The counter second gear 44b is interlocked with the external teeth 231a of the fourth ring gear 23a, for example, the counter second gear 44b is directly meshed with the external teeth 231a of the fourth ring gear 23 a.

In the embodiment of fig. 11-15, the second braking device 61a may be a brake and is used to brake the intermediate shaft 41 b. Thereby making power-driven system 100a relatively more compact and convenient to arrange.

The transmission between the planet carrier and the wheel is schematically described below.

The power drive system 100a may comprise a first power take-off shaft 43a and a second power take-off shaft 44a, the first power take-off shaft 43a being arranged between the third planet carrier 14a and one wheel 41a of the second pair of wheels of the vehicle 10000, the second power take-off shaft 44a being arranged between the fourth planet carrier 24a and the other wheel 42a of the second pair of wheels, which may be a pair of front wheels, but may of course be a pair of rear wheels.

As an alternative embodiment, the fourth motor generator 31a and the third sun gear 11a may be coaxially idly sleeved on the first power output shaft 43a, and the fifth motor generator 32a and the fourth sun gear 21a may be coaxially idly sleeved on the second power output shaft 44a, thereby making the structure of the power drive system 100a more compact. The fourth motor generator 31a and the fifth motor generator 32a may be symmetrically distributed, the first planetary gear mechanism 1a and the second planetary gear mechanism 2a may be symmetrically distributed, and the fourth motor generator 31a and the fifth motor generator 32a may be respectively located on the opposite outer sides of the first planetary gear mechanism 1a and the second planetary gear mechanism 2a, that is, for example, in fig. 13, the fourth motor generator 31a is located on the outer side of the first planetary gear mechanism 1a, that is, on the left side, and the fifth motor generator 32a is located on the outer side of the second planetary gear mechanism 2a, that is, on the right side.

As an alternative embodiment, as shown in fig. 15, a first reduction gear assembly 51a may be further disposed between the first power output shaft 43a and the third planet carrier 14a, and a second reduction gear assembly 52a may be further disposed between the second power output shaft 44a and the fourth planet carrier 24 a. The first reduction gear assembly 51a and the second reduction gear assembly 52a may have the same structure, thereby improving the versatility of the reduction gear assembly and reducing the cost. Moreover, the gear reduction assembly is arranged between the power output end of the power driving system 100a and the wheels, so that the effects of reducing speed and increasing torque can be better achieved.

The configuration, connection relationship, and typical operation of the power drive system 100a in the embodiment of fig. 11 will be described with reference to the accompanying drawings.

Referring to fig. 11, the power drive system 100a shown in this embodiment mainly includes two single-row planetary gear mechanisms 1a, 2a, two

motor generators

31a, 32a, and an intermediate transmission assembly 4b,

brake devices

61a, 62a, and the like.

The intermediate shaft 41b is fixedly provided with an intermediate shaft first gear 42b and an intermediate shaft second gear 44b, the second braking device 61a can be a brake and is used for braking the intermediate shaft 41b, the intermediate shaft first gear 42b can be linked with the external teeth 131a of the third gear ring 13a through an intermediate idle gear 43b, and the intermediate shaft second gear 44b can be directly linked with the external teeth 231a of the fourth gear ring 23 a.

The third brake device 62a is configured to selectively brake the third carrier 14a or the fourth carrier 24a, although it is understood that such braking may be direct braking or, of course, indirect braking.

Exemplary operating conditions of the power drive system 100a in the embodiment of FIG. 11 are described below.

Electric-only operating conditions (by means of the fourth and fifth motor-

generators

31a, 32 a):

the second brake device 61a brakes the intermediate shaft 41b, so that the third ring gear 13a and the fourth ring gear 23a are indirectly braked. The fourth motor generator 31a and the fifth motor generator 32a may be operated as motors, respectively. Thus, the power generated by the fourth motor generator 31a is transmitted to the left wheel 41a via the third sun gear 11a, the third planetary gear 12a, the third carrier 14a, and the first power output shaft 43a, and the rotation speed of the fourth motor generator 31a changes in positive correlation with the rotation speed of the left wheel 41 a. The power generated by the fifth motor generator 32a is transmitted to the right wheel 42a via the fourth sun gear 21a, the fourth planetary gear 22a, the fourth carrier 24a, and the second power output shaft 44a, and the rotation speed of the fifth motor generator 32a and the rotation speed of the right wheel 42a change in positive correlation.

And (3) a slipping working condition:

taking the left wheel 41a slipping as an example for illustration, the third brake device 62a will brake the third carrier 14a while the second brake device 61a is in the off state. The fourth motor generator 31a outputs the generated power to the fourth carrier 24a through the third sun gear 11a, the third planetary gear 12a, the third planet carrier 14a, the third ring gear 13a, the intermediate idle gear 43b, the intermediate shaft first gear 42b, the intermediate shaft 41b, the intermediate shaft second gear 44b, and the fourth ring gear 23a, and also outputs the power from the fifth motor generator 32a to the fourth carrier 24a, and the two portions of power are coupled and output from the second power output shaft 44a to the right wheel 42 a. Therefore, when the left wheel slips, the left fourth motor generator 31a can still output power from the wheel which does not slip on the right side, and the fourth motor generator 31a does not need to be reversed, so that the timeliness and the success rate of getting rid of the trouble are greatly improved.

Sliding in neutral gear:

the second brake device 61a and the third brake device 62a are all in the off state, and the fourth motor generator 31a and the fifth motor generator 32a are in the follow-up state.

Recovering braking energy:

the second brake device 61a brakes the intermediate shaft 41b, the third brake device 62a is in an off state, and the braking energy is output to the corresponding motor generator through the respective power output shaft and the planetary gear mechanism, thereby driving the motor generator to generate electricity.

Briefly describing a vehicle 10000 according to an embodiment of the present invention, referring to fig. 16, the vehicle 10000 includes a power drive system 1000 and a drive system 100a in the above embodiment, and the power drive system 1000 in fig. 1-4 may be used as a front drive, so that the power coupling device 100 of the power drive system 1000 drives a pair of front wheels, while the drive system 100a in fig. 5-15 may be used for a rear drive. Further, referring to a vehicle 10000 shown in fig. 17, it may comprise only a front drive portion of the power drive system 1000. Of course, the present invention is not limited thereto. It should be understood that other configurations of the vehicle 10000 according to the embodiment of the present invention, such as a brake system, a driving system, a steering system, etc., are known in the art and well known to those skilled in the art, and thus will not be described in detail herein.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean 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 invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples described in this specification can be combined and combined by those skilled in the art. Although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. A power drive system, comprising:

a power coupling device for driving a first pair of wheels of a vehicle, the power coupling device comprising: the planetary gear set comprises a first sun gear, a first planet carrier, a first gear ring, a second sun gear, a second planet carrier and a second gear ring, wherein the first gear ring is coaxially connected with the second gear ring;

an intermediate shaft arranged to be linked with the first and second gear rings;

an engine configured to selectively engage the intermediate shaft;

a first motor generator, a second motor generator and a third motor generator, the first motor generator being linked with the first sun gear, the second motor generator being linked with the second sun gear, the third motor generator being provided to be selectively linked with the engine;

a fourth motor generator and a fifth motor generator;

first and second power output shafts, and a plurality of sets of first and second planetary gear mechanisms, the power coupling device being provided for engaging the first and second power output shafts, the plurality of sets of first planetary gear mechanisms being provided in series between the fourth motor generator and the first power output shaft and being capable of outputting power from the fourth motor generator to the first power output shaft through a speed change action, the plurality of sets of second planetary gear mechanisms being provided in series between the fifth motor generator and the second power output shaft and being capable of outputting power from the fifth motor generator to the second power output shaft through a speed change action, wherein the plurality of sets of first planetary gear mechanisms share a same first common ring gear, the plurality of sets of second planetary gear mechanisms share a same second common ring gear, the first power take-off shaft being adapted to be connected to one of a second pair of wheels of the vehicle, the second power take-off shaft being adapted to be connected to the other of the second pair of wheels, the first pair of wheels being one of a front pair of wheels and a rear pair of wheels, the second pair of wheels being the other of the front pair of wheels and the rear pair of wheels; and

a first braking device for directly or indirectly braking the intermediate shaft;

a second brake device provided for braking the first common ring gear, and a third brake device provided for braking the second common ring gear;

a power engagement device configured to engage the first power output shaft with the second power output shaft.

2. The power drive system according to claim 1, wherein clutches are provided between the engine and the third motor generator and between the engine and the intermediate shaft.

3. The power drive system of claim 2, further comprising:

a dual clutch, the dual clutch comprising: a first engagement portion, a second engagement portion, and a third engagement portion configured to selectively engage at least one of the first engagement portion and the second engagement portion, the engine being in linkage with the third engagement portion, the intermediate shaft being in linkage with the first engagement portion, and the third motor generator being in linkage with the second engagement portion.

4. A power drive system according to claim 3, wherein the engine is coaxially connected to the third engagement portion; the intermediate shaft is coaxially connected with the first engagement portion; the third motor generator is linked with the second engagement portion by a gear mechanism.

5. The power drive system of claim 1, further comprising: and the intermediate shaft is linked with the first gear ring and the second gear ring through the intermediate transmission device.

6. A power drive system according to claim 5 wherein the intermediate transmission is a gear transmission.

7. The power drive system of claim 6, wherein the intermediate transmission comprises:

an outer tooth part coaxially linked with the first gear ring and the second gear ring; and

an intermediate shaft fixed gear fixedly provided on the intermediate shaft, the outer gear portion being meshed with the intermediate shaft fixed gear.

8. A power drive system according to claim 5 wherein the intermediate transmission is a belt transmission, a chain transmission or a CVT transmission.

9. The power drive system of claim 1, wherein the intermediate shaft is fixed coaxially with the first and second ring gears.

10. A power drive system according to claim 1, wherein the first and second planet carriers act as power take-offs for the power drive system.

11. A power drive system according to claim 10, wherein a first carrier output gear is coaxially disposed on the first carrier and a second carrier output gear is coaxially disposed on the second carrier.

12. The power-driven system of claim 1, wherein the first sun gear and the second sun gear have the same number of teeth, a first planet gear is disposed between the first sun gear and the first ring gear, a second planet gear is disposed between the second sun gear and the second ring gear, the first planet gear and the second planet gear have the same number of teeth, and the first ring gear and the second ring gear have the same number of teeth.

13. The power drive system according to claim 1, wherein the first sun gear, the first carrier, and the first ring gear are housed inside the first motor generator, and the second sun gear, the second carrier, and the second ring gear are housed inside the second motor generator.

14. A power drive system according to any one of claims 1-13,

the power coupling device is used for driving a first pair of wheels of the vehicle;

the power drive system further includes:

a first planetary gear mechanism and a second planetary gear mechanism, the first planetary gear mechanism including: a third sun gear, a third planet carrier, and a third ring gear, the second planetary gear mechanism including: a fourth sun gear, a fourth planet carrier and a fourth gear ring;

a fourth motor generator and a fifth motor generator, the fourth motor generator being linked with the third sun gear, the fifth motor generator being linked with the fourth sun gear;

a first power take-off shaft disposed between the third planet carrier and one of a second pair of wheels of a vehicle, and a second power take-off shaft disposed between the fourth planet carrier and the other of the second pair of wheels, the first pair of wheels being one of a front pair of wheels and a rear pair of wheels, the second pair of wheels being the other of the front pair of wheels and the rear pair of wheels;

a second brake device provided for braking the third gear ring, and a third brake device provided for braking the fourth gear ring; and

15. A power drive system according to any one of claims 1-13,

the power drive system further includes:

a first planetary gear mechanism and a second planetary gear mechanism, the first planetary gear mechanism including: a third sun gear, a third planet carrier, and a third ring gear, the second planetary gear mechanism including: a fourth sun gear, a fourth planet carrier, and a fourth ring gear, wherein the third planet carrier and the fourth planet carrier serve as power take-offs to drive a second pair of wheels, the first pair of wheels being one of a pair of front wheels and a pair of rear wheels, the second pair of wheels being the other of the pair of front wheels and the pair of rear wheels;

an intermediate drive assembly configured to be in linkage with the third gear ring and the fourth gear ring, respectively;

a second braking device configured to brake the intermediate transmission assembly.

16. A vehicle characterized by comprising a power drive system according to any one of claims 1-15.