CN106555849B

CN106555849B - Power driving system and vehicle with same

Info

Publication number: CN106555849B
Application number: CN201510623748.1A
Authority: CN
Inventors: 凌和平; 翟震; 郑峰; 徐友彬; 罗永孟
Original assignee: BYD Co Ltd
Current assignee: BYD Co Ltd
Priority date: 2015-09-25
Filing date: 2015-09-25
Publication date: 2019-12-10
Anticipated expiration: 2035-09-25
Also published as: CN106555849A

Abstract

The invention discloses a power driving system and a vehicle. The power drive system includes: a differential, the differential comprising: the first planet gear and the second planet gear are respectively arranged on the first planet carrier and the second planet carrier, the first planet gear and the second planet gear are respectively meshed with the first gear and the second gear, and the second planet gear is also meshed with the first planet gear; a power output shaft arranged to be linked with the power input end of the differential; a plurality of input shafts, each input shaft being arranged to be linked with the power output shaft; and a first motor generator which is linked with one of the input shafts. The differential mechanism of the power driving system according to the embodiment of the invention realizes the differential function by utilizing the planetary differential principle, and has compact and simple structure.

Description

Power driving system and vehicle with same

Technical Field

The invention relates to a power driving system for a vehicle and the vehicle with the power driving system.

Background

In one of the differential technologies known to the inventor, the differential includes a driven gear of a main reducer (main reducer driven gear), a planetary gear, a central wheel, etc., the planetary gear is mounted on an auxiliary plate of the driven gear through a square shaft and a shaft sleeve and is meshed with the central wheel, the rotating and moving functions of the planetary gear are realized by a rotating pair and a plane moving pair, and the central wheel is connected with a left half shaft and a right half shaft through an angular positioning pin and a cylindrical pair or a spline, so as to achieve the purpose of outputting torque. The differential eliminates the original components such as left and right shells, planetary gear shafts and the like of the differential, and directly installs the planetary gear on the auxiliary plate of the driven gear of the main reducer by using a square shaft and a shaft sleeve, thereby effectively reducing the number of parts of the differential, simplifying the structure and lightening the weight.

However, the differential mechanism utilizes a symmetrical bevel gear structure to realize inter-wheel differential, is only a partial innovation of the traditional symmetrical bevel gear differential mechanism, and cannot really solve the defects of overlarge axial size, large mass of a shell and a bevel gear and relative reliability deviation of the differential mechanism.

Disclosure of Invention

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

Therefore, the differential mechanism of the power driving system realizes the differential function by utilizing the planetary differential principle, and has compact and simple structure.

The invention also provides a vehicle with the power transmission system.

a power drive system according to an embodiment of the present invention includes: a differential, said differential comprising: the planet carrier comprises a first planet carrier, a first planet wheel and a first gear ring, wherein the first planet wheel is arranged on the first planet carrier, and is meshed with the first gear ring; the second planet gear is arranged on the second planet carrier, and is meshed with the second gear ring and the first planet gear; the first gear ring and the second gear ring form two power output ends of the differential, and the first planet carrier and the second planet carrier form a power input end of the differential; a power output shaft configured to be coupled to the power input of the differential; a plurality of input shafts, each of the input shafts being provided in linkage with the power output shaft; a first motor generator operatively coupled to one of the plurality of input shafts.

The differential mechanism of the power driving system according to the embodiment of the invention realizes the differential function by utilizing the planetary differential principle, and has compact and simple structure.

In addition, the power driving system according to the embodiment of the invention may also have the following additional technical features:

in some embodiments, the power take-off shaft is fixed coaxially with the first and second planet carriers.

in some embodiments, the power drive system further comprises: the first output part is linked with the first gear ring, and the second output part is linked with the second gear ring.

In some embodiments, the first output is a left side gear and the second output is a right side gear; and

The first gear ring is provided with first external teeth, the second gear ring is provided with second external teeth, the first external teeth are meshed with the left half axle gear, and the second external teeth are meshed with the right half axle gear.

In some embodiments, the power drive system further comprises: an engine configured to selectively engage at least one of the plurality of input shafts.

In some embodiments, the input shaft and the power output shaft are in transmission through a gear pair.

in some embodiments, a plurality of fixed driven gears are fixedly arranged on the power output shaft, a fixed driving gear is fixedly arranged on each input shaft, and the fixed driven gears are meshed with the corresponding fixed driving gears.

In some embodiments, the plurality of input shafts comprises:

First input shaft and second input shaft, the second input shaft is established the axle sleeve is established on the first input shaft, fixed driving gear includes: fix the first fixed driving gear on first input shaft and fix the fixed driving gear of second on the second input shaft, fixed driven gear includes: the first fixed driven gear is meshed with the first fixed driving gear, and the second fixed driven gear is meshed with the second fixed driving gear.

in some embodiments, the power drive system further comprises:

An engine; and

A dual clutch, the dual clutch comprising: the engine includes a first engagement portion, a second engagement portion, and a third engagement portion configured to selectively engage at least one of the first engagement portion and the second engagement portion, the engine being coupled to the third engagement portion, the first input shaft being coupled to the first engagement portion, the second input shaft being coupled to the second engagement portion.

In some embodiments, the first motor generator is linked to the first or second fixed driving gear through a gear structure.

In some embodiments, the first planet gear partially overlaps the second planet gear in an axial direction.

In some embodiments, the first planet comprises: a first tooth and a second tooth, the second planet comprising: the first tooth part is meshed with the first gear ring, the second tooth part and the third tooth part are correspondingly overlapped and meshed in the axial direction, and the fourth tooth part is meshed with the second gear ring.

In some embodiments, the first planet gear and the second planet gear are both cylindrical gears.

In some embodiments, each of the first ring gear and the second ring gear includes:

The main part flat board portion with set up the annular side wall portion of the periphery edge of main part flat board portion, be provided with a plurality of teeth on the internal face of annular side wall portion, main part flat board portion with inject the cavity between the annular side wall portion, the cavity of first ring gear with the cavity orientation of second ring gear is in order to constitute installation space each other, first planet carrier with first planet wheel and the second planet carrier with the second planet wheel is accomodate in the installation space.

In some embodiments, the first gear ring and the second gear ring are provided with a gap in the axial direction.

in some embodiments, each of the first planet gears is provided with a first planet gear shaft, two ends of the first planet gear shaft are respectively connected with the first planet carrier and the second planet carrier, each of the second planet gears is provided with a second planet gear shaft, and two ends of the second planet gear shaft are respectively connected with the first planet carrier and the second planet carrier.

In some embodiments, the revolution axis of the first planet wheel coincides with the revolution axis of the second planet wheel, and the revolution radius of the first planet wheel is the same as the revolution radius of the second planet wheel.

In some embodiments, the power drive system further comprises: a first output portion and a second output portion, the first output portion being in linkage with the first gear ring, the second output portion being in linkage with the second gear ring; a second motor generator that is linked with the first output unit, and a third motor generator that is linked with the second output unit.

In some embodiments, the transmission includes a first input shaft, a second input shaft, and a third input shaft, the third input shaft is sleeved on the second input shaft, the second input shaft is sleeved on the first input shaft, and the engine is connected with the first input shaft, the second input shaft, and the third input shaft through three clutches.

in some embodiments, the first gear ring is in linkage with a left front wheel and the second gear ring is in linkage with a right front wheel;

The power drive system further includes:

a fourth motor generator linked with the left rear wheel and a fifth motor generator linked with the right rear wheel; and

An anti-skid synchronizer configured to selectively synchronize the left and right rear wheels such that the left and right rear wheels rotate in synchronization.

the vehicle according to the embodiment of the invention comprises the power driving system of the embodiment.

drawings

FIG. 1 is an exploded view of a differential according to an embodiment of the present invention;

FIG. 2 is a front view of a differential according to an embodiment of the present invention;

FIG. 3 is a schematic plan view of a differential according to an embodiment of the present invention;

FIG. 4 is a partial perspective view of the differential with the first ring gear and the first carrier removed, according to an embodiment of the present invention;

FIG. 5 is a partial front view of a differential according to an embodiment of the present invention, showing primarily the first planet carrier, first planet gears, and second planet carrier and second planet gears, etc.;

FIG. 6 is a schematic of the engagement of a first planet and a second planet;

FIG. 7 is a diagrammatic view of the engagement of a first planet and a second planet;

FIG. 8 is a perspective view of the first gear ring or the second gear ring according to an embodiment of the present invention;

FIG. 9 is a perspective view of the first ring gear or the second ring gear according to another embodiment of the present invention;

FIG. 10 is a schematic illustration of a power drive system according to one embodiment of the present invention;

FIG. 11 is a schematic illustration of a power drive system according to another embodiment of the present invention;

FIG. 12 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

FIG. 13 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

FIG. 14 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

FIG. 15 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

FIG. 16 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

FIG. 17 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

FIG. 18 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

FIG. 19 is a schematic illustration of a power drive system according to yet another embodiment of the present invention;

fig. 20 is a schematic diagram of a vehicle according to an embodiment of the invention.

Detailed Description

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

In the description of the present invention, it is to be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", and the like, indicate orientations and positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus, should not be considered as limiting the present invention.

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

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

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

A power drive system 1000 according to an embodiment of the present invention, which power drive system 1000 is applicable to a vehicle, will be described in detail below with reference to the accompanying drawings.

As shown in fig. 10 to 15, a power drive system 1000 according to some embodiments of the present invention mainly includes a differential 100, a transmission 104, and a first motor generator 401, the transmission 104 being connected between the differential 100 and the first motor generator 401.

The specific structure of differential 100 will first be described in detail with respect to the illustrated embodiment, and other configurations of power drive system 1000 will be described after a detailed description of the construction of differential 100.

The differential 100 according to the embodiment of the present invention will be described in detail with reference to fig. 1 to 9, wherein the differential 100 can be used for an inter-wheel differential or an inter-axle differential, for example, the inter-wheel differential, and the differential 100 can enable left and right driving wheels to roll at different angular velocities when the vehicle is running in a curve or on an uneven road surface, so as to ensure that the driving wheels on both sides make a pure rolling motion with the ground.

As shown in fig. 1, a differential 100 according to some embodiments of the present invention may include a first carrier 11, a first planet gear 12, and a first ring gear 13, and a second carrier 21, a second planet gear 22, and a second ring gear 23.

In conjunction with the embodiments of fig. 1 and 5, each of the first carrier 11 and the second carrier 21 may be configured as a circular plate-like structure, which may reduce the axial dimension of the differential 100 to some extent. In some embodiments, the first planet carrier 11 and the second planet carrier 21 may be a split structure, and since a single small component is relatively easy to form, the separate machining of the first planet carrier 11 and the second planet carrier 21 may simplify the manufacturing process and improve the machining precision.

As shown in fig. 1, 3, 5 and in conjunction with fig. 6-7, the first planet gears 12 are arranged on the first planet carrier 11, for example, each first planet gear 12 is provided with a first planet gear shaft 14, both ends of the first planet gear shaft 14 are rotatably supported on the first planet carrier 11 and the second planet carrier 21, respectively, for example, both ends of the first planet gear shaft 14 can be rotatably supported in shaft holes corresponding to each other on the first planet carrier 11 and the second planet carrier 21 through bearings, and the first planet gears 12 can be fixed on the corresponding first planet gear shafts 14. Of course, both ends of the first planet carrier shaft 14 and the first planet carrier 11 and the second planet carrier 12 may also be fixedly connected, for example, both ends of the first planet carrier shaft 14 are respectively welded and fixed with the corresponding shaft holes of the first planet carrier 11 and the second planet carrier 12, at this time, the first planet gears 12 are rotatably sleeved on the corresponding first planet carrier shaft 14, for example, the first planet gears 12 can be rotatably sleeved on the first planet carrier shaft 14 through bearings. Thus, the first planet carrier 11 and the second planet carrier 21 can be connected through the first planet shaft 14, so that the first planet carrier 11 and the second planet carrier 21 keep moving at the same speed and in the same direction (namely, the first planet carrier 11 and the second planet carrier 21 are linked). Furthermore, with this connection, the first planet carrier 11 and the second planet carrier 21 can support/fix the first planet axle 14 well, preventing the first planet axle 14 from being disconnected from the single planet carrier, which may cause the differential 100 to fail.

referring to fig. 3, the first planetary gears 12 are engaged with the first ring gear 13, and may be embodied in an inner-meshing manner, that is, the first planetary gears 12 are located inside the first ring gear 13 and are engaged with teeth on the first ring gear 13. The first planetary gears 12 are preferably plural and equally spaced in the circumferential direction inside the first ring gear 13, for example, as a preferred embodiment, the number of the first planetary gears 12 may be three, and any two adjacent first planetary gears 12 are spaced apart by an angle of 120 °.

Similarly, as shown in fig. 1, 3, 5 and in conjunction with fig. 6-7, the second planet gears 22 are arranged on the second planet carrier 21, for example, each second planet gear 22 is provided with one second planet gear shaft 24, for example, both ends of the second planet gear shaft 24 can be rotatably supported in the shaft holes of the first planet carrier 11 and the second planet carrier 21 corresponding to each other through bearings, and the second planet gears 22 can be fixed on the corresponding second planet gear shafts 24. Of course, both ends of the second planetary gear shaft 24 and the first and second planetary gear carriers 11 and 12 may also be fixedly connected, for example, both ends of the second planetary gear shaft 24 are respectively welded and fixed with the corresponding shaft holes of the first and second planetary gear carriers 11 and 12, at this time, the second planetary gear 22 is rotatably sleeved on the corresponding second planetary gear shaft 24, for example, the second planetary gear 22 may be rotatably sleeved on the second planetary gear shaft 24 through a bearing. Therefore, the purpose of connecting the first planet carrier 11 and the second planet carrier 21 can be achieved through the second planet shaft 24, so that the first planet carrier 11 and the second planet carrier 21 keep moving at the same speed and in the same direction. Moreover, by adopting the connection mode, the first planet carrier 11 and the second planet carrier 21 can well support/fix the second planet wheel shaft 24, and the second planet wheel shaft 24 is prevented from being disconnected with a single planet carrier, so that the differential 100 is prevented from being failed.

Furthermore, in other embodiments of the present invention, in order to keep the first planet carrier 11 and the second planet carrier 21 capable of moving at the same speed and in the same direction, the first planet carrier 11 and the second planet carrier 21 may be directly and fixedly connected through an intermediate component, that is, the same speed and the same direction of movement of the first planet carrier 11 and the second planet carrier 21 may be realized through the first planet shaft 14 and the second planet shaft 24 in the above embodiments, while the embodiment may realize the same speed and the same direction of movement of the first planet carrier 11 and the second planet carrier 21 directly through the provision of the intermediate component, for example, the intermediate component may be located between the first planet carrier 11 and the second planet carrier 21 and welded and fixed with the first planet carrier 11 and the second planet carrier 21, respectively.

Referring to fig. 3, the second planetary gear 22 is meshed with the second ring gear 23, and may be in an inner meshing manner, that is, the second planetary gear 22 is located inside the second ring gear 23 and meshed with teeth on the second ring gear 23. The second planetary gears 22 are preferably plural and equally spaced in the circumferential direction inside the second ring gear 23, for example, as a preferred embodiment, the number of the second planetary gears 22 may be three, and any two adjacent second planetary gears 22 are spaced by an angle of 120 °.

it should be noted that fig. 3 is a schematic plan view of a differential 100 according to an embodiment of the present invention, in which the meshing relationship between the first planetary gear 12 and the second planetary gear 22 and the meshing relationship between the first planetary gear 12 and the first ring gear 13 and between the second planetary gear 22 and the second ring gear 23 are schematically shown, and since fig. 3 is a plan view and the three meshing relationships are shown at the same time, the relative positional relationship among the components is only schematic and does not show or imply the actual spatial arrangement positions of the components.

in the embodiment where the first planetary gear 12 and the second planetary gear 22 are both plural, it is preferable that the plural first planetary gears 12 and the plural second planetary gears 22 are respectively engaged correspondingly. For example, as shown in fig. 1 and 4, if the first planet gears 12 and the second planet gears 22 are three, the first planet gear 12 can be meshed with the corresponding first second planet gear 22, the second first planet gear 12 can be meshed with the corresponding second planet gear 22, and the third first planet gear 12 can be meshed with the corresponding third second planet gear 22, so that there are multiple sets of first planet gears 12 and second planet gears 22 meshed with each other, and when the differential 100 transmits power, the power can be transmitted between the multiple sets of first planet gears 12 and second planet gears 22 meshed with each other more stably and reliably.

In addition, in another embodiment in which the first planetary gear 12 and the second planetary gear 22 are both plural, the plural first planetary gears 12 and the plural second planetary gears 22 are alternately arranged in the circumferential direction, and any adjacent first planetary gear 12 and second planetary gear 22 mesh. That is, in this embodiment, the plurality of first planetary gears 12 and the plurality of second planetary gears 22 are alternately arranged in the circumferential direction and form a ring shape, each of the first planetary gears 12 meshes with its adjacent two second planetary gears 22, and similarly, each of the second planetary gears 22 meshes with its adjacent two first planetary gears 12.

In this regard, referring to the embodiment of fig. 3, the revolution axis O of the first planet wheel 12 coincides with the revolution axis O of the second planet wheel 22, and the revolution radii of the first planet wheel 12 and the second planet wheel 22 (i.e., the distances of the central axes of the planet wheels from the revolution axis O) are the same.

In particular, as shown in fig. 1-2, 4-7, the first planet gears 12 are in meshing engagement with the second planet gears 22. In other words, for the first planet wheel 12, it meshes not only with the first ring gear 13, but also with the second planet wheel 22, and for the second planet wheel 22, it meshes not only with the second ring gear 23, but also with the first planet wheel 12.

As shown in fig. 3, the first ring gear 13 and the second ring gear 23 may form two power output ends of the differential 100, and the first planet carrier 11 and the second planet carrier 21 may form power input ends of the differential 100 (for example, in this case, the first planet carrier 11 and the second planet carrier 21 may be rigidly connected together), so that power output by an external power source may be input from the first planet carrier 11 and the second planet carrier 21, and may be output from the first ring gear 13 and the second ring gear 23 respectively after the differential action of the differential 100. At this time, as an alternative embodiment, the first planet carrier 11 and the second planet carrier 21 may be connected to a power source such as an engine, a motor, etc., and the first ring gear 13 and the second ring gear 23 may be connected to the corresponding half shafts, which are in turn connected to the corresponding wheels, through a gear transmission structure, but is not limited thereto.

the operation principle of the differential 100 will be briefly described below by taking an example in which the differential 100 is applied to an inter-wheel differential, the first gear ring 13 and the second gear ring 23 constitute a power output end of the differential 100, and the first carrier 11 and the second carrier 21 constitute a power input end of the differential 100, where at this time, the first gear ring 13 may be connected to a left half shaft through external teeth, the left half shaft may be connected to a left wheel, the second gear ring 23 may be connected to a right half shaft through external teeth, the right half shaft may be connected to a right wheel, and power output by a power source such as an engine and/or a motor may be output to the first carrier 11 and the second carrier 21 through a speed reduction effect of a main speed reducer. If the vehicle runs on a flat road surface and does not turn, the left wheel and the right wheel theoretically rotate at the same speed, the differential mechanism 100 does not play a role in differential speed at the moment, the first planet carrier 11 and the second planet carrier 21 rotate at the same speed and in the same direction, the first gear ring 13 and the second gear ring 23 rotate at the same speed and in the same direction, and the first planet wheel 12 and the second planet wheel 22 only revolve and do not rotate. If the vehicle runs on an uneven road or turns, the left wheel and the right wheel theoretically have different rotating speeds, the rotating speeds of the first gear ring 13 and the second gear ring 23 are also different, namely, a rotating speed difference exists, at the moment, the first planet wheel 12 and the second planet wheel 22 rotate while revolving, the rotation of the first planet wheel 12 and the second planet wheel 22 can accelerate one of the first gear ring 13 and the second gear ring 23 and decelerate the other one of the first gear ring and the second gear ring 23, and the rotating speed difference between the accelerated gear ring and the decelerated gear ring is the rotating speed difference between the left wheel and the right wheel, so that the differential action is realized.

In summary, the differential 100 according to the embodiment of the present invention utilizes the planetary differential principle, and has higher space utilization rate, smaller axial dimension, and more advantages in terms of production and assembly in terms of structure and connection form. Such structural style not only can avoid the axial and radial size defects of the bevel gear, but also can better utilize the hollow space inside the driving and driven gear, thereby realizing better space utilization rate, greatly facilitating the whole vehicle arrangement of the differential mechanism 100 assembly and the limitation of the weight, and simultaneously having higher reliability and better transmission efficiency, being beneficial to improving the reliability of a power transmission chain and the power output fluency during the bending, and having higher practicability compared with the symmetrical bevel gear differential mechanism.

the meshing relationship of the first planetary gear 12 and the second planetary gear 22 will be described in detail below with reference to specific embodiments.

Referring to fig. 3, 5-7, the first planet gear 12 and the second planet gear 22 partially overlap in the axial direction (left-right direction in fig. 7), that is, the first planet gear 12 and the second planet gear 22 only partially overlap, and the other parts are offset, and the overlapped parts of the first planet gear 12 and the second planet gear 22 may mesh with each other, and the offset parts may mesh with the respective ring gears.

Specifically, as shown in fig. 6 and 7, the first planet wheel 12 may include a first tooth portion 151 and a second tooth portion 152, and a dashed line K2 in fig. 7 is used as a boundary line, the second planet wheel 22 may include a third tooth portion 153 and a fourth tooth portion 154, and a dashed line K1 in fig. 7 is used as a boundary line, the second tooth portion 152 and the third tooth portion 153 form an overlapping portion, that is, the second tooth portion 152 and the third tooth portion 153 are axially overlapped and meshed with each other, the first tooth portion 151 and the fourth tooth portion 154 are axially offset and meshed with the respective corresponding ring gears, that is, the first tooth portion 151 is meshed with the first ring gear 13, and the fourth tooth portion 154 is meshed with the second ring gear 23.

Therefore, the axial size of the differential 100 is more compact, and the volume of the differential 100 is smaller, which is beneficial to the installation and arrangement of the differential 100.

The power input and power output of differential 100 are described in detail below in connection with specific embodiments.

As shown in fig. 3, the differential 100 further includes differential input shafts 31, 32 and differential output shafts 41, 42, the differential input shafts 31, 32 are connected to the first carrier 11 and the second carrier 21, respectively, and as in the example of fig. 3, one differential input shaft 31 is connected to the left side of the first carrier 11, and the other differential input shaft 32 is connected to the right side of the second carrier 21. The differential output shafts 41, 42 are connected to the first ring gear 13 and the second ring gear 23, respectively, and as in the example of fig. 3, one differential output shaft 41 is connected to the left side of the first ring gear 13, and the other differential output shaft 42 is connected to the right side of the second ring gear 23. The differential input shafts 31, 32, the differential output shafts 41, 42, the first ring gear 13 and the second ring gear 23 may be arranged coaxially.

Further, as shown in fig. 3, the differential input shaft includes: a first differential input shaft 31 and a second differential input shaft 32, the first differential input shaft 31 being connected to the first planet carrier 11, the second differential input shaft 32 being connected to the second planet carrier 21, the differential output shaft may comprise: first differential output shaft 41 and second differential output shaft 42, first differential output shaft 41 links to each other with first ring gear 13, second differential output shaft 42 links to each other with second ring gear 23, first differential input shaft 31 and second differential input shaft 32 and first differential output shaft 41 and second differential output shaft 42 all can be the hollow shaft structure, wherein as preferred embodiment, first differential output shaft 41 overlaps coaxially on first differential input shaft 31, and second differential output shaft 42 overlaps coaxially on second differential input shaft 32, and differential 100 is more compact in structure, the volume is littleer from this.

however, the differential input shaft and the differential output shaft described above are only one alternative embodiment. In the embodiment of the power drive system of fig. 10-19, however, the differential 100 outputs power to the outside through the outer teeth of the ring gear.

According to some embodiments of the invention, the number of teeth of the first ring gear 13 is equal to the number of teeth of the second ring gear 23, and the number of teeth of the first planet gear 12 is equal to the number of teeth of the second planet gear 22.

According to some embodiments of the present invention, the first planet gears 12 and the second planet gears 22 are cylindrical gears, and the differential 100 using cylindrical gears is more compact than a conventional symmetrical bevel gear differential, and in particular, has a higher space utilization rate in structure and connection form, a smaller axial size, and is more advantageous in production and assembly.

The structure of the first ring gear 13 and the second ring gear 23 will be described in detail below with reference to specific embodiments.

In some embodiments of the present invention, the first gear ring 13 and the second gear ring 23 are of a symmetrical structure, in other words, the first gear ring 13 and the second gear ring 23 are symmetrically arranged, which can increase the versatility of the gear rings and reduce the cost.

specifically, as shown in fig. 1 in conjunction with fig. 3, each of the first ring gear 13 and the second ring gear 23 includes: the main body flat plate portion 161 and the annular side wall portion 162 provided at the outer peripheral edge of the main body flat plate portion 161 may be integrally molded components. The annular side wall portion 162 is provided with a plurality of gear teeth on an inner wall surface thereof, cavities a1, a2 (see fig. 3) are defined between the main body flat plate portion 161 and the annular side wall portion 162, that is, a cavity a1 is defined between the main body flat plate portion 161 of the first ring gear 13 and the annular side wall portion 162, a cavity a2 is defined between the main body flat plate portion 161 of the second ring gear 23 and the annular side wall portion 162, and the cavity a1 in the first ring gear 13 and the cavity a2 in the second ring gear 23 face each other to form a mounting space a (see fig. 3), in which the first carrier 11 and the first planet gears 12 and the second carrier 21 and the second planet gears 22 are housed, so that the differential 100 is relatively more compact, occupies a smaller volume, and is easier to arrange, while the first ring gear 13 and the second ring gear 23 function as an outer casing, capable of protecting the planet carriers and planet gears housed therein, the service life is prolonged. In addition, the installation space a defined by the first gear ring 13 and the second gear ring 23 is relatively closed, and external impurities are not easy to enter the installation space a to influence moving parts, so that the stable operation of the differential 100 is ensured.

As shown in fig. 2, the first ring gear 13 and the second ring gear 23 are provided with a gap D in the axial direction, that is, the first ring gear 13 and the second ring gear 23 are spaced apart from each other in the axial direction and do not closely adhere to each other. For those skilled in the art, since the width of the meshing portion of the first planetary gear 12 and the second planetary gear 22 determines the size of the gap D, that is, the width of the meshing portion of the first planetary gear 12 and the second planetary gear 22 is equal to the minimum value of the gap D, the size of the gap D can be indirectly controlled by controlling the width of the meshing portion of the first planetary gear 12 and the second planetary gear 22, and for those skilled in the art, the width of the meshing portion of the first planetary gear 12 and the second planetary gear 22 can be set to be relatively narrow on the premise of ensuring stable power transmission of the first planetary gear 12 and the second planetary gear 22 and the service life of the first planetary gear 12 and the second planetary gear 22, so that the gap D can be effectively reduced, and the differential 100 has a smaller axial size, is more compact, and is easy to arrange.

Note that the gap D in fig. 3 described above and in conjunction with fig. 1 to 2 refers to a distance between the annular side wall portion 162 of the first ring gear 13 and the annular side wall portion 162 of the second ring gear 23. For example, referring to the embodiment of fig. 1, 2, and 3, the first and second ring gears 13 and 23 each include a main body flat plate portion 161 and an annular side wall portion 162.

while in other embodiments of the present invention, as in the embodiment with reference to fig. 8 and 9, each of the first and second ring gears 13 and 23 further includes an annular flange portion 163, the annular flange portion 163 extending from an end surface of the annular side wall portion 162 in a direction away from the main plate portion 161, in the embodiment of fig. 8, an inner diameter of the annular flange portion 163 may be substantially equal to an outer diameter of the annular side wall portion 162, so that the annular flange portion 163 protrudes outward in a radial direction with respect to the annular side wall portion 162 (i.e., an outer peripheral surface of the first ring gear 13 or the second ring gear 23). In the embodiment of fig. 9, the outer diameter of the annular flange portion 163 may be substantially equal to the outer diameter of the annular side wall portion 162, and the inner diameter of the annular flange portion 163 may be larger than the inner diameter of the annular side wall portion 162, i.e., the thickness of the annular flange portion 163 is thinner than the thickness of the annular side wall portion 162.

However, it should be noted that, in the ring gear structure of the embodiment shown in fig. 1, 2 and 3, the gap D between the two ring gears refers to the gap between the annular side wall portions 162 of the two ring gears. In the ring gear structure in the embodiment of fig. 8 and 9, the gap D between the two ring gears refers to the gap between the annular flange portions 163 of the two ring gears.

according to some embodiments of the present invention, since the first ring gear 13 and/or the second ring gear 23 may further include the annular flange portion 163, when such a ring gear structure is adopted, due to the presence of the annular flange portion 163, the above-mentioned gap D may be at least partially further reduced, and preferably, the gap D may be reduced to zero, compared to a ring gear without the annular flange portion 163, for example, the first ring gear 13 and the second ring gear 23 may adopt the ring gear structure shown in fig. 8 at the same time, and at this time, the end surfaces of the annular flange portion 163 of the first ring gear 13 and the annular flange portion 163 of the second ring gear 23 may be substantially attached together, so that the gap D is zero, so that the installation space a is more closed, and external foreign objects are more difficult to enter the installation space a to affect moving parts, thereby ensuring stable operation of the differential 100. It should be understood, of course, that the description herein is merely illustrative and should not be construed as a limitation on the scope of the present invention, and that after reading the above description, those skilled in the art can flexibly select the combination of the types of ring gears, for example, to ensure that at least one of the ring gears has the annular flange portion 163, after understanding the technical idea that the gap D can be further reduced or even reduced to zero by providing the annular flange portion 163, so that the gap D can be further reduced or even reduced to zero, thereby making the installation space a more airtight.

Further, as an alternative embodiment, the radial dimensions of the first ring gear 13 and the second ring gear 23 are the same, and each of the first ring gear 13 and the second ring gear 23 may be an integrally molded component.

having described the differential 100 in detail, the remaining structure of the power drive system 1000 will now be described.

Referring to fig. 10-15, the transmission 104 may include a plurality of input shafts 101, 102 and a power output shaft 103. In some embodiments, the power take-off shaft 103 of the transmission 104 may be one, but is not limited thereto. The power take-off shaft 103 is arranged to be coupled to the power input of the differential 100, i.e. the power take-off shaft 103 is arranged to be coupled to the first planet carrier 11 and the second planet carrier 21.

Each input shaft is provided in conjunction with the power output shaft 103, in other words, as shown in fig. 10 and 11, the power output shaft 103 follows the motion when any one of the input shafts rotates, or the input shafts follow the motion when the power output shaft 103 rotates.

As shown in fig. 10 and 11, the first motor generator 401 is provided in conjunction with one of the input shafts. As in the example of fig. 10, the first motor generator 401 is linked with the first input shaft 101. In the example of fig. 11, the first motor generator 401 is linked with the second input shaft 102.

For the transmission mode of the input shafts 101 and 102 and the power output shaft 103, a conventional gear pair can be adopted for transmission.

For example, the power output shaft 103 is fixedly provided with a plurality of fixed driven gears 107a, 107b, each of which is fixedly provided with a fixed driving gear (e.g., a first fixed driving gear 106 and a second fixed driving gear 105), and the fixed driven gears are engaged with the corresponding fixed driving gears.

as shown in the example of fig. 10 to 11, the fixed driven gear 107a is engaged with the fixed driving gear 105 to form one pair of gear pairs, and the fixed driven gear 107b is engaged with the fixed driving gear 106 to form another pair of gear pairs. It will be appreciated that the two pairs of gear pairs have different transmission speed ratios, and therefore the transmission 104 in this embodiment has two transmission gears with different speed ratios, so that the structure of the power drive system 1000 is relatively simple and compact, and the requirement of the vehicle for the transmission speed ratio in normal running can also be met.

As shown in fig. 10-15, the plurality of input shafts includes a first input shaft 101 and a second input shaft 102, the first input shaft 101 may be a solid shaft, the second input shaft 102 may be a hollow shaft, the second input shaft 102 is sleeved on the first input shaft 101, for example, the second input shaft 102 is coaxially sleeved on the first input shaft 101, the axial length of the first input shaft 101 is greater than that of the second input shaft 102, and one end, for example, the right end, of the first input shaft 101 may extend out from the inside of the second input shaft 102.

Each input shaft may be fixedly provided with only one fixed driving gear, that is, the fixed driving gear includes a first fixed driving gear 106 and a second fixed driving gear 105, the first fixed driving gear 106 is fixedly arranged on the first input shaft 101, and the second fixed driving gear 105 is fixedly arranged on the second input shaft 102. Correspondingly, the fixed driven gear includes a first fixed driven gear 107b and a second fixed driven gear 107a, the first fixed driven gear 107b is engaged with the first fixed driving gear 106, and the second fixed driven gear 107a is engaged with the second fixed driving gear 105.

Referring to fig. 10, 12-15, the first motor generator 401 is linked with the first input shaft 101, for example, the first motor generator 401 is linked with the first fixed driving gear 106 through a gear structure, specifically, the first motor generator 401 is driven with the first fixed driving gear 106 through a gear 402 and a gear 403, and the number of teeth of the gears is designed appropriately to obtain the required transmission speed ratio of the first motor generator 401.

In the example of fig. 11, the first motor generator 401 is linked with the second fixed driving gear 105 through a gear structure, and specifically, the first motor generator 401 may transmit power with the second fixed driving gear 105 through a gear 402, a gear 403, a gear 404, and a gear 405, wherein the gear 404 and the gear 405 may be fixed on the same shaft 406, and the transmission speed ratio required by the first motor generator 401 may be obtained by properly designing the number of teeth of the gears.

further, the power drive system 1000 may further include an engine 301, the engine 301 being configured to be selectively engageable with at least one of the plurality of input shafts, specifically, two input shafts, and a double clutch 204 being provided between the engine 301 and the two input shafts. The dual clutch 204 includes: a first engagement portion 201, a second engagement portion 202 and a third engagement portion 203, wherein the first engagement portion 201 and the second engagement portion 202 may be two driven discs of a dual clutch 204, the third engagement portion 203 may be a housing of the dual clutch 204, at least one of the two driven discs may selectively engage the housing, that is, at least one of the first engagement portion 201 and the second engagement portion 202 may selectively engage the third engagement portion 203. Of course, both driven discs may also be completely disconnected from the housing, i.e. both the first engagement portion 201 and the second engagement portion 202 are in a disconnected state from the third engagement portion 203.

Referring to fig. 10 to 15, the engine 301 is connected to the third engaging portion 203, the first input shaft 101 is connected to the first engaging portion 201, and the second input shaft 102 is connected to the second engaging portion 202. In this way, the power generated by the engine 301 can be selectively output to the first input shaft 101 and the second input shaft 102 through the dual clutch 204.

As a preferred embodiment of the present invention, the power output shaft 103 is coaxially fixed with the first and second planetary carriers 11 and 21, thereby making the connection portion of the transmission 104 and the differential 100 more compact, i.e., directly coaxially fixing the power output shaft 103 with the two planetary carriers, thereby enabling the volume of the power drive system 1000 to be reduced at least to some extent.

In a further embodiment, as shown in fig. 10-17, the power drive system 1000 further includes a first output 601 and a second output 602, the first output 601 being in communication with the first ring gear 13, and the second output 602 being in communication with the second ring gear 23. Further, the first output portion 601 is a left side gear, the second output portion 602 is a right side gear, and the first ring gear 13 is provided with first external teeth 603, the second ring gear 23 is provided with second external teeth 604, the first external teeth 603 are engaged with the left side gear 601, and the second external teeth 604 are engaged with the right side gear 602, so that the power passing through the differential 100 can be finally output to the left and right wheels through the left side gear 603 and the right side gear 604.

As shown in fig. 16 and 17, the second motor generator 501 is configured to be linked with the first output portion 601, and the third motor generator 502 is configured to be linked with the second output portion 602, for example, a gear 503 may be disposed on a motor shaft of the second motor generator 501, the gear 503 is engaged with the left side gear 601, and a gear 504 is disposed on a motor shaft of the third motor generator 502, and the gear 504 is engaged with the right side gear 602.

Referring to fig. 16 to 17, the second motor generator 501 and the third motor generator 502 are symmetrically distributed left and right with respect to the differential 100, so that the center of gravity of the power drive system 100 is located at the center position or closer to the center position.

referring to the embodiment of fig. 18-19, one of the main differences between the power drive system 1000 in this embodiment and the power drive system 1000 in the embodiment of fig. 10-17 is that: the number of input shafts. In some embodiments, the input shafts include a first input shaft 101, a second input shaft 102, and a third input shaft 1003, the third input shaft 1003 may be a hollow shaft and is sleeved on the second input shaft 102, the second input shaft 102 may also be a hollow shaft and is sleeved on the first input shaft 101, and the three input shafts may be coaxially arranged. The engine 301 is connected with the first input shaft 101, the second input shaft 102 and the third input shaft 1003 through a three-clutch 205, specifically, the three-clutch 205 has a first driven disk 206, a second driven disk 207, a third driven disk 208 and a housing 209, the housing 209 is selectively engageable with at least one of the first driven disk 206, the second driven disk 207 and the third driven disk 208, the first input shaft 101 is connected with the first driven disk 206, the second input shaft 102 is connected with the second driven disk 207, the third input shaft 1003 is connected with the third driven disk 208, and the engine 301 is connected with the housing 209. In the embodiment of fig. 18, the first driven disk 206, the second driven disk 207 and the third driven disk 208 are axially distributed, and in the embodiment of fig. 19, the first driven disk 206, the second driven disk 207 and the third driven disk 208 are radially distributed.

Exemplary operating conditions of the power drive system 1000 according to an embodiment of the present invention are briefly described below with reference to fig. 10.

For example, the first engaging portion 201 is engaged with the third engaging portion 203, the second engaging portion 202 is disengaged from the third engaging portion 203, and the power generated by the engine 301 is output to the differential 100 through the first input shaft 101 and the power output shaft 103, and the differential 100 distributes the power to the driving wheels on both sides.

For another example, the second engaging portion 202 is engaged with the third engaging portion 203, and the first engaging portion 201 is disengaged from the third engaging portion 203, so that the power generated by the engine 301 is output to the differential 100 through the second input shaft 102 and the power output shaft 103, and the differential 100 distributes the power to the driving wheels on both sides.

For example, the double clutch 204 is completely disengaged, and the power generated by the first motor generator 401 is output to the differential 100 through the first input shaft 101 and the power output shaft 103, and the differential 100 distributes the power to the drive wheels on both sides.

for another example, the first engaging portion 201 is engaged with the third engaging portion 203, and the second engaging portion 202 is disengaged from the third engaging portion 203, so that a part of the power generated by the engine 301 is output to the first motor generator 401 through the first input shaft 101, the first motor generator 401 is driven to generate power as a motor, and another part of the power output by the engine 301 is output to the differential 100 through the power output shaft 103, and the power is distributed to the driving wheels on both sides by the differential 100.

The main difference between the embodiment of fig. 11 and the embodiment of fig. 10 is that the first motor generator 401 is linked with the second input shaft 102, while the embodiment of fig. 8 is that the first motor generator 401 is linked with the first input shaft 101, and the rest of the description is omitted.

For the embodiment of fig. 12-15, the difference is the addition of a rear drive differential lock as compared to the embodiment of fig. 10.

referring to fig. 12-14 in conjunction with fig. 1-9, the first ring gear 13 is linked with the left front wheel 910a, e.g., the first ring gear 13 is linked with the left front wheel 910a via the first external teeth 603 and the left side gear 601, the second ring gear 23 is linked with the right front wheel 910b, e.g., the second ring gear 23 is linked with the right front wheel 910b via the second external teeth 604 and the right side gear 602. The fourth motor generator 901 is linked with the left rear wheel 910c by a gear structure, for example, the fourth motor generator 901 is linked with the left rear wheel 910c by gears W1, W2, W3, W4, the gear W1 is coaxially connected with the fourth motor generator 901, the gear W1 is engaged with the gear W2, the gear W2 is coaxially connected with the gear W3, the gear W3 is engaged with the gear W4, the gear W4 is fixedly provided on the left half shaft 904, and the left rear wheel 910c is provided on the left half shaft 904. Similarly, the fifth motor generator 902 is linked with the right rear wheel 910d through a gear structure, for example, the fifth motor generator 902 is linked with the right rear wheel 910d through gears X1, X2, X3 and X4, the gear X1 is coaxially connected with the fifth motor generator 902, the gear X1 is engaged with the gear X2, the gear X2 is coaxially connected with the gear X3, the gear X3 is engaged with the gear X4, the gear X4 is fixedly disposed on the right half shaft 905, and the right rear wheel 910d is disposed on the right half shaft 905.

In the example of fig. 12, an anti-skid synchronizer 903 is provided for synchronizing the gear W4 with the gear X4, e.g., the anti-skid synchronizer 903 is provided on the gear W4 and is for engaging the gear X4. In the example of fig. 13, an anti-skid synchronizer 903 is provided for synchronizing the gear W1 with the gear X1, e.g., the anti-skid synchronizer 903 is provided on the gear W1 and is for engaging the gear X1. In the example of fig. 14, an anti-slip synchronizer 903 is provided for synchronizing the gear W2 with the gear X2, e.g., the anti-slip synchronizer 903 is provided on the gear W2 and for engaging the gear X2.

In the example of fig. 15, an anti-skid synchronizer 903 is provided for synchronizing a left half shaft 904 and a right half shaft 905, and the fourth motor generator 901 and the fifth motor generator 902 are each a wheel-side motor in this embodiment, as the anti-skid synchronizer 903 is provided on the left half shaft 904 and for engaging the right half shaft 905.

In summary, the anti-skid synchronizer 903 is configured to selectively synchronize the left rear wheel 910c and the right rear wheel 910d, in other words, when the anti-skid synchronizer 903 is in the engaged state, the left rear wheel 910c and the right rear wheel 910d will rotate synchronously, i.e. at the same speed and in the same direction, and at this time, the left rear wheel 910c and the right rear wheel 910d will not rotate at different speeds. When the anti-skid synchronizer 903 is in a disconnected state, the fourth motor generator 901 can drive the left rear wheel 910c alone, the fifth motor generator 902 can drive the right rear wheel 910d alone, and the two rear wheels are independent and do not interfere with each other, so that the function of differential rotation of the wheels is realized.

in addition, for the technical solutions and/or technical features described in the above embodiments, those skilled in the art can combine the technical solutions and/or technical features in the above embodiments without conflict or contradiction, and the combined technical solution may be a superposition of two or more technical solutions, a superposition of two or more technical features, or a superposition of two or more technical solutions and technical features, so that functional interaction and support of each technical solution and/or technical feature with each other can be achieved, and the combined solution has a more superior technical effect.

For example, a person skilled in the art may combine the solution of the first planet gear 12 partially overlapping the second planet gear 22 with the solution of the first planet carrier 11 and the second planet carrier 21 having the plate-like structure, which may effectively reduce the axial size of the differential 100, thereby making the differential 100 smaller in size.

for another example, a person skilled in the art may combine the scheme that the first planet wheel 12 and the second planet wheel 22 partially overlap with the scheme that the planet wheel and the planet carrier are accommodated in the installation space, so that not only the axial size of the differential 100 may be effectively reduced, but also the planet wheel and the planet carrier are hidden in the installation space and prevented from being exposed and damaged, thereby increasing the service life and reducing the maintenance cost.

For another example, a person skilled in the art may combine a scheme in which the revolution axis of the first planet wheel 12 coincides with the revolution axis of the second planet wheel 22 with a scheme in which the revolution radius of the first planet wheel 12 is the same as the revolution radius of the second planet wheel 22, so that the differential 100 has a more compact structure, a smaller occupied volume, and a more convenient arrangement.

It should be understood, of course, that the above descriptions of examples are only illustrative, and those skilled in the art can freely combine technical solutions and/or combinations of technical features without conflict, and the combined solutions have more advantageous technical effects.

In addition, it is understood that the combined technical solutions also fall into the protection scope of the present invention.

overall, the differential 100 according to the embodiment of the present invention can effectively save space and reduce weight, and particularly, such a planetary gear type differential 100 can reduce the weight by about 30% and the axial dimension by about 70% as compared with the conventional bevel gear type differential, not only can reduce the friction of the bearings, but also can realize the torque distribution of the left wheel and the right wheel, so that the load distribution of the differential mechanism 100 is more reasonable, the rigidity of the differential mechanism 100 is better, in addition, the transmission efficiency is also improved to a certain extent due to the adoption of the cylindrical gear, for example, the efficiency of the conventional bevel gear transmission with 6-grade precision and 7-grade precision is about 0.97-0.98, and the transmission efficiency of the cylindrical gears with 6-level precision and 7-level precision is about 0.98-0.99, and in addition, the cylindrical gears are adopted, so that the working noise of the differential mechanism 100 is reduced, the heat productivity is reduced, and the service life of the differential mechanism 100 is greatly prolonged. In short, the differential 100 according to the embodiment of the present invention has many advantages of light weight, small size, low cost, high transmission efficiency, low noise, low heat generation, long service life, and the like.

Meanwhile, since the differential 100 according to an embodiment of the present invention may omit a sun gear, the omission of the sun gear may have the following advantages:

From mechanical analysis, the differential is realized by eliminating the sun gear and utilizing the gear ring, because the number of teeth of the gear ring is more than that of the sun gear, and the pitch circle is larger (the pitch circle refers to a pair of circles tangent at the node when the gears are in meshing transmission), so that the load and bearing torque can be more evenly distributed, which is beneficial to prolonging the service life of the differential 100. Meanwhile, the differential mechanism 100 can be better lubricated and cooled due to the fact that the sun wheel is not arranged, namely, a cavity can be formed inside the planetary wheel due to the fact that the sun wheel is omitted, the gear ring and the planetary wheel are meshed in an inner meshing relation (the sun wheel and the planetary wheel are meshed outside), lubricating oil can be stored in the gear ring, and therefore cooling and lubricating effects can be greatly improved. In addition, since the sun gear is eliminated, the number of parts is reduced, the mass and cost of the differential 100 are reduced, and the differential 100 becomes more compact and lighter.

While the power driving system 1000 having the differential 100 according to the embodiment of the present invention has significant advantages in space and driving manner, taking the advantage of space as an example, the power driving system 1000 is particularly suitable for a new energy vehicle, since a power assembly of the new energy vehicle is generally disposed in an engine compartment, the power assembly not only has a transmission, an engine, but also has at least one electric machine, and since the engine compartment has limited space, the compact differential 100 according to the embodiment of the present invention can obtain advantages in space, and is more convenient to dispose. Also for example, taking the advantage of driving manner as an example, the axial space is better arranged due to the greatly reduced axial dimension of the differential 100 according to the embodiment of the present invention, and the differential 100 having two ring gears as power take-off can better achieve power connection with two electric machines (such as the above-described connection of the electric machines through the external teeth of the ring gears), which is difficult to achieve on the conventional conical differential.

Briefly describing a vehicle 10000 according to an embodiment of the present invention, as shown in fig. 20, the vehicle 10000 includes a power driving system 1000 in the above embodiment, and the power driving system 1000 may be used for forward driving or, of course, for backward driving, and the present invention is not limited thereto. It should be understood that other configurations of the vehicle 10000 according to the embodiment of the present invention, such as a brake system, a driving system, a steering system, etc., are known in the art and well known to those skilled in the art, and thus will not be described in detail herein.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above are not necessarily intended to refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, various embodiments or examples described in this specification can be combined and combined by those skilled in the art.

although embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention, and that variations, modifications, substitutions and alterations can be made to the above embodiments by those of ordinary skill in the art within the scope of the present invention.

Claims

1. A power drive system, comprising:

A differential, said differential comprising:

the planet carrier comprises a first planet carrier, a first planet wheel and a first gear ring, wherein the first planet wheel is arranged on the first planet carrier, and is meshed with the first gear ring;

the second planet gear is arranged on the second planet carrier, and is meshed with the second gear ring and the first planet gear;

The first gear ring and the second gear ring form two power output ends of the differential, and the first planet carrier and the second planet carrier form a power input end of the differential;

at least one of the first ring gear and the second ring gear includes: an annular side wall portion provided on an inner wall surface thereof with a plurality of teeth for meshing with the planetary gears, and an annular flange portion extending from an end surface of the annular side wall portion of one of the ring gears toward the other ring gear or provided on end surfaces of the annular side wall portions of the two ring gears, respectively, and extending opposite to each other, the annular flange portion having an inner diameter larger than that of the annular side wall portion;

a power output shaft configured to be coupled to the power input of the differential;

A plurality of input shafts, each of the input shafts being provided in linkage with the power output shaft;

A first motor generator operatively coupled to one of the plurality of input shafts.

2. The power-drive system of claim 1, wherein the first planet gear partially overlaps the second planet gear in the axial direction.

3. The power drive system of claim 2, wherein the first planet gear comprises: a first tooth and a second tooth, the second planet comprising: the first tooth part is meshed with the first gear ring, the second tooth part and the third tooth part are correspondingly overlapped and meshed in the axial direction, and the fourth tooth part is meshed with the second gear ring.

4. The power-drive system of claim 1, wherein the first and second planets are cylindrical gears.

5. The power drive system according to claim 1, characterized in that each of the first ring gear and the second ring gear includes:

6. The power drive system according to claim 1, characterized in that the first ring gear and the second ring gear are provided with a gap in the axial direction.

7. A power drive system according to claim 1, characterized in that each first planet wheel is provided with a first planet wheel axle, which at both ends are connected to the first planet carrier and the second planet carrier, respectively, and each second planet wheel is provided with a second planet wheel axle, which at both ends are connected to the first planet carrier and the second planet carrier, respectively.

8. The power-driven system of claim 1, wherein a revolution axis of the first planet is coincident with a revolution axis of the second planet, and a revolution radius of the first planet is the same as a revolution radius of the second planet;

The first and second planet carriers being spaced apart, the first and second planet gears being arranged in direct mesh between the first and second planet carriers such that the first and second planet carriers are located on opposite outer sides of the first and second planet gears, respectively;

The annular flange portion has an outer diameter substantially equal to an outer diameter of the annular side wall portion, or an inner diameter substantially equal to an outer diameter of the annular side wall portion such that the annular flange portion projects radially outward from the annular side wall portion.

9. A power drive system according to claim 1, wherein the power take-off shaft is fixed coaxially with the first and second planetary carriers.

10. The power drive system of claim 1, further comprising: the first output part is linked with the first gear ring, and the second output part is linked with the second gear ring.

11. A power drive system according to claim 10, wherein the first output section is a left side gear and the second output section is a right side gear; and

12. The power drive system of claim 1, further comprising: an engine configured to selectively engage at least one of the plurality of input shafts.

13. A power drive system according to claim 1, wherein the input shaft and the power output shaft are driven by a range gear pair.

14. A power drive system according to claim 13, wherein a plurality of fixed driven gears are fixedly disposed on the power output shaft, a fixed drive gear is fixedly disposed on each of the input shafts, and the fixed driven gears are engaged with the corresponding fixed drive gears.

15. the power drive system of claim 14, wherein the plurality of input shafts comprises:

16. The power drive system of claim 15, further comprising:

An engine; and

A dual clutch, the dual clutch comprising: a first engagement portion, a second engagement portion, and a third engagement portion configured to selectively engage at least one of the first engagement portion and the second engagement portion, the engine being coupled to the third engagement portion, the first input shaft being coupled to the first engagement portion, the second input shaft being coupled to the second engagement portion.

17. A power drive system according to claim 15 wherein the first motor generator is geared with the first or second fixed drive gear by a gear arrangement.

18. The power drive system of claim 1, further comprising:

a first output portion and a second output portion, the first output portion being in linkage with the first gear ring, the second output portion being in linkage with the second gear ring;

A second motor generator that is linked with the first output unit, and a third motor generator that is linked with the second output unit.

19. a power drive system according to claim 1, characterized in that the power drive system comprises: the transmission comprises a first input shaft, a second input shaft and a third input shaft, the third input shaft is sleeved on the second input shaft, the second input shaft is sleeved on the first input shaft, and the engine is connected with the first input shaft, the second input shaft and the third input shaft through three clutches.

20. The power-driven system according to claim 1, wherein the first ring gear is linked with a left front wheel, and the second ring gear is linked with a right front wheel;

The power drive system further includes:

21. A vehicle characterized by comprising a power drive system according to any one of claims 1-20.