WO2017107847A1

WO2017107847A1 - Power drive system and vehicle having said power drive system

Info

Publication number: WO2017107847A1
Application number: PCT/CN2016/110151
Authority: WO
Inventors: 廉玉波; 凌和平; 翟震; 郑峰; 徐友彬
Original assignee: 比亚迪股份有限公司
Priority date: 2015-12-25
Filing date: 2016-12-15
Publication date: 2017-06-29
Also published as: CN106915240B; CN106915240A

Abstract

Provided are a power drive system (1000) and a vehicle (10000); the power drive system (1000) comprises: a power coupling device (100), said power coupling device (100) comprising: a first sun gear (11), first planetary carrier (14), and first ring gear (13), and a second sun gear (21), second planetary carrier (24), and second ring gear (23); the first ring gear (13) and second ring gear (23) are coaxially connected; an intermediate shaft (61), said intermediate shaft (61) being configured to move concomitantly with the first ring gear (13) and second ring gear (23); an engine (54), said engine (54) being configured to selectably engage with the intermediate shaft (61); a first electric motor generator (51), second electric motor generator (52), and third electric motor generator (53); the first electric motor generator (51) moves concomitantly with the first sun gear (11), the second electric motor generator (52) moves concomitantly with the second sun gear (21), and the third electric motor generator (53) is configured to selectably move concomitantly with the engine (54); a first braking device (41) which directly or indirectly brakes the intermediate shaft (61). The power drive system (1000) achieves a differential function in a situation without a conventional mechanical differential, and also has an abundance of drive modes.

Description

Power drive system and vehicle having the same

Technical field

The present invention relates to the field of automotive technology, and more particularly to a power drive system and a vehicle having the same.

Background technique

In the related art, a transmission for a vehicle is provided with a pair of differential mechanisms and a pair of motors, and the differential mechanism has a sun gear, a planetary gear, a carrier, and an internal ring gear. The power output from the engine is input to the sun gear of a pair of differential mechanisms after shifting through the intermediate transmission structure. A pair of motors respectively input driving forces to the ring gears of a pair of differential mechanisms. The transmission eliminates the traditional mechanical differential components and uses two sets of planetary gear mechanisms to couple the two motors to the engine power.

However, the above-mentioned transmission device is suitable for a work vehicle (such as a snow removal vehicle), and the motor output mechanism is a worm gear mechanism, and the unidirectionality of the motor power transmission is realized by self-locking, and is only used for the steering differential speed when the vehicle is cornering, and It is impossible to achieve conditions such as pure electric, hybrid, and parking power generation.

Summary of the invention

The present invention aims to solve at least one of the above technical problems in the prior art to some extent.

The invention proposes a power drive system which realizes the differential function under the premise of canceling the conventional mechanical differential and has a rich transmission mode.

The invention also proposes a vehicle having the above described power drive system.

A power drive system according to an embodiment of the present invention includes: a power coupling device including: a first sun gear, a first planet carrier and a first ring gear, and a second sun gear, a second planet carrier, and a second a ring gear, the first ring gear is coaxially connected to the second ring gear; an intermediate shaft, the intermediate shaft is arranged to be linked with the first ring gear and the second ring gear; an engine, the engine Provided to selectively engage the intermediate shaft; a first motor generator, a second motor generator, and a third motor generator, the first motor generator being associated with the first sun gear, the second A motor generator is coupled to the second sun gear, the third motor generator being configured to selectively interlock with the engine; a first brake device that directly or indirectly brakes the intermediate shaft.

The power drive system according to the embodiment of the present invention realizes the differential function while eliminating the conventional mechanical differential, and has a rich transmission mode.

A vehicle according to another embodiment of the present invention includes the power drive system of the above embodiment.

DRAWINGS

1 is a schematic diagram of a power drive system in accordance with an embodiment of the present invention;

Figure 2 is a partial schematic view of the power drive system of Figure 1, mainly showing the power coupling device;

3 is a schematic diagram of a power drive system in accordance with another embodiment of the present invention;

4 is a schematic diagram of a power drive system in accordance with still 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, the illustrated portion of which may be used for a vehicle rear drive;

16-17 are schematic views of a vehicle in accordance with an embodiment of the present invention.

detailed description

The embodiments of the present invention are described in detail below, and the examples of the embodiments are illustrated in the drawings, wherein the same or similar reference numerals are used to refer to the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the drawings are intended to be illustrative of the invention and are not to be construed as limiting.

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", Directions such as "post", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", etc. The positional relationship is based on the orientation or positional relationship shown in the drawings, and is merely for the convenience of the description of the present invention and the simplified description, and is not intended to indicate or imply that the device or component referred to has a specific orientation, and is constructed and operated in a specific orientation. Therefore, it should not be construed as limiting the invention.

Moreover, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, features defining "first" and "second" may include one or more of the features either explicitly or implicitly. In the description of the present invention, the meaning of "a plurality" is at least two, such as two, three, etc., unless specifically defined otherwise.

In the present invention, the terms "installation", "connected", "connected", "fixed" and the like shall be understood broadly, and may be either a fixed connection or a detachable connection, unless explicitly stated and defined otherwise. , or integrated; can be mechanical connection, can also be electrically connected or can communicate with each other; can be directly connected, or can be indirectly connected through an intermediate medium, can be the internal communication of two elements or the interaction of two elements. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood on a case-by-case basis.

In the present invention, the first feature "on" or "under" the second feature may include direct contact of the first and second features, and may also include first and second features, unless otherwise specifically defined and defined. It is not in direct contact but through additional features between them. Moreover, the first feature "above", "above" and "above" the second feature includes the first feature directly above and above the second feature, or merely indicating that the first feature level is higher than the second feature. The first feature "below", "below" and "below" the second feature includes the first feature directly below and below the second feature, or merely the first feature level being less than the second feature.

A power drive system 1000 according to an embodiment of the present invention, which is suitable for use in a vehicle 10000, such as a hybrid vehicle 10000, which can serve as a power source for the vehicle 10000 and provide a normal vehicle 10000, will be described below with reference to the accompanying drawings. The power required to drive.

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

Referring to FIG. 1 and 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, and a third motor generator. 53. Engine 54 and first brake device 41.

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

Referring to FIG. 2, the power coupling device 100 includes a first sun gear 11, a first planet carrier 14 and a first ring gear 13, a second sun gear 21, a second planet carrier 24, and a second ring gear 23. Wherein, the first sun gear 11, the first planet 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 planet carrier 24 and the second ring gear 23 may constitute a planetary gear The main part of the mechanism 2.

The first planet gear 12 is mounted on the first planet carrier 14 and is disposed between the first sun gear 11 and the first ring gear 13, and the first planet gear 12 meshes with the first sun gear 11 and the first ring gear 13, respectively. The first planet gears 12 may be mounted on the first planet carrier 14 via a planetary axle, and the first planet gears 12 may be plural and evenly spaced along the circumferential spacing of the first sun gear 11. For example, considering the stability of power transmission and the manufacturing cost, the first planetary gears 12 may be three and evenly disposed outside the first sun gear 11, and the adjacent two first planetary gears 12 are spaced apart by approximately 120°.

The manner in which the first planet gear 12 meshes with the first sun gear 11 is externally engaged. The first planetary gear 12 meshes with the first ring gear 13 in a meshing manner, that is, the inner circumference of the first ring gear 13 is formed with teeth, and the inner circumference of the first planetary gear 12 and the first ring gear 13 The teeth on the face engage. The first planet gear 12 can rotate about the axis of the planetary axle or can revolve around the first sun gear 11.

Similarly, referring to FIG. 2, the second planetary gear 22 is mounted on the second planet carrier 24 and disposed between the second sun gear 21 and the second ring gear 23, and the second planetary gear 22 and the second sun gear respectively 21 engages with the second ring gear 23. The second planet gears 22 may be mounted on the second planet carrier 24 via a planetary axle, and the second planet gears 22 may be plural and evenly spaced along the circumferential spacing of the second sun gear 21. For example, considering the stability of power transmission and the manufacturing cost, the second planetary gears 22 may be three and evenly disposed outside the second sun gear 21, and the adjacent two second planetary gears 22 are spaced apart by approximately 120°.

The manner in which the second planet gear 22 meshes with the second sun gear 21 is externally engaged. The meshing manner of the second planetary gear 22 and the second ring gear 23 is internal engagement, that is, the inner circumference of the second ring gear 23 is formed with teeth, and the inner circumference of the second planetary gear 22 and the second ring gear 23 are formed. The teeth on the face engage. The second planet gear 22 can be rotated about the axis of the planet wheel axle or can be revolved around the second sun gear 21.

Wherein, the first ring gear 13 and the second ring gear 23 are coaxially connected, so that the first ring gear 13 and the second ring gear 23 operate synchronously, that is, the motion states of the first ring gear 13 and the second ring gear 23 Always be consistent. For example, the first ring gear 13 and the second ring gear 23 rotate at the same speed and in the same direction. In an embodiment of the invention, The first ring gear 13 and the second ring gear 23 may be formed in a unitary structure to constitute a common ring gear 1323 and shared by the two planetary gear mechanisms 1, 2.

In other embodiments, as shown in FIGS. 1-4, the power coupling device 100 may further include a power transmission portion 3, and the power transmission portion 3 is coaxially coupled with the first ring gear 13 and the second ring gear 23, in other words, The power transmission portion 3 is disposed coaxially with the first ring gear 13 and the second ring gear 23, and the power transmission portion 3 is interlocked with the first ring gear 13 and the second ring gear 23 to move in synchronization.

Of course, it should be understood that there are various ways to achieve the same motion state of the first ring gear 13 and the second ring gear 23 (like turning toward the same speed), as described herein, the first ring gear 13 and the first The two ring gears are formed in one piece to form a common ring gear 1323. Alternatively, the first ring gear 13 and the second ring gear 23 may also be connected by other components (such as the power transmission portion 3 described above), and the power transmission portion 3 is connected to the first ring gear 13 and the second ring gear 23 via a ring gear. The portion 31 is fixed. Furthermore, the above two modes can be combined. As shown in the embodiment of FIGS. 1-3, the first ring gear 13 and the second ring gear 23 are not only integrated to form a common ring gear 1323, but also the first ring gear 13 The second ring gear 23 is also fixed to the power transmission portion 3 via the ring gear connecting portion 31.

It should be noted that the above-mentioned "coupling" can be understood as a plurality of components (for example, two) associated motions. Taking two components as an example, when one of the components moves, the other component also moves.

For example, in some embodiments of the invention, the linkage of the gear to the shaft may be understood to mean that the shaft that is associated therewith will also rotate as the gear rotates, or that the gear that is associated therewith will also rotate as the shaft rotates.

For another example, the linkage of the shaft with the shaft can be understood as the other shaft that is linked with it when one of the shafts rotates.

For another example, the linkage of a gear and a gear can be understood as the other gear that is linked to it will also rotate when one of the gears rotates.

Of course, it should be understood that the two components of the linkage may be relatively stationary as one of the components is relatively stationary.

Referring to FIGS. 1 and 3, the intermediate shaft 61 is disposed in linkage with the first ring gear 13 and the second ring gear 23. The manner in which the intermediate shaft 61 is coupled to the first ring gear 13 and the second ring gear 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 between the engine 54 and the intermediate shaft 61 is possible, at which time the engine 54 is coupled with the intermediate shaft 61, not at the engine 54. When the intermediate shaft 61 is engaged, the engine 54 and the intermediate shaft 61 are disconnected, and the engine 54 and the intermediate shaft 61 are not interlocked at this time.

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

The second motor generator 52 is coupled to the second sun gear 21, and the second motor generator 52 and the second sun gear 21 may be coaxially connected, and the second motor generator 52 may be located at one end of the second sun gear 21.

The third motor generator 53 is disposed to be selectively coupled with the engine 54. When the engine 54 is interlocked with the third motor generator 53, the engine 54 engages the third motor generator 53 and the power is available to the engine 54 and the third motor generator. The transmission between the machines 53 is performed, and when the engine 54 and the third motor generator 53 are disconnected, the engine 54 and the third motor generator 53 are not interlocked.

Thus, the power drive system 1000 according to the embodiment of the present invention has at least four power sources, namely, three motor generators and an engine, thereby greatly enriching the transmission mode and transmission efficiency of the power drive system 1000, with respect to specific typical work. In the following, detailed description will be made below in conjunction with specific embodiments, and will not be described here.

Here, it should be noted that in the description of the "motor generator" of the present invention, the motor generator can be understood as a motor having a function of a generator and a motor unless otherwise specified.

The first brake device 41 is provided for braking the intermediate shaft 61, and the first brake device 41 can directly brake the intermediate shaft 61, and of course the intermediate shaft 61 can be braked indirectly. It will be understood that in a particular embodiment of the invention, the braking of one component (such as a brake or brake) to another component can be understood broadly, that is, as direct braking or indirect braking.

When the first brake device 41 brakes the intermediate shaft 61, since the intermediate shaft 61 is interlocked with the first ring gear 13 and the second ring gear 23, the braking effect by the first brake device 41 is achieved. Braking of a ring gear 13 and a second ring gear 23. In other words, in these embodiments, the first brake device 41 indirectly effects the braking action on the first ring gear 13 and the second ring gear 23 by the braking action on the intermediate shaft 61. Of course, it can be understood that the first brake device 41 can also be arranged to directly brake the first ring gear 13 and the second ring gear 23, thus indirectly braking the intermediate shaft 61.

The first carrier 14 and the second carrier 24 of the power coupling device 100 can serve as a power output of the power coupling device 100, so that when the first brake device 41 brakes the intermediate shaft 61, the first motor generator 51 can The generated power is output through the first planet carrier 14 to a corresponding wheel such as the left wheel 73, and the second motor generator 52 can output the generated power through the second carrier 24 to a corresponding wheel such as the right wheel 74.

At this time, the

wheels

73, 74 on both sides are associated with the first motor generator 51 and the second motor generator 52, respectively, and by controlling the rotational speeds of the first motor generator 51 and the second motor generator 52, two independently controllable The speed of the wheel, thereby achieving a differential speed.

For example, when the vehicle 10000 is traveling on a flat road surface and traveling in a straight line, the first motor generator 51 and the second motor generator 52 can output power at the same rotational speed, so that the speed of the corresponding wheel is determined by the deceleration of the respective planetary gear mechanisms. The upper is equal, thereby ensuring that the vehicle 10000 can smoothly travel in a straight line.

For another example, when the vehicle 10000 is traveling on an uneven road or turning, the rotational speed of the wheels on both sides may theoretically have a rotational speed difference. Taking the left turn as an example, the turning radius of the left wheel 73 is small and the turning radius of the right wheel 74 is large. To ensure pure rolling motion between the wheel and the ground, the rotational speed of the left wheel 73 is smaller than that of the right wheel 74. The rotational speed of the first motor generator 51 at this time may be smaller than the output rotational speed of the second motor generator 52, and the specific rotational speed difference may be indirectly calculated from the steering angle of the steering wheel. If the driver turns the steering wheel counterclockwise (to the left) by a certain angle, the controller of the vehicle 10000 can 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 rotational speed difference between the wheels on both sides is also obtained. determine. Then, the controller may control the first motor generator 51 and the second motor generator 52 to respectively output power to the respective rotation speeds so that the difference between the rotation speeds of the two can be matched with the rotation speed difference required by the wheels, so that the two planetary gears are passed through the two planetary gears. After the deceleration of the mechanism, the two wheels can achieve the desired speed, thus achieving a pure rolling turn.

The above description is made by taking the first motor generator 51 and the second motor generator 52 as electric motors as an example. Of course, the first motor generator 51 and the second motor generator 52 can also operate as a generator, for example, for recycling a wheel system. Dynamic energy.

When the engine 54 is disconnected from the intermediate shaft 61 and the third motor generator 51 engages the engine 54 to interlock with the engine 54, the engine 54 can drive the third motor generator 53 to generate electricity, whereby the power transmission path is short and the charging efficiency is high. . It should be understood that at this time, the wheel is disconnected from the engine 54, and if the vehicle is in the park state, the parking power generation function is realized, or if the first motor generator 51 and the second motor generator 52 are used as the motor to drive the wheel, The driving power generation function is realized.

Further, 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 motor generators can be mixed, whereby the three motor generators, particularly the third motor generator 53 can adjust the speed of the engine 54 to compensate for the torque of the engine 54 so that the engine 54 is in an optimal operating range for improved fuel economy. Further, the first motor generator 51 and the second motor generator 52 can adaptively frequently change the rotational speed, thereby achieving transient adjustment of the wheel rotational speed, improving the power, stability, and safety of the vehicle.

It can be understood that the above planetary gear mechanism 1 and the planetary gear mechanism 2 can adopt the same transmission ratio. For example, with the sun gear as the power input and the planet carrier (the first planet carrier 14 and the second planet carrier 24) as the power take-off, the two planetary gear mechanisms can use the same gear ratio. That is, the number of teeth of the first sun gear 11 and the second sun gear 21, the number of teeth of the first planetary gear 12 and the second planetary gear 22, and the number of teeth of the first ring gear 13 and the second ring gear 23 (internal teeth) may be respectively the same .

In summary, according to the power driving system 1000 of the embodiment of the present invention, the pure electric mode or the braking energy recovery of the first motor generator 51 and the second motor generator 52 can be realized by the braking action of the first braking device 41. The mode, and by separately controlling the output rotational speeds of the first motor generator 51 and the second motor generator 52, the wheels on both sides can be obtained with different torques to realize the differential function. When the braking action of the first brake device 41 is released, the third motor generator 53 and the engine 54 can also be interposed and dynamically coupled with the first motor generator 51 and the second motor generator 52 to jointly output power. , thereby significantly improving the power and passability of the power drive system 1000.

Further, the powers of the first motor generator 51 and the second motor generator 52 are input from the first sun gear 11 and the second sun gear 21, respectively, and 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 outputted from the first carrier 14 and the second carrier 24, and the power input and output are such that the first motor generator 51 and the second motor generator 52 are in different working conditions. A better transmission ratio can be obtained, and the driving efficiency of the first motor generator 51 and the second motor generator 52 when operating as a motor and the power generation efficiency as a generator can be improved.

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

Referring to FIGS. 1 and 3, a clutch is 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 disconnection of the engine 54 with the third motor generator 53 is achieved. This can be achieved by a clutch, and the engagement and disengagement of the engine 54 with the intermediate shaft 61 can be achieved by another clutch.

In order to reduce the number of parts, reduce the manufacturing cost, and improve the integrated production of the module, the above-mentioned engine 54 and the third motor generator 53 and the two clutches between the engine 54 and the intermediate shaft 61 can be integrated, for example, using a dual clutch. 42.

Referring to FIGS. 1 and 3, the dual clutch 42 includes a first engagement portion 421, a second engagement portion 422, and a third engagement portion 423, wherein the first engagement portion 421 and the second engagement portion 422 may be dual clutch 42 Two driven discs, the third engaging portion 423 may be a housing of the dual clutch 42, and at least one of the two driven discs may selectively engage the housing, that is, the first engaging portion 421 and the second engaging portion At least one of the portions 422 can selectively engage the third joint portion 423. Of course, the two driven disks can also be completely disconnected from the housing, that is, both the first engaging portion 421 and the second engaging portion 422 are in an open state with the third engaging portion 423.

The engine 54 is interlocked with the third engaging portion 423. For example, the engine 54 is coaxially coupled to the third engaging portion 423, and the intermediate shaft 61 is interlocked with the first engaging portion 421, and the intermediate shaft 61 is coaxially coupled to the first engaging portion 421.

The third motor generator 53 is interlocked with the second engaging portion 422. Referring to the embodiment of FIG. 1, the third motor generator 53 and the second engaging portion 422 are interlocked by a gear mechanism, which may include a gear 531 and a gear 532, a gear The 532 can be coaxially connected to the second engaging portion 422, the gear 532 is sleeved on the intermediate shaft 61, the gear 531 is fixed on the motor shaft of the third motor generator 53, and the gear 531 is meshed with the gear 532, wherein the second engaging portion 422 A hollow shaft 533 may be disposed between the gear 532 and the hollow shaft 533 is sleeved on the intermediate shaft 61. In the embodiment of FIG. 1, the third motor generator 53 is located on one side of the dual clutch 42.

Referring to the embodiment of FIGS. 3-4, the third motor generator 53 is disposed 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 in the dual clutch. Radial outer side of 42. In some embodiments of the present invention, the dual clutch 42 is housed inside the housing of the third motor generator 53, and more specifically, the dual clutch 42 is housed inside the rotor of the third motor generator 53. In this embodiment, the connection structure of the third motor generator 53 and the second joint portion 422 can still adopt the corresponding structure in the embodiment of FIG. 1, and details are not described herein again. For the motor arrangement in the embodiments of FIGS. 3 and 4, the axial dimension of the power drive system 1000 can be greatly reduced, and the requirements for the axial arrangement space of the power drive system 1000 can be reduced.

The transmission mode between the intermediate shaft 61 and the first ring gear 13 and the second ring gear 23 will be described in detail below with reference to the embodiment of Fig. 1.

In this embodiment, as shown in FIGS. 1 and 3, the intermediate shaft 61 is interlocked with the first ring gear 13 and the second ring gear 23 via the intermediate transmission 62. For the intermediate transmission 62, those skilled in the art can flexibly design based on space arrangement requirements, transmission ratio requirements, transmission reliability requirements, and the like.

In one embodiment of the invention, the intermediate transmission 62 may be a gear transmission that includes an intermediate shaft fixed gear 621 and an outer tooth portion 622. The outer tooth portion 622 is coaxially coupled with the first ring gear 13 and the second ring gear 23, in other words, the outer tooth portion 622 is disposed coaxially with the first ring gear 13 and the second ring gear 23, and the outer tooth portion 622 is first The ring gear 13 and the second ring gear 23 can be interlocked for synchronous movement, that is, rotating in the same direction and at the same speed. In some embodiments of the present invention, the outer tooth portion 622, the first ring gear 13 and the second ring gear 23 may be formed in a unitary structure, and the outer tooth portion 622 is located on the outer peripheral surface of the common ring gear 1323.

The intermediate shaft fixed gear 621 is fixedly disposed on the intermediate shaft 61, and the intermediate shaft fixed gear 621 is meshed with the external tooth portion 622. Thereby, the intermediate transmission device 62 has a simple structure and reliable transmission, is low in space layout requirements, is easy to implement, and is effectively controlled in manufacturing cost.

Of course, in other embodiments, the intermediate transmission 62 can also be a belt transmission mechanism, a chain transmission mechanism, or a CVT (Continuously Variable Transmission, such as a continuously variable transmission) transmission mechanism.

In order to make the power drive system 1000 more compact and smaller in size, the components can be integrated, for example, the power transmission portion 3 and the intermediate shaft 61 are integrally formed. Further, the power transmission portion 3 and the intermediate shaft 61 may be configured 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 ring gear 13 and the second ring gear 23, such as the intermediate shaft 61 and the first ring gear 13 and the second by the ring gear connecting portion 31. The ring gear 23 is fixedly connected.

Referring to FIG. 4, at this time, the intermediate shaft 61 and the power transmission shaft 3 are the same component, the engine 54 is disposed coaxially with the shaft, and the third motor generator 53 is disposed radially outward of the dual clutch 42 by this arrangement. The axial size and radial size of the power drive system 1000 are greatly reduced, so that the power drive system 1000 tends to be smaller, the volume is smaller, the space requirement is lower, and the lightweight design is reduced, and the design is reduced. The overall vehicle quality improves the fuel economy of the engine 54.

Referring to FIGS. 3 and 4, further, the first brake device 41 is disposed between the dual 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 coaxially fixed with the first ring gear 13 and the second ring gear 23 . For example, referring to FIG. 2 and in conjunction with FIGS. 1 and 3, the power transmission shaft 3 is coupled to the common ring gear 1323 via a ring gear connecting portion 31, which may be a plurality of radial connecting arms, radial connecting arms Both ends 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. Of course, the ring gear connecting portion 31 may be configured in a ring shape, the outer peripheral edge of which is fixed to the inner peripheral surface of the common ring gear 1323, and the inner peripheral edge is fixed to the outer peripheral surface of the power transmission shaft 3. In the embodiment of Figures 1 and 3, the power transmission shaft 3 is disposed in parallel with the intermediate shaft 61, and in the embodiment of Figure 4, the power transmission shaft 3 and the intermediate shaft 61 are the same component.

In some embodiments, as shown in FIG. 1, the first brake device 41 can be configured to directly brake the intermediate shaft 61, thereby indirectly achieving braking of the first ring gear 13 and the second ring gear 23. In the embodiment of Fig. 4, since the intermediate shaft 61 and the power transmission shaft 3 are the same member, the first brake device 41 is equivalent to directly braking the two shafts at the same time.

Since the first carrier 14 and the second carrier 24 can serve as the power output of the power drive system 1000, gears can be provided on the planet carrier to facilitate the external output of the planet carrier. As shown in FIG. 2, in an embodiment of the present invention, the first carrier 14 is coaxially disposed with a first carrier output gear 141, and the second carrier 24 is coaxially disposed with a second carrier output. Gear 241. Further, the first carrier output gear 141 is located radially outward of the first carrier 14, and the second carrier output gear 241 is located radially outward of the second carrier 24 due to the first carrier 14 and the second carrier 24 has a relatively large radial dimension, and the two output gears 141, 241 are respectively disposed radially outward of the respective planet carriers, so that the two output gears 141, 241 have a relatively larger radius of rotation, which is convenient for the vehicle The

half shafts

71, 72 of the 10000 or the side gears 711, 721 on the

half shafts

71, 72 are cooperatively driven, thereby improving the reliability of the transmission.

Referring to Figure 1 and in conjunction with the embodiment of Figure 2, the power coupling device 100 has two planetary gear mechanisms 1, 2 while the first motor generator 51 (specifically its rotor) and the second motor generator 52 (specifically its rotor) ) is coaxially connected to the first sun gear 11 and the 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. Therefore, in some embodiments of the present invention, the housings of the first motor generator 51 and the second motor generator 52 may constitute an integral structure and cover the two planetary gear mechanisms 1, 2 to form a common housing. That is, the common housing can be used as the integral housing of the power coupling device 100, and the two planetary gear mechanisms 1, 2, and the two

motor generators

51, 52 can be housed in the common housing, thereby reducing the number of components and The power drive system 1000 has a more compact structure, smaller size, easier processing and manufacturing, greatly saves manufacturing costs, and realizes a highly integrated design of the product, enabling the power drive system 1000 to achieve efficient modular production, which is greatly in manufacturing and assembly. Increased efficiency.

Of course, in another embodiment of the present invention, the first sun gear 11, the first planet carrier 14, the first planet gear 12, and the first ring gear 13 may be housed inside the first motor generator 51, that is, the first motor power generation Inside the casing of the machine 51, the second sun gear 21, the second planet gear 22, the second planet carrier 24, and the second ring gear 23 may be housed inside the second motor generator 52, such as the casing of the second motor generator 52. Inside the body.

Therefore, the highly integrated design of the product can be realized, and the power drive system 1000 can realize efficient modular production, and the efficiency is greatly improved in the manufacturing and assembly steps, thereby effectively reducing the cost.

The detailed construction and typical operating conditions of the power drive system 1000 in the embodiment of Fig. 1 will be described in detail below with reference to 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 includes a first sun gear 11, a first planet gear 12, a first planet carrier 14 and a first ring gear 13, the first sun gear 11 being in an intermediate position, and the first planet gear 12 and the first sun gear respectively 11 meshes with the first ring gear 13, the first planet gear 12 is mounted on the first planet carrier 14, the first planet carrier 14 is coaxially fixed with a first planet carrier output gear 141, and the first planet carrier output gear 141 is left. The side gears 711 on the half shaft 71 are engaged, and the left side wheel 73 is connected to the outside of the left half shaft 71.

The planetary gear mechanism 2 includes a second sun gear 21, a second planetary gear 22, a second planet carrier 24, and a second ring gear 23, the second sun gear 21 being at an intermediate position, and the second planet gear 22 and the second sun gear 22, respectively 21 is meshed with the second ring gear 23, the second planet gear 22 is mounted on the second planet carrier 24, the second planet carrier 24 is coaxially fixed with the second planet carrier output gear 241, and the second planet carrier output gear 241 is right The side gears 721 on the half shaft 72 are engaged, and the right side wheel 74 is connected to the outside of the right half shaft 72.

The number of teeth of each of the motion pair of the planetary gear mechanism 1 and the corresponding motion pair of the planetary gear mechanism 2 may be the same, so that the planetary gear mechanism 1 and the planetary gear mechanism The structure 2 has the same gear ratio when transmitting power according to the same transmission path.

The first ring gear 13 and the second ring gear 23 may be formed in an integral structure to constitute a common ring gear 1323. The common ring gear 1323 is coaxially fixed with the power transmission shaft 3, and the common ring gear 1323 and the power transmission shaft 3 may be disposed. The ring gear connecting portion 31 is connected.

An intermediate shaft fixed gear 621 is fixedly disposed on the intermediate shaft 61. The intermediate shaft fixed gear 621 is meshed with the external tooth portion 622 fixed to the common ring gear 1323.

The first brake device 41 is a brake and serves 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 to the first sun gear 11, and the first motor generator 51 is sleeved coaxially with the first sun gear 11 on the power transmission shaft 3, and the second motor generator 52 and the second sun The wheel 21 is coaxially fixed, and the second motor generator 52 and the second sun gear 21 are also coaxially sleeved on the power transmission shaft 3.

The left end of the intermediate shaft 61 is coaxially connected to the first engaging portion 421 of the dual clutch 42. The motor shaft of the third motor generator 53 is fixedly provided with a gear 531, the gear 531 meshes with the gear 532, and the gear 532 passes through the hollow shaft 533 and the The two engaging portions 422 are coaxially connected, and the gear 532 and the hollow shaft 533 are sleeved on the intermediate shaft 61. The engine 54 is coaxially coupled to the third engagement portion 423.

Wherein, the first engaging portion 421 and the second engaging portion 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 the first At least one of the engagement portion 421 and the second engagement portion 422 (ie, the housing of the dual clutch may selectively engage at least one of the two driven disks).

As can be seen from the structure of the embodiment of Fig. 1, the power drive system 1000 eliminates the conventional mechanical differential, but can selectively input the power of the engine 54 and the third motor generator 53 to the common ring gear. 1323, the purpose of braking the common ring gear 1323 can also be achieved by selectively braking the intermediate shaft 61 by the first braking device 41, so that the sun gears of the two side planetary gear mechanisms are independently independent of the first motor generator 51. The second motor generator 52 is interlocked, and finally the carrier of the two sets of planetary gear mechanisms is used as the power output end to output power. That is, various driving conditions can be realized by different operating modes and rotational speed adjustments of the dual clutch 42, the first brake device 41, and the three motor generators.

Pure electric operating conditions:

The engine 54 and the third motor generator 53 do not operate, and the dual clutch 42 is in an open state. The first brake device 41 brakes the intermediate shaft 61 such 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 operate independently to drive the wheels on the corresponding side.

Hybrid working condition 1:

The first engaging portion 421 is engaged with the third engaging portion 423 and the second engaging portion 422 is disconnected from the third engaging portion 423, and the engine 54, the first motor generator 51, and the second motor generator 52 operate, the third motor generator 53 does not work. 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 dynamically coupled with the first motor generator 51, and then output from the first carrier 14 to the left wheel 73. Another portion of the power of the engine 54 is dynamically coupled with the second motor generator 52 and output from the second carrier 24 to the right wheel 74.

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 may pass through the first motor generator 51 and the second motor generator 52 when the vehicle speed needs to be constantly changed in a short time. The speed adjustment is completed, thereby ensuring that the engine 54 can always operate at a relatively high speed, improving the fuel economy of the engine 54.

Mixed working condition two:

The first engaging portion 421 and the second engaging portion 422 all engage the third engaging portion 423 (ie, the dual clutch 42 is fully engaged), the engine 54, the first motor generator 51, the second motor generator 52, and the third motor generator 53 All work. The power output from the engine 54 is output to the power coupling device 100 via the intermediate shaft 61, and the third motor generator 53 can now operate in the form of a generator that uses a portion of the power from the engine 54 to generate power (the portion of the power is transmitted via the dual clutch 42). To the third motor generator 53), 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 in the form of a motor at this time. Working and power coupling with the engine 54 to output power from the respective planet carriers.

Or at this time, the third motor generator 53 can also output power as a motor, supplement the torque of the engine 54, and adjust the speed of the engine 54. At this time, the first motor generator 51 and the second motor generator 52 are also in the form of a motor. Working, the power is output to the respective wheels after the first carrier 14 and the second carrier 24 are coupled.

Since the three motor generators and the engine 54 are in a rotational speed coupling relationship, when the vehicle speed needs to be changed for a short time, the speed of the motor generator can be adjusted. For example, the third motor generator 53 performs speed regulation in the form of a motor, or the first motor generator 51 and the second motor generator 52 perform speed regulation. Of course, three motor generators can also perform speed regulation at the same time. This ensures that the engine 54 can always be driven at a relatively high speed to achieve better fuel economy.

Extended program conditions:

In the pure electric 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, and the engine 54 outputs the power drive. The third motor generator 53 performs power generation to supplement the first motor generator 51 and the second motor generator 52 with necessary electric energy, which may also be referred to as driving power generation.

Parking power generation condition 1:

When the vehicle is in the park state (eg, by the parking brake system brake wheels 73, 74), the second engagement portion 422 engages the third engagement portion 423 and the first engagement portion 421 is disconnected from the third engagement portion 423, the engine The generated power is output to the third motor generator 53 to drive the third motor generator 53 to generate electricity. Thereby, 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 can be understood that the first motor generator 51 and the second motor generator 52 do not operate at this time.

Parking power generation condition 2:

When the vehicle is in the park 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, and the first engaging portion 421 and the second engaging portion 422 are all engaged. The third engaging portion 423, a part of the power of the engine 54 is output to the third motor generator 53, and another part of the power of the engine is output to the common ring gear 1323 through the intermediate shaft 61, and then transmitted to the common ring gear 1132 by the common ring gear 1323 to the first sun gear 11 to The first motor generator 51 is transmitted from the second sun gear 21 to the second motor generator 52, thereby driving the first motor generator 51 and the second motor generator 52 to simultaneously generate electric power. In other words, under this condition, the engine 54 simultaneously drives three motors to generate electricity, thereby greatly increasing the charging power, effectively shortening the charging time, and realizing the fast charging function.

Parking power generation conditions three:

When the vehicle is in the park 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, and the first engaging portion 421 engages the third engaging portion 423 and is The second engaging portion 422 is disconnected from the third engaging portion 423, and the power generated by the engine 54 is output to the common ring gear 1323 through the intermediate shaft 61, and then transmitted to the first motor generator 51 through the first sun gear 11 through the common ring gear 1323. And transmitted to the second motor generator 52 by the second sun gear 21, thereby driving the first motor generator 51 and the second motor generator 52 to simultaneously generate electricity.

3 shows an embodiment of another power drive system 1000. Compared with the embodiment of FIG. 1, the intermediate shaft 61 of the power drive system 1000 in the embodiment of FIG. 3 is linked to the common ring gear 1323 via the intermediate transmission 62. The rest of the structure and typical working conditions are substantially the same as those of the embodiment of FIG. 1, and will not be described again here.

4 shows an embodiment of another power drive system 1000. The third motor generator 53 of the power drive system 1000 of the embodiment of FIG. 4 is coaxially fitted over the dual clutch 42 as compared to the embodiment of FIG. The radially outer side, 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 rest of the structure and typical working conditions are The embodiment of Figure 1 is substantially the same and will not be described again here.

In summary, the power drive system 1000 according to the embodiment of the present invention utilizes the first motor generator 51 and the second motor generator 52 to perform speed-variable torque transformation and dynamic coupling of two sets of planetary gear mechanisms, and strives to The power drive system 1000 becomes the simplest and most compact. Such a hybrid power drive system 1000 can not only achieve independent control of the respective side wheels of the first motor generator 51 and the second motor generator 52, but also ensure that the engine 54 is in a high fuel economy speed range to the greatest extent. jobs. 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 handling and driving experience of the system are greatly improved. At the same time, the system has the power generation function of the third motor generator 53 and the twisting function of the engine 54. Each power source can scientifically and reasonably meet the speed ratio requirement, and the mechanical control components such as the shifting components are few, and the structure is simple and compact. The space utilization rate is extremely high.

It will be appreciated that the power drive system 1000 described above can be used for a front or rear drive of a vehicle, preferably for a front drive of a vehicle. When the above-described power drive system 1000 is used for the front drive, the drive system 100a shown in FIGS. 5-15 below can be used for the rear drive to jointly drive the vehicle.

In short, the above-described power coupling device 100 of the power drive system 1000 can drive a pair of front wheels of the vehicle, and the drive system 100a shown in FIGS. 5-15 Then a pair of rear wheels of the vehicle can be driven. However, the present invention is not limited thereto. For example, the power coupling device 100 can also drive a pair of rear wheels of the vehicle, and the drive system 100a shown in FIGS. 5-15 can drive a pair of front wheels.

The drive system 100a shown in Figures 5-7 will first be described in detail with reference to specific embodiments.

As shown in FIGS. 5-7, the 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, and a second. Brake device 63a, third brake device 64a, and power engagement device 65a.

As shown in FIGS. 5-7, 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 planetary gear 12a, a third planet carrier 14a, and a Three-ring ring 13a. The third planetary gear 12a is mounted on the third carrier 14a and disposed between the third sun gear 11a and the third ring gear 13a, and the third planetary gear 12a meshes with the third sun gear 11a and the third ring gear 13a, respectively. The third planetary gear 12a may be mounted on the third planet carrier 14a via a planetary axle, and the third planetary gear 12a may be plural and evenly distributed along the circumferential direction of the third sun gear 11a, for example, considering the stability of power transmission. As well as the manufacturing cost, the third planetary gears 12a may be three and evenly disposed outside the third sun gear 11a, and the adjacent two third planetary gears 12a are spaced apart by about 120°.

The meshing manner of the third planetary gear 12a and the third sun gear 11a is external engagement. The meshing manner of the third planetary gear 12a and the third ring gear 13a is internal engagement, that is, the inner circumference of the third ring gear 13a is formed with teeth, and the inner circumferences of the third planetary gear 12a and the third ring gear 13a are formed. The teeth on the face engage. The third planet gear 12a can rotate about the axis of the planetary axle or revolve around the sun gear.

Similarly, as shown in FIGS. 5-7, 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 planetary gear 22a, and a fourth planet carrier. 24a and fourth ring gear 23a. The fourth planetary gear 22a is mounted on the fourth carrier 24a and 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 gear 22a may be mounted on the fourth planet carrier 24a via a planetary axle, and the fourth planetary gear 22a may be plural and evenly distributed along the circumferential direction of the fourth sun gear 21a, for example, considering the stability of power transmission. As well as the manufacturing cost, the fourth planetary gears 22a may be three and evenly disposed outside the fourth sun gear 21a, and the adjacent two fourth planetary gears 22a are spaced apart by approximately 120°.

The meshing manner of the fourth planetary gear 22a and the fourth sun gear 21a is external engagement. The meshing manner of the fourth planetary gear 22a and the fourth ring gear 23a is internal engagement, that is, the inner circumferential surface of the fourth ring gear 23a is formed with teeth, and the inner circumference of the fourth planetary gear 22a and the fourth ring gear 23a The teeth on the face engage. The fourth planet gear 22a can rotate about the axis of the planetary axle or revolve around the sun gear.

In some embodiments of the present invention, the third planet gear 12a may include a first gear portion 121a and a second gear portion 122a that are coaxially arranged and synchronously rotated, the first gear portion 121a meshing with the third sun gear 11a, and second The gear portion 122a meshes with the third ring gear 13a. The first gear portion 121a and the second gear portion 122a may be fixedly connected by the same shaft. The first gear portion 121a may be a small tooth portion and the second gear portion 122a may be a large tooth portion, that is, the number of teeth of the first gear portion 121a is smaller than the number of teeth of the second gear portion 122a, thereby the fourth motor generator When the power outputted by the 31a is transmitted through the first gear portion 121a and the second gear portion 122a, the first gear portion 121a and the second gear portion 122a constitute a speed reduction mechanism, and the deceleration and torsion effect of the fourth motor generator 31a is realized. . Of course, optionally, the first gear portion 121a may also be a large tooth portion and the second gear portion 122a may be a small tooth portion.

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 rotated, the third gear portion 221a meshes with the fourth sun gear 21a, and the fourth gear portion 222a and the fourth gear portion 222a The ring gear 23a is engaged. The third gear portion 221a and the fourth gear portion 222a may be fixedly connected by the same shaft. The third gear portion 221a may be a small tooth portion and the fourth gear portion 222a may be a large tooth portion, that is, the number of teeth of the third gear portion 221a is smaller than the number of teeth of the fourth gear portion 222a, thereby the fifth motor generator When the power outputted by the 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 the deceleration and torsion effect of the fifth motor generator 32a is realized. . Of course, optionally, the third gear portion 221a may also be a large tooth portion and the fourth gear portion 222a may be a small tooth portion.

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

Wherein, the third planet carrier 14a and the fourth planet carrier 24a may be used as the power output end of the driving system 100a, for example, the third planet carrier 14a and the fourth planet carrier 24a may be from a power source such as the fourth motor generator 31a and The power of the fifth motor generator 32a is externally outputted, for example, to the

wheels

41a, 42a. In some embodiments of the present invention, 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 coupled to the second pair of vehicles. The two

wheels

41a, 42a in the wheel are respectively coupled such that the third carrier 14a and the fourth carrier 24a can output the power of the drive system 100a to the second pair of

wheels

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

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

In the following description of "linkage" in the present invention, this understanding is made unless otherwise specified.

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

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

The drive system 100a may include a first power output shaft 43a and a second power output shaft 44a disposed between the third planet carrier 14a and one of the second pair of wheels of the vehicle 10000, second The power output shaft 44a is disposed between the fourth planet carrier 24a and the other of the second pair of wheels 42a. The second pair of wheels may be a pair of front wheels, and may of course be a pair of rear wheels.

As shown in FIGS. 5-7, the power engaging device 65a is disposed to engage the first power output shaft 43a and the second power output shaft 44a such that a first power output shaft 43a and a second power output shaft 44a are formed. Rigidly connected, 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 in a synchronized operation state, and when the power engagement device 65a is in the OFF state, the first power output shaft 43a is The second power output shaft 44a is capable of differential rotation, that is, the first power output shaft 43a and the second power output shaft 44a are respectively rotatable at different rotation speeds (of course, the same rotation speed can be rotated).

Here, it should be noted that the power engagement device 65a for engaging the first power output shaft 43a and the second power output shaft 44a should be understood in a broad sense, such as the power engagement device 65a can directly engage or disengage the first power output shaft 43a and The second power output shaft 44a, of course, the power engagement device 65a may also indirectly achieve engagement and disconnection of the first power output shaft 43a and the second power output shaft 44a by engaging or disengaging the other two components, The two components may be components that are coupled to the first power output shaft 43a and the second power output shaft 44a, such as the third planet carrier 14a and the fourth planet carrier 24a.

A vehicle having a drive system 100a according to an embodiment of the present invention, for example, when the vehicle 10000 is traveling on a flat road surface and traveling in a straight line, the second brake device 63a and the third brake device 64a can respectively brake the third ring gear 13a and The fourth ring gear 23a, and the fourth motor generator 31a and the fifth motor generator 32a can output power at the same rotational speed, so that the speed of the corresponding wheel is theoretically equal by the deceleration of the respective planetary gear mechanisms, thereby ensuring The vehicle 10000 can smoothly travel in a straight line.

For another example, when the vehicle 10000 is traveling on an uneven road or turning, the second brake device 63a and the third brake device 64a can respectively brake the third ring gear 13a and the fourth ring gear 23a, and the wheels on both sides. In theory, there will be a difference in rotational speed. Taking the left turn as an example, the turning radius of the left wheel is small and the turning radius of the right wheel is large. In order to ensure pure rolling motion between the wheel and the ground, the rotational speed of the left wheel is required. The 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, such as The driver rotates the steering wheel counterclockwise (turns to the left) at a certain angle, and the controller of the vehicle 10000 can 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 rotational speed difference between the wheels on both sides is also determined. At this time, the controller can control the fourth motor generator 31a and the fifth motor generator 32a to respectively output power to the respective rotation speeds, so that the difference between the rotation speeds of the two can be matched with the rotation speed difference required by the wheels, so that the two planets pass through After the deceleration of the gear mechanism, the two wheels can achieve the desired speed, thus achieving a pure rolling turn.

The fourth motor generator 31a and the fifth motor generator 32a are described as an example of the electric motor. Of course, the fourth motor generator 31a and the fifth motor generator 32a may operate as a generator. 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 The generator works to recover the braking energy.

Of course, it can be understood that the first planetary gear mechanism 1a and the second planetary gear mechanism 2a described above can adopt the same transmission ratio, for example, with the sun gear as the power input end and the planetary carrier as the power output end, two The planetary gear mechanism can use the same gear ratio. That is, the number of teeth of the third sun gear 11a and the fourth sun gear 21a, the number of teeth of the third planetary gear 12a and the fourth planetary gear 22a, and the number of teeth (internal teeth) of the third ring gear 13a and the fourth ring gear 23a may be respectively the same .

The vehicle 10000 may sometimes travel in poor road conditions, such as on a road surface that is relatively muddy or soft gravel road or sand. Taking muddy road conditions as an example, when the vehicle 10000 is traveling on a muddy road, the vehicle 10000 may be trapped in the soil and cause idling, that is, the vehicle 10000 has a slip phenomenon (slip phenomenon and the cause of the slip phenomenon are already known to those skilled in the art). openly known). For the conventional differential with self-locking function, when the wheel is slippery, it is only necessary to control the differential self-locking, so that at least the vehicle 10000 can be improved to a certain extent.

However, although the drive system 100a according to an embodiment of the present invention has a differential function, it is structurally different from the conventional differential, so that the conventional differential self-locking structure cannot be utilized. Therefore, in order to improve the passability of the vehicle 10000 and improve the adaptability of the vehicle 10000 to poor road conditions, the drive system 100a according to some embodiments of the present invention can further implement the self-locking function under the premise of implementing the differential function.

According to some embodiments of the present invention, as shown in FIGS. 5-7, when one side of the vehicle is slipping, the power engagement device 65a engages the first power output shaft 43a and the second power output shaft 44a, and the second brake The 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 unslip wheel Improve wheel slippage and improve vehicle passing ability.

In summary, according to the drive system 100a of the embodiment of the present invention, the pure electric power of the fourth motor generator 31a and the fifth motor generator 32a can be realized by the braking action of the second brake device 63a and the third brake device 64a. The mode or the braking energy recovery mode, and by separately controlling the output rotational speeds of the fourth motor generator 31a and the fifth motor generator 32a, the wheels on both sides can be obtained with different torques to realize the differential function. In addition, the drive system 100a according to the embodiment of the present invention has fewer components, is compact and simple in structure, and is small in size and easier to arrange.

In addition, the drive system 100a according to the embodiment of the present invention may not have the mechanical self-locking differential structure of the conventional power transmission system, but the function of the conventional mechanical self-locking differential can be realized by the synchronization of the power engagement device 65a. Thereby, the structure of the powertrain system 100a according to the embodiment of the present invention is made more compact and cost-effective.

In some embodiments of the invention, the power engagement device 65a may be a clutch. The clutch includes an active portion 651a and a driven portion 652a that are engageable and disengageable from each other, the active portion 651a is coupled to the first power output shaft 43a, and the driven portion 652a is coupled to the second power output shaft 44a.

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

In some embodiments of the present invention, the fourth motor generator 31a and the third sun gear 11a may be coaxially sleeved on the first power output shaft 43a, and the fifth motor generator 32a and the fourth sun gear 21a may be the same The shaft ground is sleeved on the second power output shaft 44a, thereby making the structure of the drive system 100a more compact.

In addition, the fourth motor generator 31a and the fifth motor generator 32a may be symmetrically distributed left and right, as symmetrically arranged with respect to the power engagement device 65a, and the first planetary gear mechanism 1a and the second planetary gear mechanism 2a may also be symmetrically distributed left and right, such as The power engagement devices 65a are symmetrically arranged, and the fourth motor generator 31a and the fifth motor generator 32a may be respectively located outside the first planetary gear mechanism 1a and the second planetary gear mechanism 2a, that is, for example, as shown in FIG. The fourth motor generator 31a is located on the left side of the first planetary gear mechanism 1a, and the fifth motor generator 32a is located on the outer side, that is, the right side of the second planetary gear mechanism 2a.

In some embodiments of the present invention, the first power output shaft 43a and the second power output shaft 44a may be half shafts, for example, the first power output shaft 43a may be a left half shaft, and the second power output shaft 44a may be a right half. axis.

The construction, connection relationship and typical working conditions of the drive system 100a in the embodiment of FIG. 5 will be described below 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 two

brake devices

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

Specifically, the first planetary gear mechanism 1a on the left side includes a third sun gear 11a, a third planetary gear 12a, and a third ring gear 13a, and the third sun gear 11a is disposed 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 disposed on the first power output shaft 43a. The third planetary gear 12a is a double-toothed gear and is mounted on the third carrier 14a, and the third planetary gear 12a is meshed with the third sun gear 11a and the third ring gear 13a, respectively.

Similarly, the second planetary gear mechanism 2a on the right side includes a fourth sun gear 21a, a fourth planetary gear 22a, and a fourth ring gear 23a, and the fourth sun gear 21a is disposed on the second power output shaft 44a, and the The fourth sun gear 21a is connected to the fifth motor generator 32a, and the fifth motor generator 32a is also disposed on the second power output shaft 44a. The fourth planetary gear 22a is a double-toothed 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 engagement device 65a is disposed at the first planetary gear mechanism 1a and the second planetary gear mechanism Between 2a and for selectively engaging the first power output shaft 43a and the second power output shaft 44a.

The first power output shaft 43a is connected to the left side wheel 41a and the third carrier 14a, and the second power output shaft 44a is connected to the right side wheel 42a and the fourth carrier 24a.

Typical operating conditions of the drive system 100a in the embodiment of Fig. 5 are described below.

Pure electric operating conditions (depending on the fourth motor generator 31a and the fifth motor generator 32a):

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 engagement device 65a is in an open state. The fourth motor generator 31a and the fifth motor generator 32a are each operable in the form of a motor. Thereby, the power generated by the fourth motor generator 31a is transmitted to the left side wheel 41a through the third sun gear 11a, the third planetary gear 12a, the third carrier 14a, and the first power output shaft 43a, and the fourth motor generator The rotational speed of 31a changes in a positive correlation with the rotational speed of the left wheel 41a. The power generated by the fifth motor generator 32a is transmitted to the right wheel 42a through the fourth sun gear 21a, the fourth planetary gear 22a, the fourth carrier 24a, and the second power output shaft 44a, and the rotational speed of the fifth motor generator 32a. It changes in a positive correlation with the rotational speed of the wheel 42a on the right side.

Since the fourth motor generator 31a and the fifth motor generator 32a operate independently at this time, and the two do not interfere with each other, the two motors can adaptively adjust the output speed according to the torque required by the respective wheels to achieve the difference. Speed function.

It can be understood that, under this operating condition, the fourth motor generator 31a and the fifth motor generator 32a can be rotated clockwise or counterclockwise, thereby achieving pure electric forward or pure electric reverse.

Slip condition:

Taking the left wheel 41a as a slip for 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 fourth electric device The power generated by the generator 31a can be output to the second planetary gear mechanism 2a on the right side through the power engagement device 65a in the engaged state, and can be coupled with the power generated by the fifth motor generator 32a and outputted to the right side without slipping. Wheel 42a.

Thereby, when the left wheel is slipping, the fourth motor generator 31a on the left side can still output power from the wheel that is not slipped on the right side, and the fourth motor generator 31a does not need to be reversed, thereby greatly improving the timeliness of the escape. And the success rate.

Neutral coasting:

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

Brake energy recovery:

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 engagement device 65a can be in the off state. The kinetic energy is output to the corresponding motor generator through the respective power output shafts and planetary gear mechanisms, thereby driving the motor generator to generate electricity.

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

As shown in FIGS. 8-10, the drive system 100a according to further embodiments of the present invention may include a fourth motor generator 31a and a fifth motor generator 32a, a first power output shaft 43a and a second power output shaft 44a, A plurality of sets of the first planetary gear mechanism 1a and the plurality of sets of the second planetary gear mechanisms 2a and the second brake device 63a, the third brake device 64a, and the power engagement device 65a.

As shown in FIGS. 8 to 10, a plurality of sets of first planetary gear mechanisms 1a (A1, A2 shown in FIGS. 8-10) are disposed in series between the fourth motor generator 31a and the first power output shaft 43a, which The plurality of sets of the first planetary gear mechanisms 1a are provided to be capable of outputting the power from the fourth motor generator 31a to the first power output shaft 43a by the shifting action, since the plurality of sets of the first planetary gear mechanisms 1a are arranged in series, While the power of the four motor generators 31a is output to the first power output shaft 43a, the plurality of sets of the first planetary gear mechanisms 1a can sequentially shift the power to function as a multi-step shifting function. For example, each of the first planetary gear mechanisms functions as a deceleration and torsion, and thus the plurality of sets of the first planetary gear mechanisms 1a form a multi-stage deceleration effect, thereby increasing the output torque of the fourth motor generator 31a.

Similarly, a plurality of sets of second planetary gear mechanisms 2a are disposed 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 being arranged to be capable of coming from the fifth motor generator 32a The power is output to the second power output shaft 44a by the shifting action, and since the plurality of sets of the second planetary gear mechanisms 2a are disposed in series, the power of the fifth motor generator 32a is outputted to the second power output shaft 44a, The plurality of sets of the second planetary gear mechanisms 2a can sequentially shift the power of the part to function as a multi-step shifting function. For example, each of the second planetary gear mechanisms functions as a deceleration and torsion, so that the plurality of sets of the second planetary gear mechanisms 2a form a multi-stage deceleration effect, thereby increasing the output torque of the fifth motor generator 32a.

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

The first power output shaft 43a may be coupled to one of the second pair of wheels of the vehicle, and the second power output shaft 44a may be coupled to the other of the second pair of wheels 42a, at which time the power coupling device 100 is Drive the first pair of wheels. The first pair of wheels is a pair 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 FIGS. 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 planetary gear, and a planet. The frame and the ring gear (the plurality of sets of the first planetary gear mechanisms 1a share the ring gear, that is, the first common ring gear 13a).

The planet wheels are mounted on the planet carrier and are disposed between the sun gear and the ring gear, and the planet wheels mesh with the sun gear and the ring gear, respectively. The planet wheels can be mounted on the planet carrier by the planetary axles. The planet wheels can be multiple and evenly distributed along the circumferential direction of the sun gear. For example, considering the stability of power transmission and the manufacturing cost, the planet wheels can be three and The cloth is placed on the outside of the sun gear, and the adjacent two planet wheels are spaced approximately 120° apart.

The meshing of the planet gear with the sun gear is external engagement. The meshing manner of the planetary gear and the ring gear is internal engagement, that is, the inner circumferential surface of the ring gear is formed with teeth, and the planetary gear meshes with the teeth on the inner circumferential surface of the ring gear. The planet wheels can rotate around the axis of the planet wheel or revolve around the sun gear.

Similarly, the second planetary gear mechanism 2a may also include a sun gear, a planetary gear, a carrier, and a ring gear (the plurality of sets of second planetary gear mechanisms 2a share the ring gear, that is, the second common ring gear 23a). Further, the relative positional relationship, the connection relationship, the acting relationship, and the like between the components may be identical to those of the first planetary gear mechanism 1a, and thus will not be described in detail herein. Further, the connection relationship and the like of the plurality of sets of the first planetary gear mechanism 1a and the plurality of sets of the second planetary gear mechanisms 2a will be described in detail below in conjunction with specific embodiments.

As shown in FIGS. 8 to 10, the plurality of sets of the first planetary gear mechanisms 1a share the same first common ring gear 13a, and the plurality of sets of the second planetary gear mechanisms 2a share the same second common ring gear 23a. Thereby, the structure of the drive system 100a is made more compact, smaller in size, and more convenient to arrange.

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 23a. In some embodiments of the invention, the second brake device 63a and the third brake device 64a may be brakes, but are not limited thereto.

As shown in FIGS. 8-10, the power engagement device 65a is provided for engaging the first power output shaft 43a and the second power output shaft 44a such that a formation between the first power output shaft 43a and the second power output shaft 44a is formed. Rigid connection, and thus 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 in a synchronized operation state, and when the power engagement device 65a is in the OFF state, the first power output shaft 43a is The second power output shaft 44a is capable of differential rotation, that is, the first power output shaft 43a and the second power output shaft 44a are respectively rotatable at different rotation speeds (of course, the same rotation speed can be rotated).

Here, it should be noted that the power engagement device 65a for engaging the first power output shaft 43a and the second power output shaft 44a should be understood in a broad sense, such as the power engagement device 65a can directly engage or disengage the first power output shaft 43a and The second power output shaft 44a, of course, the power engagement device 65a may also indirectly achieve engagement and disconnection of the first power output shaft 43a and the second power output shaft 44a by engaging or disengaging the other two components, The two components may be respectively connected to the first power output shaft 43a and the second power output shaft 44a, such as the carrier A23 and the carrier B23.

The vehicle having the drive system 100a according to an embodiment of the present invention, for example, when the vehicle 10000 is traveling on a flat road surface and traveling in a straight line, the second brake device 63a and the third brake device 64a can respectively brake the first common ring gear 13a And the second common ring gear 23a, the fourth motor generator 31a and the fifth motor generator 32a can output power at the same rotational speed, so that the rotational speeds of the corresponding wheels are theoretically equal by the deceleration of the respective sets of planetary gear mechanisms. Thereby, it is ensured that the vehicle 10000 can smoothly travel in a straight line.

For another example, when the vehicle 10000 is traveling on an uneven road or turning, 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. The rotational speed of the wheel will theoretically have a difference in rotational speed. Taking the left turn as an example, the turning radius of the left wheel is small and the turning radius of the right wheel is large. To ensure pure rolling motion between the wheel and the ground, the left wheel is The rotation speed is smaller than the rotation speed of the right wheel. At this time, 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 from the steering angle of the steering wheel, such as the driver. Turning the steering wheel counterclockwise (rotating to the left) at a certain angle, the controller of the vehicle 10000 can 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 rotational speed difference between the wheels on both sides is also determined. The controller can control the fourth motor generator 31a and the fifth motor generator 32a to respectively output power at a matched rotational speed, so that the difference between the two speeds can be related to the wheel Matching the rotational speed difference required, so that through the action of two planetary gear speed reduction mechanism, the two wheels can obtain a desired speed, in order to achieve pure rolling cornering.

The fourth motor generator 31a and the fifth motor generator 32a are described as an example of the electric motor. Of course, the fourth motor generator 31a and the fifth motor generator 32a may operate as a generator. 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, the fourth motor generator 31a and the fifth motor generator 32a, respectively. It can then work as a generator to recover braking energy. That is, when the fourth motor generator 31a and the fifth motor generator 32a output power as a motor or recover energy as a generator and generate power, both the second brake device 63a and the third brake device 64a are at In the braking state, the corresponding common ring gear is braked separately, and the power engagement device 65a is in the disengaged state.

Of course, it can be understood that the plurality of sets of the first planetary gear mechanism 1a and the plurality of sets of the second planetary gear mechanism 2a can adopt the same transmission ratio, that is, the sun gear is used as the power input end and the carrier is used as the power output. In the end, the two sets of planetary gear mechanisms can use the same gear ratio. For example, the number of teeth of the sun gear A11 and the sun gear B11, the number of teeth of the planetary gear A12 and the planetary gear B12, the number of teeth of the sun gear A21 and the sun gear B21, the number of teeth of the planetary gear A22 and the planetary gear B22, the first common ring gear 13a and the second common ring gear 23a The number of teeth can be the same.

In particular, when the vehicle 10000 is traveling in a poor road condition, for example, when the vehicle 10000 is traveling on a road surface that is relatively muddy or soft gravel road or sand, taking the muddy road condition as an example, the vehicle 10000 may be trapped in the soil and cause idling. That is, the slip phenomenon of the vehicle 10000 (slip phenomenon and the cause of the slip phenomenon are well known to those skilled in the art).

For the conventional differential with self-locking function, when the wheel is slippery, it is only necessary to control the differential self-locking, so that at least the vehicle 10000 can be improved to a certain extent.

Since the drive system 100a according to an embodiment of the present invention has a differential function, it is structurally different from the conventional differential, and the conventional differential self-locking structure cannot be utilized. In order to improve the passability of the vehicle 10000 and improve the adaptability of the vehicle 10000 to poor road conditions, the drive system 100a of some embodiments of the present invention can further implement the self-locking function under the premise of implementing the differential function.

According to some embodiments of the present invention, as shown in FIGS. 8-10, the power engagement device 65a engages the first power output when the vehicle appears to be slipping on one side of the vehicle. The shaft 43a and 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 unslip side wheel, improve the wheel slip phenomenon, and improve the passing ability of the vehicle.

In summary, according to the drive system 100a of the embodiment of the present invention, the pure electric mode of the fourth motor generator 31a and the fifth motor generator 32a can be realized by the braking action of the second brake device 63a and the third brake device 64a. Alternatively, the braking energy recovery mode, and by separately controlling the output rotational speeds of the fourth motor generator 31a and the fifth motor generator 32a, different torques can be obtained for the wheels on both sides to realize the differential function. In addition, the drive system 100a according to the embodiment of the present invention has fewer components, is compact and simple in structure, and is small in size and easier to arrange.

In particular, the drive system 100a according to an embodiment of the present invention may not be provided with a mechanical self-locking differential structure of a conventional powertrain, but functionally achieves a conventional mechanical self-locking by the synchronization of the power engagement device 65a. The function of the speeder, thereby making the structure of the powertrain system 100a according to an embodiment of the present invention more compact and less costly.

As shown in FIGS. 8 to 10, the series arrangement of the plurality of sets of the first planetary gear mechanism 1a and the plurality of sets of the second planetary gear mechanisms 2a will be described in detail below. It can be understood that the series connection manner of the plurality of sets of the first planetary gear mechanism 1a and the plurality of sets of the second planetary gear mechanism 2a can be the same, so that the drive system 100a can have a high degree of symmetry, and the center of gravity of the drive system 100a is more biased toward the drive system. The intermediate portion of 100a is directly in the intermediate region, whereby the stability of the vehicle can be improved and the front-to-back weight ratio is more reasonable.

Further, the sun gear A11 of the first group of first planetary gear mechanisms A1 of the plurality of sets of first planetary gear mechanisms 1a is interlocked with the fourth motor generator 31a, and the rotor of the fourth motor generator 31a may be the same as the sun gear A11. The axes are connected. The carrier A23 of the last set of first planetary gear mechanisms A2 of the plurality of sets of first planetary gear mechanisms 1a is connected to the first power output shaft 43a, such as coaxially.

Similarly, the sun gear B11 of the first group of second planetary gear mechanisms B1 of the plurality of sets of second planetary gear mechanisms 2a is interlocked with the fifth motor generator 32a, such as the rotor of the fifth motor generator 32a and the sun gear B11 Coaxially connected. The carrier B23 of the last set of second planetary gear mechanisms B2 of the plurality of sets of second planetary gear mechanisms 2a is connected to the second power output shaft 44a, such as coaxially.

In a further embodiment, the carrier A13 of the first set of first planetary gear mechanisms A1 of the plurality of sets of first planetary gear mechanisms 1a is connected to the sun gear A21 of the latter set of planetary gear mechanisms A2, such as coaxially connected, Among the plurality of sets of second planetary gear mechanisms 2a, the carrier B13 of the former set of second planetary gear mechanisms B1 is connected to the sun gear B21 of the latter set of second planetary gear mechanisms B2, such as coaxially.

For example, as shown in FIGS. 8-10, the first planetary gear mechanism 1a and the second planetary gear mechanism 2a are both groups, the carrier A13 of the first group of first planetary gear mechanisms A1 and the last group (that is, the first The two sets of the sun gear A21 of the first planetary gear mechanism A2 are connected. Similarly, the carrier B13 of the first set of second planetary gear mechanisms B1 is coupled to the sun gear B21 of the last set (i.e., the second set) of the second planetary gear mechanism B2.

It should be noted that although a feasible planetary gear mechanism series connection is given in the above embodiment, the feasible implementation manner is only a schematic description, and is not to be understood as a limitation on the protection scope of the present invention. Or suggesting that the invention must employ the above described tandem approach. Those skilled in the art can modify and/or combine the above-mentioned serial connection manner based on the above description of the specification, and the new scheme formed should belong to the equivalent implementation manner of the above serial connection, and should fall under the protection of the present invention. Within the scope.

Further, it should be noted that in the description of the "motor generator" of the present invention, the motor generator can be understood as a motor having a function of a generator and a motor unless otherwise specified.

As an alternative embodiment, as shown in Figures 8-9, the power engagement device 65a can be a clutch. The clutch includes an active portion 651a and a driven portion 652a that are engageable and disengageable from each other, the active portion 651a is coupled to the first power output shaft 43a, and the driven portion 652a is coupled to the second power output shaft 44a.

Of course, the present invention is not limited thereto. In other embodiments, as shown in FIG. 10, the power engagement device 65a may be a synchronizer that is disposed in the first power output shaft 43a and the second power output shaft 44a. One up and used to join the other.

In addition, the fourth motor generator 31a and the fifth motor generator 32a may be symmetrically distributed left and right, as symmetrical with respect to the power engagement device 65a, and the plurality of sets of the first planetary gear mechanism 1a and the plurality of sets of the second planetary gear mechanism 2a may also be bilaterally symmetrical. The distribution is symmetrically arranged as with respect to the power engagement device 65a, and the fourth motor generator 31a and the fifth motor generator 32a may be respectively located outside the plurality of sets of the first planetary gear mechanism 1a and the plurality of sets of the second planetary gear mechanisms 2a, that is, For example, taking FIG. 8 as an example, the fourth motor generator 31a is located on the outer side, that is, the left side of the plurality of sets of the first planetary gear mechanisms 1a, and the fifth motor generator 32a is located on the outer side, that is, the right side of the plurality of sets of the second planetary gear mechanisms 2a. .

As an alternative embodiment, the first power output shaft 43a and the second power output shaft 44a may be half shafts, for example, 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 relationship and typical working conditions of the drive system 100a in the embodiment of Fig. 8 will be described below 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 and A2 on the left side, two single-row planetary gear mechanisms B1 and B2 on the right side, and two motor generators 31a. 32a and

brake devices

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

Specifically, the two first planetary gear mechanisms A1, A2 on the left side are arranged in series and share the same first common ring gear 13a, the sun gear A11 and the fourth motor generator 31a of the first group of first planetary gear mechanisms A1. Coaxially connected, the planetary gears A12 of the first group of first planetary gear mechanisms A1 are mounted on the planet carrier A13, and the planetary gears A12 mesh with the sun gear A11 and the first common ring gear 13a, respectively, the planet carrier A13 and the second group first The sun gear A21 of the planetary gear mechanism A2 is coaxially connected, and the planetary gear A22 of the second group first planetary gear mechanism A2 is mounted on the carrier A23, and the planetary gear A22 meshes with the sun gear A21 and the first common ring gear 13a, respectively. The frame A23 is coaxially connected to the first power output shaft 43a, and the first power output shaft 43a is connected to the left side wheel 41a. The first motor generator 43a, the sun gear A11, and the sun gear A21 are coaxially sleeved on the first power output shaft 43a, and the first power output shaft 43a may be the left half shaft.

The two second planetary gear mechanisms 2a on the right side are arranged in series and share the same second common ring gear 23a. The sun gear B11 of the first group second planetary gear mechanism B1 is coaxially connected with the fifth motor generator 32a, first The planetary gears B12 of the second planetary gear mechanism B1 are mounted on the carrier B13, and the planetary gears B12 mesh with the sun gear B11 and the second common ring gear 23a, respectively, and the sun of the carrier B13 and the second group of second planetary gear mechanisms B2 The wheel B21 is coaxially connected, and the planetary gears B22 of the second group of second planetary gear mechanisms B2 are mounted on the carrier B23, and the planetary gears B22 mesh with the sun gear B21 and the second common ring gear 23a, respectively, the carrier B23 and the second power The output shaft 44a is coaxially connected, and the second power output shaft 44a is coupled to the right wheel 42a. The fifth motor generator 32a, the sun gear B11, and the sun gear B21 are coaxially sleeved on the second power output shaft 44a, and the second power output shaft 44a may be the right half shaft.

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

Typical operating conditions of the drive system 100a in the embodiment of Fig. 8 are described below.

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, and the power engagement device 65a is in an open state. The fourth motor generator 31a and the fifth motor generator 32a are each operable in the form of a motor. Thereby, the power generated by the fourth motor generator 31a is output to the left wheel 41a by the deceleration of the two sets of first planetary gear mechanisms 1a, and the rotational speed of the fourth motor generator 31a is positively correlated with the rotational speed of the left wheel 41a. Variety. The power generated by the fifth motor generator 32a is output to the right wheel 42a by the deceleration of the two sets of second planetary gear mechanisms 2a, and the rotational speed of the fifth motor generator 32a changes in a positive correlation with the rotational speed of the right wheel 42a. .

Since the fourth motor generator 31a and the fifth motor generator 32a operate independently at this time, the two motors do not interfere with each other, so the two motors can adaptively adjust the output speed according to the required torque of the respective wheels to realize the differential function. .

Slip condition:

Taking the left wheel 41a as a slip for 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, and the power engagement device 65a is engaged. The power generated by the four motor generators 31a can be output to the second planetary gear mechanism on the right side by the engagement of the power coupling device 65a, and can be outputted together with the power generated by the fifth motor generator 32a at the carrier B23. To the unslip wheel 42a on the right side.

Neutral coasting:

Brake energy recovery:

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 can be in an open state, and the braking energy passes through the respective power output shafts, The planetary gear mechanism is output to the corresponding motor generator to drive the motor generator to generate electricity.

The drive system 100a of other embodiments will be described in detail below with reference to FIGS. 11-15.

Referring to FIGS. 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, and the middle. The transmission assembly 4b and the second brake device 61a.

Referring to FIGS. 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 planetary gear 12a, a third planet carrier 14a, and a Three-ring ring 13a. The third planetary gear 12a is mounted on the third carrier 14a and disposed between the third sun gear 11a and the third ring gear 13a, and the third planetary gear 12a meshes with the third sun gear 11a and the third ring gear 13a, respectively. The third planetary gear 12a may be mounted on the third planet carrier 14a via a planetary axle, and the third planetary gear 12a may be plural and evenly distributed along the circumferential direction of the third sun gear 11a, for example, considering the stability of power transmission. As well as the manufacturing cost, the third planetary gears 12a may be three and evenly disposed outside the third sun gear 11a, and the adjacent two third planetary gears 12a are spaced apart by about 120°.

Similarly, referring to FIGS. 11-15, 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 planetary gear 22a, and a fourth planet carrier. 24a and fourth ring gear 23a. The fourth planetary gear 22a is mounted on the fourth carrier 24a and 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 gear 22a may be mounted on the fourth planet carrier 24a via a planetary axle, and the fourth planetary gear 22a may be plural and evenly distributed along the circumferential direction of the fourth sun gear 21a, for example, considering the stability of power transmission. As well as the manufacturing cost, the fourth planetary gears 22a may be three and evenly disposed outside the fourth sun gear 21a, and the adjacent two fourth planetary gears 22a are spaced apart by approximately 120°.

In some embodiments of the present invention, as shown in FIG. 11, the third planetary gear 12a may include a first gear portion 121a and a second gear portion 122a that are coaxially arranged and synchronously rotated, the first gear portion 121a and the third sun The wheel 11a is engaged, and the second gear portion 122a is meshed with the third ring gear 13a. The first gear portion 121a and the second gear portion 122a may be fixedly connected by the same shaft. The first gear portion 121a may be a small tooth portion and the second gear portion 122a may be a large tooth portion, that is, the number of teeth of the first gear portion 121a may be smaller than the number of teeth of the second gear portion 122a, thereby the fourth motor power generation When the power output from the machine 31a is transmitted through the first gear portion 121a and the second gear portion 122a, the first gear portion 121a and the second gear portion 122a constitute a speed reduction mechanism, and the deceleration of the fourth motor generator 31a is realized. Twist effect. Of course, in some embodiments of the invention, the first gear portion 121a may also be a large tooth portion and the second gear portion 122a may be a small tooth portion.

Similarly, as shown in FIG. 11, the fourth planetary gear 22a may include a third gear portion 221a and a fourth gear portion 222a which are coaxially arranged and synchronously rotated, and the third gear portion 221a is meshed with the fourth sun gear 21a, fourth The gear portion 222a is meshed with the fourth ring gear 23a. The third gear portion 221a and the fourth gear portion 222a may be fixedly connected by the same shaft. The third gear portion 221a may be a small tooth portion and the fourth gear portion 222a may be a large tooth portion, that is, the number of teeth of the third gear portion 221a may be smaller than the number of teeth of the fourth gear portion 222a, thereby the fifth motor power generation When the power output from the machine 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 the deceleration and the torque reduction of the fifth motor generator 32a are realized. effect. Of course, in some embodiments of the invention, the third gear portion 221a may also be a large tooth portion and the fourth gear portion 222a may be a small tooth portion.

In some embodiments of the present invention, the first gear portion 121a and the second gear portion 122a may be integrally formed to form a double-toothed gear. Similarly, the third gear portion 221a and the fourth gear portion 222a may also be integrally formed to form a double-toothed gear. The structure is simple, compact and reliable.

Wherein, the third planet carrier 14a and the fourth planet carrier 24a may be used as the power output end of the power drive system 100a. For example, the third planet carrier 14a and the fourth planet carrier 24a may be from a power source such as the fourth motor generator 31a. And/or the power of the fifth motor generator 32a is output to the outside, such as to the

wheels

41a, 42a. In some embodiments of the invention, the third planet carrier 14a and the fourth planet carrier 24a are respectively associated with two of the second pair of

wheels

41a, 42a such that the third planet carrier 14a and the fourth planet carrier 24a The power of the power drive system 100a can be output to the

wheels

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

For example, the above-described power coupling device 100 can drive a first pair of wheels, and the third planet carrier 14a and the fourth planet carrier 24a can respectively drive a second pair of wheels, wherein the first pair of wheels are a pair of front wheels and a pair of rear wheels One pair, the second pair of wheels is the remaining pair.

Referring to FIGS. 11 to 15, the fourth motor generator 31a is interlocked with the third sun gear 11a, and the rotor of the fourth motor generator 31a may be coaxially connected to the third sun gear 11a, but is not limited thereto.

Referring to Figures 11-15, the intermediate transmission assembly 4b is disposed in linkage with the third ring gear 13a and the fourth ring gear 23a, respectively, and the intermediate transmission assembly 4b may be disposed between the third ring gear 13a and the fourth ring gear 23a. The third ring gear 13a, the intermediate transmission assembly 4b and the fourth ring gear 23a are simultaneously or relatively stationary.

The second brake device 61a is provided for braking the intermediate transmission assembly 4b, and when the second brake device 61a brakes the intermediate transmission assembly 4b, the third ring gear 13a and the fourth ring gear 23a are also indirectly braked, and After the second brake device 61a releases the intermediate transmission assembly 4b, the intermediate transmission assembly 4b, the third ring gear 13a and the fourth ring gear 23a are associated in motion.

Thereby, when the second brake device 61a is in the braking state, the intermediate transmission assembly 4b, the third ring gear 13a and the fourth ring gear 23a are both braked, and the power generated by the fourth motor generator 31a can pass through the third The sun gear 11a and the third planet gear 12a are output from the third carrier 14a to the corresponding wheel, such as the left wheel 41a. The power generated by the fifth motor generator 32a can pass through the fourth sun gear 21a and the fourth planet gear 22a. Thereafter, it is output from the fourth carrier 24a to the corresponding wheel such as the wheel 42a on the right side, and the two motor generators independently control the rotational speeds of the corresponding wheels, thereby realizing the differential function.

For example, when the vehicle 10000 is traveling on a flat road surface and traveling in a straight line, the fourth motor generator 31a and the fifth motor generator 32a can have the same rotational speed. The power is output so that the rotational speeds of the corresponding wheels are theoretically equal by the deceleration 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 is traveling on an uneven road or turning, the rotational speed of the wheels on both sides is theoretically different from the rotational speed. Taking the left turn as an example, the turning radius of the left wheel is small and the turning of the right wheel is The radius of the fourth motor generator 31a can be smaller than the output speed of the fifth motor generator 32a. In order to ensure a pure rolling motion between the wheel and the ground, the rotational speed of the left wheel is smaller than the rotational speed of the right wheel. The specific speed difference can be indirectly calculated from the steering angle of the steering wheel. If the driver turns the steering wheel counterclockwise (turning to the left) at a certain angle, the controller of the vehicle 10000 can 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 rotational speed difference between the wheels on both sides is also determined. At this time, the controller can control the fourth motor generator 31a and the fifth motor generator 32a to respectively output power to the respective rotating speeds, so that the two The difference in speed can be matched to the required speed difference of the wheel, so that after the deceleration of the two planetary gear mechanisms, the two wheels can be obtained The desired speed is achieved to achieve a pure rolling turn.

The fourth motor generator 31a and the fifth motor generator 32a are described as an example of the electric motor. Of course, the fourth motor generator 31a and the fifth motor generator 32a may operate as a generator. 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 operate in the form of a generator to recover the braking energy.

Of course, it can be understood that the first planetary gear mechanism 1a and the second planetary gear mechanism 2a can adopt the same transmission ratio, that is, the sun gear is used as the power input end and the carrier is used as the power output end. Both planetary gear mechanisms can use the same gear ratio. That is, the number of teeth of the third sun gear 11a and the fourth sun gear 21a, the number of teeth of the third planetary gear 12a and the fourth planetary gear 22a, and the number of teeth (internal teeth) of the third ring gear 13a and the fourth ring gear 23a may be respectively the same .

In summary, according to the power driving system 100a of the embodiment of the present invention, the pure electric mode or braking energy recovery of the fourth motor generator 31a and the fifth motor generator 32a can be realized by the braking action of the second brake device 61a. The mode, and by individually controlling the output rotational speeds of the fourth motor generator 31a and the fifth motor generator 32a, it is possible to obtain different torques for the wheels on both sides, achieving the differential function. In addition, the power drive system 100a according to the embodiment of the present invention has fewer components, is compact and simple in structure, and is small in size and easier to arrange.

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

The vehicle 10000 can sometimes travel in poor road conditions, such as on a road surface that is relatively muddy or soft gravel road or sand. Taking muddy road conditions as an example, when the vehicle 10000 is traveling on a muddy road, the vehicle 10000 may be trapped in the soil and cause idling, that is, the vehicle 10000 has a slip phenomenon (slip phenomenon and the cause of the slip phenomenon are already known to those skilled in the art). openly known). For the conventional differential with self-locking function, when the wheel is slippery, it is only necessary to control the differential self-locking, so that at least the vehicle 10000 can be improved to a certain extent.

However, although the power drive system 100a according to an embodiment of the present invention has a differential function, it is structurally different from the conventional differential, so that the conventional differential self-locking structure cannot be utilized. Therefore, in order to improve the passability of the vehicle 10000 and improve the adaptability of the vehicle 10000 to poor road conditions, the power drive system 100a according to some embodiments of the present invention can further implement the self-locking function under the premise of implementing the differential function.

According to some embodiments of the present invention, as shown in FIG. 14 and FIG. 15, for example, the power drive system 100a further includes a third brake device 62a configured to brake the third planet carrier 14a or The fourth planet carrier 24a, that is, the skid phenomenon occurs in the vehicle 10000 under certain operating conditions, and the third brake device 62a is capable of selectively braking the third planet carrier 14a or the fourth planet carrier 24a. More specifically, the third brake device 62a brakes the planet carrier corresponding to the wheel at this time.

For example, the third carrier 14a and the fourth carrier 24a are respectively connected to the two

wheels

41a, 42a of the second pair of wheels of the vehicle 10000. When one of the wheels has a slip phenomenon, the third brake device 62a is formed. The corresponding planet carrier of the moving wheel, so that the motor generator corresponding to the sliding wheel can output the generated power through the intermediate transmission component 4b to the planet carrier on the other side, so that the power is coupled with the motor generator on the other side, and The coupled power is output to the other side of the wheel, i.e., the unslip wheel, thereby improving the ability of the vehicle 10000 to escape.

Referring to FIGS. 14-15, if the wheel 41a on the left side slips, the third brake device 62a brakes the third carrier 14a on the left side, and according to the motion characteristics of the planetary gear mechanism, the fourth electric power generation on the left side at this time. The power generated by the machine 31a can be output through the third ring gear 13a, and the third ring gear 13a is interlocked with the fourth ring gear 23a on the right side through the intermediate transmission assembly 4b, so that the power generated by the fourth motor generator 31a can be transmitted to the right. The fourth ring gear 23a on the side, at this time, the fifth motor generator 32a on the right side can also output power, and the two parts of the power are coupled to the right fourth carrier 24a and output to the right unsliding wheel 42a, that is, Said that two The motor can output power through the unslip wheel, which greatly improves the ability of the vehicle 10,000 to get out of the trap.

It can be understood that at this time the second brake device 61a releases the intermediate transmission assembly 4b, that is, the second brake device 61a does not brake the intermediate transmission assembly 4b at this time.

In some embodiments of the present invention capable of implementing a differential self-locking function, the third brake device 62a may be a parking brake system (not shown) of the vehicle 10000, the parking brake system being configured to be selectively One of the wheels of the pair of wheels (cooperating with the third carrier 14a and the fourth carrier 24a) is separately braked to achieve a braking action on the carrier connected to the wheel. For example, when the left wheel is slipping, the parking brake system can brake only the left planet carrier corresponding to the left wheel (eg, the third planet carrier 14a), or when the right wheel slips, the parking brake The system can only brake the right side of the right side of the planet carrier (eg, the fourth planet carrier 24a).

Of course, the present invention is not limited thereto. For example, the third brake device 62a may also be the service brake system of the vehicle 10000, and the process of implementing the differential self-locking function is basically the same as the above-described parking brake system. The purpose of this is not described in detail.

It should be noted that the parking brake system or the service brake system described above may be different from the parking brake system or the service brake system that is known and widely used. Taking the parking brake system as an example, the widely used parking brake system generally brakes a pair of wheels, such as a pair of rear wheels at the same time (for example, braking the rear brake shoes by a cable) However, the parking brake system according to the embodiment of the present invention needs to be able to achieve independent braking of two of the pair of wheels, for example, separately braking the left rear wheel (when the right rear wheel can be in a non-braking state) ) or brake the right rear wheel separately (the left rear wheel can be in the non-braking state). Since the construction and operating principles of conventional parking brake systems are known to those of ordinary skill in the art, one of ordinary skill in the art will only need to make simple modifications and/or modifications to conventional parking brake systems, thereby enabling implementation in accordance with the present invention. The parking brake system of the example is capable of selectively braking the two wheels of a pair of wheels individually. For example, the parking brake system has two subsystems, each of which corresponds to a single wheel. For example, one of the subsystems can be braked by one cable pulling the left rear brake shoe, and the other subsystem can be passed. The other cable pulls the right rear wheel brake shoe for braking (here, the cable is only illustrative, for example, any other existing methods that can be realized and their equivalents can be used, and of course, the electric form can also be used) .

For similar reasons, the service brake system may also be different from the widely used service brake system. Of course, those skilled in the art are aware of the difference between the parking brake system and the conventional parking brake system of the embodiment of the present invention. The difference between the service brake system and the conventional service brake system of the embodiment of the present invention is also understandable and achievable, and thus will not be described in detail herein.

In an embodiment in accordance with another aspect of the present invention, the power drive system 100a may also be implemented by providing other components having a brake function when implementing the differential self-locking function.

As in some embodiments, as shown in FIG. 14, the third brake device 62a is configured to selectively engage the third planet carrier 14a or the fourth planet carrier 24a to the housing of the power drive system 100a, thereby enabling Braking action on the third planet carrier 14a or the fourth planet carrier 24a.

Further, as shown in FIG. 15, the third brake device 62a may be two, for example,

third brake devices

621a, 622a, and respectively correspond to the third carrier 14a and the fourth carrier 24a, that is, each planet The frame corresponds to a

third brake device

621a, 622a which can operate independently of each other and without interference. Of course, as shown in FIG. 14, the third carrier 14a and the fourth carrier 24a may share the same third brake device 62a. In some embodiments of the invention, the third brake device 62a may be a synchronizer or a brake or the like, but is not limited thereto.

As described above, when the vehicle 10000 is slipping, the corresponding carrier of the skid wheel can be braked by the third brake device 62a, thereby realizing the purpose of the motor generator corresponding to the slip wheel passing power through the other unsliding wheel. At this time, the motor generator corresponding to the slip wheel and the motor generator corresponding to the unsliding wheel may simultaneously output power. Thus, in an embodiment in accordance with the invention, when one side wheel slip occurs, each of the motor generators can each operate as a motor and rotate in the same direction from start to finish. Therefore, the motor generators corresponding to the two motor generators, especially the slip wheels, do not need to be reversed, which not only simplifies the control strategy, but also shortens the time when the vehicle 10000 is trapped, and helps to quickly and efficiently remove the trap.

Of course, it can be understood that when the fourth motor generator 31a and the fifth motor generator 32a participate in driving the vehicle 10000 to advance, the two motor generators can also rotate in the same direction from start to finish.

In this way, when the wheel is traveling forward and suddenly enters a poor road condition, if one side of the wheel is slipping, the planet carrier corresponding to the slipping wheel is braked by controlling the third brake device 62a, so that the side is electrically generated. The machine transmits power to the other side quickly through the intermediate transmission assembly 4b, and directly outputs it after being coupled with the power of the motor generator on the other side. During this period, since the motor generator corresponding to the slip wheel does not need to be reversed, that is, there is no need to stop and re-rotate, the two motor generators can quickly perform power coupling and jointly drive the unslip when the wheel slip occurs. Wheels, greatly improved the vehicle 10,000 Timeliness.

For the case of how to achieve a dynamic coupling of the motor generator quickly without reversing, those 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 invention is illustrated by way of a specific embodiment. It is to be understood that the following examples are merely illustrative and are not to be construed as limiting the scope of the invention or The system 100a must employ an intermediate transmission assembly 4b having the following configuration. Those skilled in the art should be able to modify and/or replace the technical features in the following embodiments and their equivalents after reading the above-described principles of the specification and the following specific embodiments, and the embodiments formed after the modification are also It should fall within the scope of protection of the present invention.

For example, referring to FIGS. 11-15, the intermediate transmission assembly 4b may include an intermediate shaft 41b on which the intermediate shaft first gear 42b and the intermediate shaft second gear 44b are disposed, wherein the intermediate shaft first gear 42b is passable The intermediate idler gear 43b is interlocked with the third ring gear 13a, and the intermediate shaft second gear 44b is interlocked with the fourth ring gear 23a. Of course, in other embodiments of the present invention, the intermediate shaft second gear 44b is interlocked with the fourth ring gear 23a via the intermediate idle gear 43b, and the intermediate shaft first gear 42b is interlocked with the third ring gear 13a.

The intermediate shaft first gear 42b and the intermediate shaft second gear 44b may be fixedly disposed on the intermediate shaft 41b, and the radial sizes of the intermediate shaft first gear 42b and the intermediate shaft second gear 44b are preferably different. For example, the radial dimension of the countershaft gear that meshes with the intermediate idler gear 43b is relatively small. Referring to the embodiment shown in Figures 11-15, the radial dimension of the intermediate shaft first gear 42b is smaller than that of the intermediate shaft second gear 44b. Radial size. Thereby, it is possible to ensure that the axial direction of the intermediate shaft 41b is consistent with the power output shaft (half shaft) or the axial direction of the motor generator, and the reliability and stability of the transmission are improved.

Further, the outer peripheral surfaces of the third ring gear 13a and the fourth ring gear 23a are respectively provided with

external teeth

131a, 231a, and the intermediate shaft first gear 42b is interlocked with the external teeth 131a of the third ring gear 13a via the intermediate idler gear 43b, such as The intermediate idler gear 43b meshes with the intermediate shaft first gear 42b and the external teeth 131a of the third ring gear 13a, respectively. The intermediate shaft second gear 44b is interlocked with the external teeth 231a of the fourth ring gear 23a, and the intermediate shaft second gear 44b is directly meshed with the external teeth 231a of the fourth ring gear 23a.

In the embodiment of Figures 11-15, the second brake device 61a can be a brake and used to brake the intermediate shaft 41b. This makes the power drive system 100a relatively more compact and easy to arrange.

The following is a schematic illustration of the transmission between the planet carrier and the wheel.

The power drive system 100a may include a first power output shaft 43a and a second power output shaft 44a disposed between the third planet carrier 14a and one of the second pair of wheels of the vehicle 10000, the first The two power output shafts 44a are disposed between the fourth planet carrier 24a and the other of the second pair of wheels 42a. The pair of wheels may be a pair of front wheels, and of course may be a pair of rear wheels.

In some embodiments of the present invention, the fourth motor generator 31a and the third sun gear 11a may be coaxially sleeved on the first power output shaft 43a, and the fifth motor generator 32a and the fourth sun gear 21a may be the same The shaft ground is sleeved on the second power output shaft 44a, thereby making the structure of the power drive system 100a more compact. In addition, the fourth motor generator 31a and the fifth motor generator 32a may be symmetrically distributed left and right, and the first planetary gear mechanism 1a and the second planetary gear mechanism 2a may be symmetrically distributed left and right, and the fourth motor generator 31a and the fifth electric motor The generators 32a may be located outside 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 outside the first planetary gear mechanism 1a, that is, on the left side. The fifth motor generator 32a is located on the outer side, that is, the right side of the second planetary gear mechanism 2a.

In some embodiments of the present invention, as shown in FIG. 15, a first reduction gear assembly 51a, a second power output shaft 44a and a fourth planet may be disposed between the first power output shaft 43a and the third carrier 14a. A second reduction gear assembly 52a is also disposed between the brackets 24a. The structure of the first reduction gear assembly 51a and the structure of the second reduction gear assembly 52a can be the same, whereby the versatility of the reduction gear assembly can be improved and the cost can be reduced. Moreover, by providing such a gear reduction assembly between the power output end of the power drive system 100a and the wheel, the effect of decelerating and increasing the twist can be better achieved.

The construction, connection relationship and typical working conditions of the power drive system 100a in the embodiment of Fig. 11 will be described below 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, and two

brake devices

61a, 62a. Wait.

Specifically, the first planetary gear mechanism 1a on the left side includes a third sun gear 11a, a third planetary gear 12a, and a third ring gear 13a, and the third sun gear 11a is disposed 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 disposed in the air. A power output shaft 43a. The third planetary gear 12a is a double-toothed gear and is mounted on the third carrier 14a, and the third planetary gear 12a is meshed with the third sun gear 11a and the third ring gear 13a, respectively.

The intermediate shaft 41b is fixedly provided with an intermediate shaft first gear 42b and an intermediate shaft second gear 44b, the second brake device 61a may be a brake and used to brake the intermediate shaft 41b, and the intermediate shaft first gear 42b may pass through the intermediate idler 43b is interlocked with the external teeth 131a of the third ring gear 13a, and the intermediate shaft second gear 44b is directly coupled to the external teeth 231a of the fourth ring gear 23a.

The third brake device 62a is provided for selectively braking the third planet carrier 14a or the fourth planet carrier 24a, it being understood that such braking may be direct braking or, of course, indirect move.

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

The second brake device 61a brakes the intermediate shaft 41b such 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 are each operable in the form of a motor. Thereby, the power generated by the fourth motor generator 31a is transmitted to the left side wheel 41a through the third sun gear 11a, the third planetary gear 12a, the third carrier 14a, and the first power output shaft 43a, and the fourth motor generator The rotational speed of 31a changes in a positive correlation with the rotational speed of the left wheel 41a. The power generated by the fifth motor generator 32a is transmitted to the right wheel 42a through the fourth sun gear 21a, the fourth planetary gear 22a, the fourth carrier 24a, and the second power output shaft 44a, and the rotational speed of the fifth motor generator 32a. It changes in a positive correlation with the rotational speed of the wheel 42a on the right side.

Since the fourth motor generator 31a and the fifth motor generator 32a operate independently at this time, and the two do not interfere with each other, the two motors can adaptively adjust the output speed according to the torque required by the respective wheels to achieve the differential speed. Features.

Slip condition:

Taking the left wheel 41a as a slip as an example, 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 passes the generated power through the third sun gear 11a, the third planet gear 12a, the third carrier 14a, the third ring gear 13a, the intermediate idler gear 43b, the intermediate shaft first gear 42b, and the intermediate shaft 41b. The intermediate shaft second gear 44b and the fourth ring gear 23a are output to the fourth carrier 24a, and the power from the fifth motor generator 32a is also output to the fourth carrier 24a, and the two parts are dynamically coupled from the second power. The output shaft 44a is output to the wheel 42a on the right side. Thereby, when the left wheel is slipping, the fourth motor generator 31a on the left side can still output power from the wheel that is not slipped on the right side, and the fourth motor generator 31a does not need to be reversed, thereby greatly improving the timeliness of the escape. And the success rate.

Neutral coasting:

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

Brake energy recovery:

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

A vehicle 10000 according to an embodiment of the present invention will be briefly described below. Referring to FIG. 16, the vehicle 10000 includes the power drive system 1000 and the drive system 100a in the above embodiment, and the power drive system 1000 in FIGS. 1-4 can be used. The front drive, and thus the power coupling device 100 of the power drive system 1000 drives one For the front wheels, the drive system 100a of Figures 5-15 can be used for the rear drive. Further, referring to the vehicle 10000 shown in FIG. 17, it may include only the portion of the power drive system 1000 for the front drive. Of course, the invention is not limited thereto. It should be understood that other configurations of the vehicle 10000, such as the brake system, the travel system, the steering system, and the like, according to embodiments of the present invention are known in the art and are well known to those skilled in the art, and therefore will not be described herein. .

In the description of the present specification, the description with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" and the like means a specific feature described in connection with the embodiment or example. A structure, material or feature is included in at least one embodiment or example of the invention. In the present specification, the schematic representation of the above terms is not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples. Further, various embodiments or examples described in this specification can be joined and combined by those skilled in the art. Although the embodiments of the present invention have been shown and described, it is understood that the above-described embodiments are illustrative and are not to be construed as limiting the scope of the invention. The embodiments are subject to variations, modifications, substitutions and variations.

Claims

A power drive system, comprising:

a power coupling device comprising: a first sun gear, a first planet carrier and a first ring gear, and a second sun gear, a second planet carrier and a second ring gear, the first ring gear and the first ring gear The second ring gear is coaxially connected;

An intermediate shaft, the intermediate shaft being disposed in linkage with the first ring gear and the second ring gear;

An engine configured to selectively engage the intermediate shaft;

a first motor generator, a second motor generator, and a third motor generator, wherein the first motor generator is linked to the first sun gear, and the second motor generator is linked to the second sun gear, The third motor generator is configured to selectively interlock with the engine;

A first brake device that brakes the intermediate shaft directly or indirectly.
A power drive system according to claim 1, wherein a clutch is provided between said engine and said third motor generator and said engine and said intermediate shaft.
The power drive system of claim 2, further comprising:

a dual clutch including: a first engagement portion, a second engagement portion, and a third engagement portion, the third engagement portion being configured to selectively engage the first engagement portion and the second engagement portion At least one of the engine, the engine is interlocked with the third engaging portion, the intermediate shaft is interlocked with the first engaging portion, and the third motor generator is interlocked with the second engaging portion.
A power drive system according to claim 3, wherein said engine is coaxially coupled to said third engaging portion; said intermediate shaft is coaxially coupled to said first engaging portion; said third electric power generation The machine and the second engaging portion are interlocked by a gear mechanism.
A power drive system according to any one of claims 1 to 4, further comprising: an intermediate transmission through which said intermediate shaft passes said first ring gear and said second The ring gear is linked.
The power drive system of claim 5 wherein said intermediate transmission is a gear transmission.
The power drive system of claim 6 wherein said intermediate transmission comprises:

An external tooth portion coaxially coupled with the first ring gear and the second ring gear; and

An intermediate shaft fixed gear disposed on the intermediate shaft, the outer tooth portion meshing with the intermediate shaft fixed gear.
The power drive system of claim 5 wherein said intermediate transmission is a belt drive, a chain drive or a CVT drive.
The power drive system according to any one of claims 1 to 4, wherein the intermediate shaft is coaxially fixed to the first ring gear and the second ring gear.
A power drive system according to any one of claims 1-9, wherein the first planet carrier and the second planet carrier are configured as power take-offs of the power drive system.
The power drive system according to claim 10, wherein the first planet carrier is coaxially disposed with a first planet carrier output gear, and the second planet carrier is coaxially disposed with a second planet carrier Output gear.
The power drive system according to any one of claims 1 to 11, wherein the first sun gear and the second sun gear have the same number of teeth, the first sun gear and the first tooth a first planetary gear is disposed between the rings, and a second planetary gear is disposed between the second sun gear and the second ring gear, and the number of teeth of the first planetary gear and the second planetary gear is the same. The first ring gear has the same number of teeth as the second ring gear.
The power drive system according to any one of claims 1 to 12, wherein the first sun gear, the first planet carrier and the first ring gear are housed in the first motor generator Internally, the second sun gear, the second planet carrier, and the second ring gear are housed inside the second motor generator.
A power drive system according to any one of claims 1 to 13, wherein

The power coupling device is configured to drive a first pair of wheels of the vehicle;

The power drive system further includes:

a fourth motor generator and a fifth motor generator;

a first power output shaft and a second power output shaft, and a plurality of sets of first planetary gear mechanisms and a plurality of sets of second planetary gear mechanisms, the plurality of sets of first planetary gear mechanisms being disposed in series with the fourth motor generator and the Between the first power output shafts and capable of outputting power from the fourth motor generator to the first power output shaft through a shifting action, the plurality of sets of second planetary gear mechanisms being disposed in series at the fifth Between the motor generator and the second power output shaft, and capable of outputting power from the fifth motor generator to the second power output shaft through a shifting action, wherein the plurality of sets of first planetary gear mechanisms Sharing the same first common ring gear, the plurality of sets of second planetary gear mechanisms sharing the same second common ring gear, the first power output shaft being adapted to be connected to one of the second pair of wheels of the vehicle, The second power take-off shaft is adapted to be coupled to the other of the second pair of wheels, the first pair of wheels being a pair of a pair of front wheels and a pair of rear wheels, the second pair of wheels being a pair of front wheels Another pair of rear wheels;

a second brake device and a third brake device, the second brake device being configured to brake the first common ring gear, the third brake device being configured to brake the second brake device Shared ring gear;

A power engagement device configured to engage the first power take off shaft and the second power take off shaft.
A power drive system according to any one of claims 1 to 13, wherein

The power coupling device is configured to drive 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 ring gear;

a fourth motor generator and a fifth motor generator, wherein the fourth motor generator is coupled to the third sun gear, and the fifth motor generator is coupled to the fourth sun gear;

a first power output shaft and a second power output shaft, the first power output shaft being disposed between the third planet carrier and one of a second pair of wheels of the vehicle, the second power output shaft being disposed at Between the fourth planet carrier and the other of the second pair of wheels, the first pair of wheels is a pair of a pair of front wheels and a pair of rear wheels, and the second pair of wheels is a pair Another pair of the front wheel and the pair of rear wheels;

a second brake device and a third brake device, the second brake device being configured to brake the third ring gear, the third brake device being configured to brake the fourth tooth Circle;

A power engagement device configured to engage the first power take off shaft and the second power take off shaft.
A power drive system according to any one of claims 1 to 13, wherein

The power coupling device is configured to drive 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 ring gear, wherein the third planet carrier and the fourth planet carrier are configured as a power output end to drive a second pair of wheels, the first pair of wheels being a pair of front wheels and a pair a pair of the rear wheels, the second pair of wheels being the other pair of the pair of front wheels and the pair of rear wheels;

a fourth motor generator and a fifth motor generator, wherein the fourth motor generator is coupled to the third sun gear, and the fifth motor generator is coupled to the fourth sun gear;

An intermediate transmission assembly, the intermediate transmission assembly being disposed to be coupled to the third ring gear and the fourth ring gear, respectively;

A second brake device, the second brake device being arranged to brake the intermediate transmission assembly.
The power drive system of claim 16 further comprising a third brake device configured to brake the third planet carrier or the fourth planet carrier.
A vehicle characterized by comprising the power drive system according to any one of claims 1-17.