CN117685338A - Power drive assembly and vehicle - Google Patents

Abstract

The invention provides a power driving assembly and a vehicle, and relates to the technical field of vehicles, wherein the power driving assembly comprises a driving device, a speed reducing device, a differential device, a planet carrier, a first half shaft, a second half shaft and a shell, wherein an inner gear ring is fixedly arranged on the inner side of the shell; the speed reducing device comprises a speed reducing planetary gear set which is respectively meshed with a first sun gear and an inner gear ring on an output shaft of the driving device, and each gear in the speed reducing planetary gear set is arranged on the planet carrier in a autorotation way; the differential device comprises a third planetary gear, a fourth planetary gear and a fifth planetary gear which are arranged on the planetary carrier in a autorotation manner, the third planetary gear is fixedly connected with the fifth planetary gear, the fourth planetary gear is respectively meshed with the third planetary gear and a second sun gear on the first half shaft, and the fifth planetary gear is meshed with a third sun gear on the second half shaft. The invention reduces the volume and weight of the power driving assembly and improves the freedom degree of the gears in the differential mechanism in parameter design.

Description

Power drive assembly and vehicle

Technical Field

The invention relates to the technical field of vehicles, in particular to a power driving assembly and a vehicle.

Background

The power driving assembly is an important part for providing power for the vehicle, wherein the power driving assembly of the vehicle mainly comprises a driving device, a speed changer and a differential mechanism, the driving device is used for providing power, the speed changer is used for adjusting the rotating speed and the torque output by the driving device, and the differential mechanism is used for enabling a left half shaft and a right half shaft of the vehicle to rotate at different rotating speeds so as to ensure that the vehicle turns stably.

At present, most of speed variators and differentials are of independent structures, and the speed variators and the differentials are connected through driving shafts, so that the whole power driving assembly is large in size and weight and large in occupied space. Moreover, the torque transmission chains of the differential mechanism to the left half shaft and the right half shaft of the vehicle are overlapped, so that a plurality of limitations exist in the design of parameters of gears in the differential mechanism.

Disclosure of Invention

The invention solves the problems of reducing the volume and the weight of a power driving assembly so as to realize the light weight of a vehicle and improve the freedom degree of a gear in a differential mechanism in parameter design.

In order to solve the above problems, the present invention provides a power driving assembly and a vehicle.

In a first aspect, the present invention provides a power drive assembly comprising a drive device, a reduction device, a differential device, a planet carrier, a first half shaft, a second half shaft, and a housing;

an inner gear ring is fixedly arranged on the inner side of the shell, a first sun gear is arranged on an output shaft of the driving device, a second sun gear is arranged on the first half shaft, and a third sun gear is arranged on the second half shaft;

the speed reducing device comprises a speed reducing planetary gear set, each gear in the speed reducing planetary gear set is arranged on the planet carrier in a autorotation mode, and the speed reducing planetary gear set is meshed with the first sun gear and the inner gear ring respectively;

the differential device comprises a third planet wheel, a fourth planet wheel and a fifth planet wheel, wherein the third planet wheel is fixedly connected with the fifth planet wheel, the third planet wheel, the fourth planet wheel and the fifth planet wheel are respectively and rotatably arranged on the planet carrier, the third planet wheel is meshed with the fourth planet wheel, the fourth planet wheel is meshed with the second sun wheel, and the fifth planet wheel is meshed with the third sun wheel.

Optionally, the speed reduction planetary gear set includes first planet wheel and second planet wheel, first planet wheel with second planet wheel fixed connection, just first planet wheel with second planet wheel is rotatable to be set up on the planet carrier, first planet wheel with first sun gear meshing, the second planet wheel with the ring gear meshing.

Optionally, the gear ratio between the second sun gear and the third sun gear is equal to the gear ratio between the third planet gear and the fifth planet gear.

Optionally, the number of the speed reducing devices is at least three, and every two adjacent speed reducing devices are spaced along the annular gear by a first preset angle.

Optionally, the number of the differential devices is at least three, and every two adjacent differential devices are spaced along the annular gear by a second preset angle.

Optionally, the first planet wheel, the second planet wheel, the third planet wheel, the fourth planet wheel and the fifth planet wheel are respectively sleeved on a planet wheel shaft of the planet carrier through bearings.

Optionally, one end of the first half shaft is opposite to one end of the second half shaft, and the first half shaft is coaxial with the second half shaft.

Optionally, the second sun gear is disposed on the first half shaft near one end of the second half shaft, and the third sun gear is disposed on the second half shaft near one end of the first half shaft.

Optionally, the output shaft of the driving device is sleeved on the first half shaft in a hollow mode and rotates independently.

In a second aspect, the present invention provides a vehicle comprising a power drive assembly as described in the first aspect.

The power driving assembly and the vehicle have the beneficial effects that: the output torque of the driving device is transmitted to the first sun wheel through the output shaft, the first sun wheel is meshed with the speed reduction planetary gear set in the speed reduction device, the speed reduction planetary gear set is internally meshed with the inner gear ring, and as each gear of the speed reduction planetary gear set is arranged on the planet carrier in a autorotation mode and the inner gear ring is fixed, the first sun wheel can drive the speed reduction planetary gear set to rotate, and the rotation of the speed reduction planetary gear set can be transmitted to the planet carrier through the inner gear ring, so that the speed reduction torque-up function of the speed reducer is realized.

And a third planetary gear, a fourth planetary gear and a fifth planetary gear in the differential device are arranged on the planetary frame in a autorotation manner, the third planetary gear drives the first half shaft through the fourth planetary gear, and the fifth planetary gear directly drives the second half shaft. When the vehicle is in straight line, the third planetary gear is fixedly connected with the fifth planetary gear, so that the rotation speeds of the third planetary gear and the fifth planetary gear are the same, and the rotation speeds of the first half shaft and the second half shaft are the same when the vehicle is in straight line. When the vehicle turns, the third planet wheel, the fourth planet wheel and the fifth planet wheel can not only revolve around the first half shaft and the second half shaft under the drive of the planet carrier, but also rotate relative to the planet carrier, and the first half shaft and the second half shaft can generate a rotating speed difference so as to realize the differential function of the differential mechanism.

Compared with the prior art that the speed changer and the differential mechanism are respectively of independent structures, the speed reducing mechanism integrates the speed reducing function and the differential mechanism into one set of power driving assembly, and a transmission shaft is not required to be additionally designed to connect the speed changer and the differential mechanism, so that the structure volume and the weight are effectively reduced, and the vehicle weight is favorably realized. In addition, the torque transmission path of the planet carrier to the first half shaft is: the torque transmission path from the planet carrier to the second half shaft is as follows: the planetary carrier, the fifth planetary gear, the third sun gear and the second half shaft have independent torque transmission paths, so that the limitation of the superposition of the torque transmission paths on the parameter design of the gears is avoided, and the freedom degree of the parameter design of the gears in the differential device is improved.

Drawings

FIG. 1 is a schematic view of a prior art differential gear from the left axle shaft of a vehicle;

FIG. 2 is a schematic diagram of a prior art differential gear looking from the right half axle of the vehicle;

FIG. 3 is a schematic diagram of a power drive assembly according to an embodiment of the present invention;

FIG. 4 is a ratio schematic of a power drive assembly according to an embodiment of the present invention;

FIG. 5 is a differential schematic diagram of a power drive assembly of an embodiment of the present invention when the vehicle is turning right;

fig. 6 is a differential schematic diagram of the power drive assembly of an embodiment of the present invention when the vehicle is turning left.

Reference numerals illustrate:

1. a first half shaft; 2. an output shaft; 3. a driving device; 4. a planet carrier; 5. a first sun gear; 6. a first planet; 7. a second planet wheel; 8. an inner gear ring; 9. a third planet wheel; 10. a fourth planetary gear; 11. a fifth planet; 12. a second sun gear; 13. a third sun gear; 14. a second half shaft; 20. a first gear; 21. a second gear; 22. a third gear; 23. and a fourth gear.

Detailed Description

In order that the above objects, features and advantages of the invention will be readily understood, a more particular description of the invention will be rendered by reference to specific embodiments thereof which are illustrated in the appended drawings. While the invention is susceptible of embodiment in the drawings, it is to be understood that the invention may be embodied in various forms and should not be construed as limited to the embodiments set forth herein, but rather are provided to provide a more thorough and complete understanding of the invention. It should be understood that the drawings and embodiments of the invention are for illustration purposes only and are not intended to limit the scope of the present invention.

In the coordinate system XYZ provided herein, the positive direction of the X axis represents the right direction, the negative direction of the X axis represents the left direction, the positive direction of the Y axis represents the rear direction, the negative direction of the Y axis represents the front direction, the positive direction of the Z axis represents the upper direction, and the negative direction of the Z axis represents the lower direction.

It should be understood that the various steps recited in the method embodiments of the present invention may be performed in a different order and/or performed in parallel. Furthermore, method embodiments may include additional steps and/or omit performing the illustrated steps. The scope of the invention is not limited in this respect.

The term "including" and variations thereof as used herein are intended to be open-ended, i.e., including, but not limited to. The term "based on" is based at least in part on. The term "one embodiment" means "at least one embodiment"; the term "another embodiment" means "at least one additional embodiment"; the term "some embodiments" means "at least some embodiments"; the term "optionally" means "alternative embodiments". Related definitions of other terms will be given in the description below. It should be noted that the terms "first," "second," and the like herein are merely used for distinguishing between different devices, modules, or units and not for limiting the order or interdependence of the functions performed by such devices, modules, or units.

It should be noted that references to "one", "a plurality" and "a plurality" in this disclosure are intended to be illustrative rather than limiting, and those skilled in the art will appreciate that "one or more" is intended to be construed as "one or more" unless the context clearly indicates otherwise.

The names of messages or information interacted between the devices in the embodiments of the present invention are for illustrative purposes only and are not intended to limit the scope of such messages or information.

With the continuous development of electric vehicles, the disadvantage of short endurance mileage of the electric vehicles is gradually improved, so that the electric vehicles are more and more favored by consumers. The improvement of the endurance mileage of the electric automobile mainly results from the improvement of the battery capacity, but the increase of the battery capacity leads to the increasing weight of the electric automobile, so that in order to realize the light weight, the weight reduction of other parts is more and more interesting.

The power driving assembly of the electric automobile mainly comprises a motor, a speed changer and a differential mechanism, wherein the output torque of the motor is regulated by the speed changer and then is sequentially transmitted to a left half shaft and a right half shaft by a transmission shaft and the differential mechanism, and the rotation speeds of the left half shaft and the right half shaft are the same when the automobile runs in a straight line under the action of the differential mechanism; when the automobile turns, the differential mechanism makes the rotation speeds of the left half shaft and the right half shaft different, namely, the rotation speed of the outer side wheels is ensured to be larger than that of the inner side wheels, so that the automobile can turn stably.

At present, most of speed variators and differentials are of independent structures, and the speed variators and the differentials are connected through driving of a transmission shaft, so that the whole size and weight of a power assembly are large, and occupied space is large. As shown in fig. 1 and 2, the related art implements a differential function through a circular gear, in which a first gear 20 is engaged with a second gear 21 and a third gear 22 on a right half shaft of a vehicle, respectively, and the second gear 21 is engaged with a fourth gear 23 on a left half shaft of the vehicle, and the differential function is implemented through a parameter ratio between the respective gears.

The differential shown in fig. 1 and 2 reduces space occupation compared to the bevel gear configuration of a conventional differential. However, the rotational speed and torque transmission chain of the left half axle of the vehicle is: the transmission chain of the rotation speed and the torque of the left half shaft of the vehicle and the right half shaft of the vehicle is as follows: the first gear 20, the third gear 22 and the right half shaft of the vehicle, the rotational speeds of the left half shaft and the right half shaft of the vehicle and the torque transmission chains are converged at the first gear 20, and when the gear parameter design is performed, the parameters of the first gear 20 are mutually limited by the two transmission chains, so that the degree of freedom of the gear parameter design is poor.

In view of the above problems in the prior art, embodiments of the present invention provide a power drive assembly and a vehicle.

As shown in fig. 3, the power driving assembly provided by the embodiment of the invention comprises a driving device 3, a speed reducing device, a differential device, a planet carrier 4, a first half shaft 1, a second half shaft 14 and a shell;

an inner gear ring 8 is fixedly arranged on the inner side of the shell, a first sun gear 5 is arranged on the output shaft 2 of the driving device 3, a second sun gear 12 is arranged on the first half shaft 1, and a third sun gear 13 is arranged on the second half shaft 14;

the speed reducing device comprises a speed reducing planetary gear set, each gear in the speed reducing planetary gear set is arranged on the planet carrier 4 in a autorotation manner, and the speed reducing planetary gear set is meshed with the first sun gear 5 and the annular gear 8 respectively;

the differential device comprises a third planet wheel 9, a fourth planet wheel 10 and a fifth planet wheel 11, wherein the third planet wheel 9 is fixedly connected with the fifth planet wheel 11, the third planet wheel 9, the fourth planet wheel 10 and the fifth planet wheel 11 are respectively and rotatably arranged on the planet carrier 4, the third planet wheel 9 is meshed with the fourth planet wheel 10, the fourth planet wheel 10 is meshed with the second sun wheel 12, and the fifth planet wheel 11 is meshed with the third sun wheel 13.

Specifically, the driving device 3 may include a power output apparatus such as an engine and a motor, as shown by TM in fig. 3, and OUT may be regarded as a wheel in fig. 3. The shell can be cylindrical, the annular gear 8 can be fixedly arranged on the inner side of the shell along the circumferential direction of the shell, and the annular gear 8 is coaxial with the shell. The first axle 1 may be the left axle of the vehicle and the second axle 14 corresponds to the right axle of the vehicle. Alternatively, the first axle 1 may be a right axle of the vehicle and the second axle 14 corresponds to a left axle of the vehicle. The first half shaft 1 and the second half shaft 14 may be coaxial with the housing and the ring gear 8. Both ends of the carrier 4 may be supported by the housing via bearings.

The torque transmission path of the driving device 3 to the first half shaft 1 is: the driving device 3-the output shaft 2-the first sun gear 5-the decelerating planetary gear set-the planet carrier 4-the third planetary gear 9-the fourth planetary gear 10-the second sun gear 12-the first half shaft 1.

The torque transmission path of the drive device 3 to the second half shaft 14 is: the driving device 3-the output shaft 2-the first sun gear 5-the reduction planetary gear set-the planet carrier 4-the fifth planetary gear 11-the third sun gear 13-the second half shaft 14.

In this embodiment, the output torque of the driving device 3 is transmitted to the first sun gear 5 through the output shaft 2, the first sun gear 5 is meshed with the reduction planetary gear set in the reduction device, the reduction planetary gear set is meshed with the inner gear ring 8, and since each gear of the reduction planetary gear set is rotatably arranged on the planet carrier 4 and the inner gear ring 8 is fixed, the first sun gear 5 can drive the reduction planetary gear set to rotate, and the rotation of the reduction planetary gear set can be transmitted to the planet carrier 4 through the inner gear ring 8, so as to realize the reduction torque-up function of the reduction device.

The third planet wheel 9, the fourth planet wheel 10 and the fifth planet wheel 11 in the differential device are arranged on the planet carrier 4 in a rotatable manner, the third planet wheel 9 drives the first half shaft 1 through the fourth planet wheel 10, and the fifth planet wheel 11 directly drives the second half shaft 14. When the vehicle is in straight line, the third planetary gear 9 is fixedly connected with the fifth planetary gear 11, so that the rotation speeds of the third planetary gear 9 and the fifth planetary gear 11 are the same, and the rotation speeds of the first half shaft 1 and the second half shaft 14 are the same when the vehicle is in straight line. When the vehicle turns, the third planet wheel 9, the fourth planet wheel 10 and the fifth planet wheel 11 can not only revolve around the first half shaft 1 and the second half shaft 14 under the drive of the planet carrier 4, but also rotate relative to the planet carrier 4, and the first half shaft 1 and the second half shaft 14 can generate a rotation speed difference so as to realize the differential function of the differential mechanism.

Compared with the prior art that the speed changer and the differential mechanism are respectively of independent structures, the speed reducing mechanism integrates the speed reducing function and the differential mechanism into one set of power driving assembly, and a transmission shaft is not required to be additionally designed to connect the speed changer and the differential mechanism, so that the structure volume and the weight are effectively reduced, and the vehicle weight is favorably realized. The torque transmission path of the carrier 4 to the first half shaft 1 is: the torque transmission path from the planet carrier 4 to the third planet wheel 9 to the fourth planet wheel 10 to the second sun wheel 12 to the first half shaft 1 and from the planet carrier 4 to the second half shaft 14 is as follows: the two torque transmission paths are independent, so that the limitation of the superposition of the torque transmission paths on the design of gear parameters (such as the tooth ratio) is avoided, and the degree of freedom of the parameter design of gears in the differential device is improved.

In addition, because the speed reduction function and the differential function are integrated in one set of power driving assembly, the speed reduction device and the differential device can be lubricated simultaneously, wherein the speed reduction device rotates and the dropped lubricating oil can lubricate the differential device, the using amount of the lubricating oil can be reduced, and the cost is further reduced. Meanwhile, the length of the lubricating oil pipeline can be reduced, and the occupation of the lubricating oil pipeline to the space can be reduced.

Optionally, the speed reduction planetary gear set includes a first planetary gear 6 and a second planetary gear 7, the first planetary gear 6 and the second planetary gear 7 are fixedly connected, the first planetary gear 6 and the second planetary gear 7 are rotatably disposed on the planet carrier 4, the first planetary gear 6 is meshed with the first sun gear 5, and the second planetary gear 7 is meshed with the inner gear ring 8.

Specifically, the torque transmission path of the driving device 3 to the first half shaft 1 is specifically: the driving device 3-the output shaft 2-the first sun gear 5-the first planet gear 6-the second planet gear 7-the planet carrier 4-the third planet gear 9-the fourth planet gear 10-the second sun gear 12-the first half shaft 1.

The torque transmission path of the driving device 3 to the second half shaft 14 is specifically: the driving device 3-the output shaft 2-the first sun gear 5-the first planet gear 6-the second planet gear 7-the planet carrier 4-the fifth planet gear 11-the third sun gear 13-the second half shaft 14.

As shown in fig. 4, S1 is the rotation speed of the first sun gear 5, tm is the torque of the first sun gear 5, tload is the torque of the carrier 4, C is the rotation speed of the carrier 4, R is the rotation speed of the ring gear 8, S2 is the rotation speed of the second sun gear 12, S3 is the rotation speed of the third sun gear 13, and the reduction ratio of the reduction gear can be determined according to the formula one.

Wherein i represents the reduction ratio of the reduction gear, Z _R Indicating the number of teeth, Z, of the ring gear 8 _P1 Indicating the number of teeth, Z, of the first planet 6 _S1 Indicating the number of teeth, Z, of the first sun gear 5 _P2 Representing the number of teeth of the second planet wheel 7.

Alternatively, the gear ratio between the second sun gear 12 and the third sun gear 13 is equal to the gear ratio between the third planet gears 9 and the fifth planet gears 11.

In particular, the gear ratios between the second sun gear 12 and the third sun gear 13, and between the third planet gears 9 and the fifth planet gears 11, may each preferably be 1. I.e. the number of teeth of the second sun gear 12 is the same as the number of teeth of the third sun gear 13.

When the vehicle runs straight, the first half shaft 1 and the second half shaft 14 of the vehicle share the planet carrier 4, the third planet wheel 9, the fourth planet wheel 10 and the fifth planet wheel 11 revolve around the first sun wheel 5 under the drive of the planet carrier 4, and the third planet wheel 9, the fourth planet wheel 10 and the fifth planet wheel 11 cannot rotate, so that the output of the first half shaft 1 and the second half shaft 14 achieve the same rotation speed and torque.

When the vehicle turns and runs, the third planet wheel 9, the fourth planet wheel 10 and the fifth planet wheel 11 not only revolve under the drive of the planet carrier 4, but also rotate, so that the first half shaft 1 and the second half shaft 14 output different rotating speeds, and the differential mechanism function is realized.

Specifically, taking the first axle 1 as the left axle of the vehicle and the second axle 14 as the right axle of the vehicle as an example, the principle of achieving the differential is as follows:

as shown in fig. 5, when the rotational speed of the left axle output of the vehicle is required to be higher, i.e., the vehicle turns right, the speed value at which the second sun gear 12 rises is equal to the speed value at which the third sun gear 13 falls, which can be achieved by the ratio of the numbers of teeth of the second sun gear 12 and the third sun gear 13.

As shown in fig. 6, when the rotational speed of the output of the right half shaft of the vehicle is required to be higher, i.e., the vehicle turns left, it is possible to achieve that the speed value at which the second sun gear 12 is lowered is equal to the speed value at which the third sun gear 13 is raised by the ratio of the numbers of teeth of the second sun gear 12 and the third sun gear 13.

Therefore, to realize the differential function, the speed change value n of the second sun gear 12 is required _S2 Equal to the speed variation n of the third sun gear 13 _S3 And the direction of change is opposite.

As a result of the fact that,

thus, w _S2 ＝w _S3 ，w _S2 Represents the angular velocity change value, w, of the second sun gear 12 _S3 The angular velocity change value of the third sun gear 13 is shown, and pi represents the circumference ratio.

As known from the gear transmission principle, the linear speeds of the gears meshed with each other are equal, and thus the relationship between the gears is shown in formula two.

Wherein w is _S3 Represents the angular velocity change value, r, of the third sun gear 13 _S3 Represents the radius, w, of the third sun gear 13 _p5 Represents the angular velocity variation value, r, of the fifth planet 11 _p5 Represents the radius, w, of the fifth planet 11 _S2 Represents the angular velocity change value, r, of the second sun gear 12 _S2 Represents the radius, w, of the second sun gear 12 _p4 Representing a fourth planet wheel 10, r _p4 Represents the radius, w, of the fourth planet wheel 10 _p3 Represents the angular velocity variation value, r, of the third planet wheel 9 _p3 The radius of the third planetary gear 9 is represented by r, the radius of the gear is represented by m, the modulus of the gear is represented by m, and the number of teeth of the gear is represented by z.

Since the second sun gear 12 meshes with the fourth planet gear 10 and the fourth planet gear 10 meshes with the third planet gear 9, the moduli of the three gears are equal, namely:

m _S2 ＝m _p4 ＝m _p3 ，

wherein m is _S2 Representing the modulus, m, of the second sun gear 12 _p4 Representing the modulus, m, of the fourth planet wheel 10 _p3 Representing the modulus of the third planet wheel 9.

Since the third sun gear 13 is meshed with the fifth planet gear 11, m _S3 ＝m _p5 ，m _S3 Represents the modulus, m, of the third sun gear 13 _p5 The modulus of the fifth planet 11 is shown.

Because the third planet wheel 9 is fixedly connected with the fifth planet wheel 11, the angle change values of the third planet wheel 9 and the fifth planet wheel are equal, namely

w _p3 ＝w _p5 ，

The following formula can be obtained in combination with formula two:

obtained by calculation, z _S3 *z _p3 ＝z _S2 *z _p5 。

Wherein z is _S3 Indicating the number of teeth, z, of the third sun gear 13 _p3 Representing the number of teeth, z, of the third planet wheel 9 _S2 Representing the number of teeth, z, of the second sun gear 12 _p5 The number of teeth of the fifth planet 11 is shown.

That is, the gear ratio between the second sun gear 12 and the third sun gear 13 is the same as the gear ratio between the third planetary gear 9 and the fifth planetary gear 11, and specifically, it is preferable that the gear number of the third planetary gear 9 is the same as the gear number of the fifth planetary gear 11, and the gear number of the second sun gear 12 is the same as the gear number of the third sun gear 13, that is, the gear ratio k0 between the second sun gear 12 and the third sun gear 13 is equal to 1.

Optionally, the number of the speed reducing devices is at least three, and every two adjacent speed reducing devices are spaced along the annular gear 8 by a first preset angle.

Specifically, since the first planetary gears 6 and the second planetary gears 7 are fixedly connected in one-to-one correspondence, the number of the first planetary gears 6 and the second planetary gears 7 in the speed reducing device is the same, and is at least three. Wherein, each first planet wheel 6 and second planet wheel 7 are respectively arranged on the planet carrier 4 along the extending direction of the annular gear 8 at intervals, every two adjacent first planet wheels 6 are spaced by a first preset angle, and every two adjacent second planet wheels 7 are spaced by a first preset angle. For example, when the number of the speed reducing devices is three, the first preset angle may be 120 degrees.

Optionally, the number of the differential devices is at least three, and every two adjacent differential devices are spaced along the annular gear 8 by a second preset angle.

Specifically, the number of the third planetary gears 9, the fourth planetary gears 10 and the fifth planetary gears 11 in the differential device is the same, and is at least three. The respective third planetary gears 9, fourth planetary gears 10 and fifth planetary gears 11 are disposed on the carrier 4 at intervals along the extending direction of the ring gear 8, every adjacent two third planetary gears 9 are spaced apart by a second preset angle, every adjacent two fourth planetary gears 10 are spaced apart by a second preset angle, and every adjacent two fifth planetary gears 11 are spaced apart by a second preset angle. For example, when the number of differential devices is three, the second preset angle may be 120 degrees.

In this alternative embodiment, the plurality of speed reducing devices and the plurality of differential devices are arranged on the planet carrier 4 at intervals, so that the planet carrier 4 can be better supported on the annular gear 8, and the rotation of the planet carrier 4 along the annular gear 8 is smoother.

Optionally, the first planet wheel 6, the second planet wheel 7, the third planet wheel 9, the fourth planet wheel 10 and the fifth planet wheel 11 are respectively sleeved on a planet wheel shaft of the planet carrier 4 through bearings.

Specifically, each planet wheel is respectively arranged on a planet wheel shaft of the planet carrier 4 through a bearing sleeve, so that each planet wheel can rotate on the planet wheel shaft relative to the planet carrier 4. The first planet wheel 6, the second planet wheel 7, the third planet wheel 9 and the fifth planet wheel 11 can be arranged on the same planet wheel shaft, so that the structure of the planet carrier is simplified, and the processing is convenient. The wheel sets of the first planet wheel 6 and the second planet wheel 7 and the wheel sets of the third planet wheel 9 and the fifth planet wheel 11 can be respectively arranged on two different planet wheel shafts, and the planet wheel shafts can be overlapped, so that the axial size of the power driving assembly is reduced, and the occupation of space is reduced.

Alternatively, one end of the first half shaft 1 is disposed opposite to one end of the second half shaft 14, and the first half shaft 1 is coaxial with the second half shaft 14.

Alternatively, the second sun gear 12 is disposed on the first half shaft 1 near an end of the second half shaft 14, and the third sun gear 13 is disposed on the second half shaft 14 near an end of the first half shaft 1.

Illustratively, assuming that the first axle 1 is the left axle of the vehicle and the second axle 14 is the right axle of the vehicle, the second sun gear 12 is disposed at the right end of the first axle 1 and the second axle 14 is disposed at the left end of the vehicle.

In this alternative embodiment, the second sun gear 12 and the third sun gear 13 are disposed as close as possible, so that the axial dimension of the power driving assembly can be reduced, and the volume of the power driving assembly can be further reduced.

Alternatively, the output shaft 2 of the driving device 3 is sleeved on the first half shaft 1 in a hollow manner and rotates independently of each other.

Specifically, the output shaft 2 of the driving device 3 may be a cylinder suitable for the first half shaft 1 to penetrate, and is sleeved on the first half shaft 1, and the output shaft 2 may rotate relative to the first half shaft 1 under the driving of the driving device 3. The two are coaxially arranged, so that the occupation of the whole structure to the space can be reduced, and the size of the power driving assembly is further reduced.

The vehicle provided by the embodiment of the invention comprises the power driving assembly.

The technical improvements and technical effects of the vehicle are the same as those of the above-described power drive assembly, and will not be described in detail herein.

Those skilled in the art will appreciate that implementing all or part of the above-described methods in accordance with the embodiments may be accomplished by way of a computer program stored on a computer readable storage medium, which when executed may comprise the steps of the embodiments of the methods described above. The storage medium may be a magnetic disk, an optical disk, a Read-Only Memory (ROM), a random access Memory (Random Access Memory, RAM), or the like. In this application, the units described as separate units may or may not be physically separate, and units shown as units may or may not be physical units, may be located in one place, or may be distributed on a plurality of network units. Some or all of the units may be selected according to actual needs to achieve the purpose of the embodiment of the present invention. In addition, each functional unit in the embodiments of the present invention may be integrated in one processing unit, or each unit may exist alone physically, or two or more units may be integrated in one unit. The integrated units may be implemented in hardware or in software functional units.

Although the invention is disclosed above, the scope of the invention is not limited thereto. Various changes and modifications may be made by one skilled in the art without departing from the spirit and scope of the invention, and these changes and modifications will fall within the scope of the invention.

Claims (10)

1. The power driving assembly is characterized by comprising a driving device (3), a speed reducing device, a differential device, a planet carrier (4), a first half shaft (1), a second half shaft (14) and a shell;

an inner gear ring (8) is fixedly arranged on the inner side of the shell, a first sun gear (5) is arranged on an output shaft (2) of the driving device (3), a second sun gear (12) is arranged on the first half shaft (1), and a third sun gear (13) is arranged on the second half shaft (14);

the speed reducing device comprises a speed reducing planetary gear set, each gear in the speed reducing planetary gear set is arranged on the planet carrier (4) in a autorotation mode, and the speed reducing planetary gear set is meshed with the first sun gear (5) and the inner gear ring (8) respectively;

the differential device comprises a third planet wheel (9), a fourth planet wheel (10) and a fifth planet wheel (11), wherein the third planet wheel (9) is fixedly connected with the fifth planet wheel (11), the third planet wheel (9), the fourth planet wheel (10) and the fifth planet wheel (11) are respectively and rotatably arranged on the planet carrier (4), the third planet wheel (9) is meshed with the fourth planet wheel (10), the fourth planet wheel (10) is meshed with the second sun wheel (12), and the fifth planet wheel (11) is meshed with the third sun wheel (13).

2. The power drive assembly according to claim 1, characterized in that the reduction planetary gear set comprises a first planetary gear (6) and a second planetary gear (7), the first planetary gear (6) and the second planetary gear (7) are fixedly connected, and the first planetary gear (6) and the second planetary gear (7) are rotatably arranged on the planet carrier (4), the first planetary gear (6) is meshed with the first sun gear (5), and the second planetary gear (7) is meshed with the inner gear ring (8).

3. A power drive assembly according to claim 1, characterized in that the gear ratio between the second sun gear (12) and the third sun gear (13) is equal to the gear ratio between the third planet gear (9) and the fifth planet gear (11).

4. The power drive assembly according to claim 1, characterized in that the number of reduction means is at least three, each adjacent two reduction means being spaced along the annulus gear (8) by a first preset angle.

5. The power drive assembly according to any one of claims 1 to 4, characterized in that the number of differential devices is at least three, each adjacent two of the differential devices being spaced along the ring gear (8) by a second preset angle.

6. The power drive assembly according to any one of claims 2 to 4, characterized in that the first planetary wheel (6), the second planetary wheel (7), the third planetary wheel (9), the fourth planetary wheel (10) and the fifth planetary wheel (11) are respectively sleeved on a planetary wheel shaft of the planetary carrier (4) through bearings.

7. The power drive assembly according to any one of claims 1 to 4, characterized in that one end of the first half shaft (1) is arranged opposite one end of the second half shaft (14), and the first half shaft (1) is coaxial with the second half shaft (14).

8. The power drive assembly according to claim 7, characterized in that the second sun gear (12) is arranged on the first half shaft (1) near an end of the second half shaft (14), and the third sun gear (13) is arranged on the second half shaft (14) near an end of the first half shaft (1).

9. A power drive assembly according to any one of claims 1-4, characterized in that the output shaft (2) of the drive means (3) is hollow around the first half-shaft (1) and rotates independently of each other.

10. A vehicle comprising a power drive assembly as claimed in any one of claims 1 to 9.