CN104670010B - A kind of electronic active spur gear differential mechanism for possessing torque fixed direction allocation function - Google Patents

Abstract

The invention discloses an electric active spur gear differential with torque orientation distribution function, which comprises: a driving motor, a main differential, and a coupling transmission device. The main differential includes a drive shaft, a transmission, a first output shaft and a second output shaft that can rotate around the axis; the coupling transmission includes a first planetary gear train and a second planetary gear train, and the second planetary gear train is connected to the motor output The shaft is connected to receive the torque output by the output shaft of the motor and output another torque. The first planetary gear train is connected to the second planetary gear train to receive the torque output by the second planetary gear train. The first planetary gear train Connected to the transmission to provide torque in opposite directions to the first output shaft and the second output shaft. The present invention can selectively distribute the driving torque transmitted through it to the half shafts on both sides, and realize the torque distribution between the two output shafts by directly forcing the rotation of the planetary gear pair connecting the two output shafts, that is, the torque Distribution is done directly inside the differential.

Description

An Electric Active Spur Gear Differential with Torque Oriented Distribution Function

technical field

The invention relates to the field of automobile transmission, in particular to an electric active spur gear differential with torque orientation distribution function.

Background technique

The car differential is the main part of the drive axle. Its function is to transmit power to the left and right half shafts of the car while allowing the left and right half shafts to rotate at different speeds, so that the wheels on both sides can drive as purely as possible. Reduce the friction between the tire and the ground.

When the vehicle is running, the spur gear differential, like the traditional differential, has the function of balancing the different rotational speeds between the left and right wheels. In this case, when the vehicle is turning, the wheel with a larger trajectory radius rotates faster than the wheel with a smaller trajectory radius, but the torque distribution ratio of the left and right wheels is fixed at 1:1. This is possible to a certain extent, but for optimal vehicle control, the wheels with larger turning radii should output more torque than the wheels with lower turning radii. In fact, the active differential with torque veering distribution function is installed on the rear axle, which can prevent the vehicle from understeering the front wheels, and when the active torque distribution control system intervenes, it will not slow down the vehicle, thus improving the performance of the vehicle. safety and maneuverability.

In addition, although the traditional differential can reasonably distribute the driving force of the car on the driving wheels on a well-attached flat road, once encountering rough and muddy road conditions, when one of the driving wheels slips or even completely idling, A differential would waste all of the drive wheels on a slipping wheel, preventing the car from moving properly. Of course, the existence of limited-slip and locking differentials can effectively solve this problem, but this type of differential tends to make the speed of the driving wheels on both sides of the wheel the same. Therefore, the maneuverability of the vehicle in high-speed turns is limited to a certain extent.

Based on this, it is necessary to design a new type of electric active differential with torque directional distribution capability on the basis of the mechanical structure of the spur gear differential.

Contents of the invention

The invention designs and develops an electric active spur gear differential with the function of torque directional distribution, which solves the defect that the torque of the left and right wheels can only be evenly distributed in the prior art, and realizes the directional input of the drive shaft according to the demand. Torque is distributed to the left and right wheels.

The technical scheme provided by the invention is:

An electric active spur gear differential with torque directional distribution, comprising:

a driving motor having a motor output shaft capable of outputting torque;

The main differential, which includes a drive shaft, a transmission device, a first output shaft and a second output shaft rotatable around an axis, and the drive shaft will drive the first output shaft and the second output shaft through the transmission device to be able to Rotate in the same direction at the same or different speeds;

The coupling transmission device includes a first planetary gear train and a second planetary gear train, the second planetary gear train is connected to the output shaft of the motor, receives the torque output by the output shaft of the motor, and outputs another torque , the first planetary gear train is connected to the second planetary gear train to receive the torque output by the second planetary gear train, the first planetary gear train is connected to the transmission device, and is the first The output shaft and the second output shaft provide torque in opposite directions.

Preferably, the transmission includes

a first sun gear coaxially fixedly connected to the first output shaft for common rotation with the first output shaft;

a second sun gear coaxially fixedly connected to the second output shaft for common rotation with the second output shaft;

a first planet gear meshing with the first sun gear;

a second planet gear meshing with the second sun gear;

a first planet carrier, which is rotatably connected to the first planet wheel;

a second planet carrier, which is rotatably connected to the second planet wheel;

a differential case, which is rotatably connected to the first planetary carrier and the second planetary carrier, and the drive shaft drives the differential case to rotate through a pair of meshed gears, so that the first planetary gear and the second planetary carrier The second planetary gears revolve around the first sun gear and the second sun gear respectively.

Preferably, the first planetary gear train includes a third sun gear, a third planetary gear, a fourth planetary gear and a first ring gear, the third sun gear is fixed relative to the ground, and the third sun gear and the first planetary gear The three planetary gears, the fourth planetary gear and the first ring gear mesh sequentially, the fourth planetary gear is rotatably connected to the second planetary carrier, and the third planetary gear is rotatably connected to the third planetary carrier, The revolution of the third planetary gear is output through the third planetary carrier.

Preferably, the second planetary gear train includes a fourth sun gear, a fifth planetary gear, and a second ring gear, and the fourth sun gear is coaxially fixedly connected to the output shaft of the motor, so that the fourth The sun gear rotates together with the output shaft of the motor, the fifth planetary gear meshes with the fourth sun gear and the second ring gear respectively, and the fourth planetary carrier is rotatably connected to the fifth planetary gear, so that the revolution of the fifth planetary gear is output through the fourth planetary carrier, the third planetary carrier is fixedly connected to the fourth planetary carrier, and the first ring gear is fixedly connected to the second ring gear .

Preferably, the third planet carrier and the fourth planet carrier are integrally formed.

Preferably, the first ring gear and the second ring gear are integrally formed.

An automobile, comprising the above-mentioned electric active spur gear differential with the function of torque directional distribution.

The beneficial effects of the present invention are:

The electric active positive differential is the best substitute for the traditional clutch-based differential with a coupling transmission, because the differential does not use the traditional bevel pinion of the differential, but uses a positive positive differential with planetary gears arranged in parallel. gear, which means that the required space and weight are greatly reduced, while the potential torque capacity is significantly increased. And the design of the differential is more compact, lighter and less noisy. Efficiency and performance are greatly improved. Data show that using a spur gear differential instead of a traditional bevel gear differential can save more than 30% of the weight of the rear axle of a mid-level car and almost 70% of the space for the transverse axis.

1. The electric active spur gear differential with torque directional distribution function according to the present invention can selectively directional distribute the driving torque transmitted through it to the half shafts on both sides, and when the torque is directional distribution, due to It will not change the total torque, so it will not slow down the vehicle, and it can increase the turning maneuverability of the car and the driving pleasure of the driver.

2. The active differential implements the torque distribution between the left and right half shafts through the rotation of the planetary gear pairs that are directly forced to connect the left and right half shafts, that is, the torque distribution is directly completed inside the differential. Therefore, the differential does not require any redundant components, and its required axial space is greatly reduced.

3. A set of coupling mechanism is used as the power transmission mechanism for the torque distribution of the differential, which has the function of deceleration and power coupling at the same time, and the differential motor can be arranged coaxially to make the structure of the differential more compact . The motor does not rotate when torque is not being distributed, and only rotates to provide torque when torque is being actively distributed.

4. Only one motor is needed as the power source for the differential to realize torque distribution, which is easy to control. That is, it is only necessary to control the forward rotation or reverse rotation of the motor rotor to distribute the torque on the left and right half shafts in a directional manner. This is different from other differentials that realize torque distribution based on clutches or brakes, which need to have two sets of clutches or brakes as power sources at the same time, resulting in a large number of parts and a complicated structure.

5. Using the motor as the power source for the torque distribution of the differential is also beneficial to the application of the differential in electric vehicles or hybrid vehicles, thereby expanding the field of use of the differential. That is to say, the present invention can be installed on vehicles powered by traditional power sources as well as vehicles powered by new energy sources, and has a wide range of applications.

6. Since the present invention is an improved design on the basis of the original spur gear differential structure, it has the characteristics of low cost of transformation and processing, and good inheritance of manufacturing process and technological process.

Description of drawings

Fig. 1 is a structural schematic diagram of a differential gear according to the present invention.

Fig. 2 is a sectional view of A-A in Fig. 1 .

Fig. 3 is the working principle of the first planetary gear train according to the present invention.

Fig. 4 is a schematic diagram of the torque flow path when the differential torque distribution device according to the present invention is not working.

Fig. 5 is a schematic diagram of the flow path of the torque distributed by the torque directional distribution device under the right turning condition of the vehicle.

Detailed ways

The present invention will be further described in detail below in conjunction with the accompanying drawings, so that those skilled in the art can implement it with reference to the description.

Automotive differential is a differential mechanism that can transmit rotational motion from one shaft to two shafts, and enable the latter to rotate at different speeds. As shown in Figure 1, the automotive differential transfers the vehicle engine The generated torque is distributed to the first output shaft 62 and the second output shaft 64 respectively located on the left and right sides of the vehicle, causing them to rotate along their axes.

The differential of the present invention includes a differential housing 22, which contains other working parts, and the differential also includes two asymmetrical first sun gears 16, second sun gears 18 and first planetary gears 12. And the planetary gear device that the second planetary gear 14 forms. Meshing of the differential The first planetary gear 12 and the second planetary gear 14 are respectively meshed with the first sun gear 16 and the second sun gear 18, that is, the first planetary gear 12 is meshed with the first sun gear 16 but not with the second sun gear. The gear 18 meshes, and the second planetary gear 14 meshes with the second sun gear 18 but does not mesh with the first sun gear 16 . The first sun gear 16 and the second sun gear 18 are respectively connected with the first output shaft 62 and the second output shaft 64 . The first planet carrier 26 of the first planetary gear 12 is connected with the differential case 22 so that it can rotate together with the differential case 22 . The other end of the second planetary gear 14 and its second planetary carrier 36 protrude outward through the hole 15 on the differential case 22 and are connected to the first planetary gear train 30 of the torque directional distribution device 60 . This type of spur gear differential can realize the ability of directional torque distribution to the first output shaft 62 and the second output shaft 64 through the combination of the second planetary gear 14 and its second planetary carrier 36 and the torque distribution device 60 , and the first planetary gear 12 and the second planetary gear 14 of the differential have theoretically realized the same function as the bevel planetary gear in the bevel gear differential.

The differential of the present invention can work as a conventional differential. The outside of the drive shaft 72 is connected to the engine through a drive train to transmit the drive torque of the engine, and a bevel drive gear 74 is mounted on it. Bevel drive gear 74 meshes with bevel ring gear 66 mounted on differential case 22 . When the engine applies torque and turns drive shaft 72 , bevel drive gear 74 thereon turns bevel ring gear 66 and differential case 22 . The differential case 22 then rotates the first planetary carrier 26, and then the first planetary carrier 26 causes the first planetary gear 12 and the second planetary gear 14 to produce a revolution around the x-axis and rotate the first sun gear 16 and the second planetary gear 14 respectively meshed with it. The second sun gear 18 , in turn, rotates the first output shaft 62 and the second output shaft 64 . If one of the first output shaft 62 or the second output shaft 64 rotates faster than the other, such as when making a turn, the first planetary gears 12 and the second planetary gears 14 will each spin, but will still impart torque. It is transmitted to the first sun gear 16 and the second sun gear 18 meshing with them respectively and the first output shaft 62 or the second output shaft 64 connected thereto.

The spur gear differential of the present invention also has the ability to selectively distribute the torque output from the engine to the first output shaft 62 and the second output shaft 64, so that the first output shaft 62 and the second output shaft One of the 64 shafts is capable of transmitting more torque than the other. This ability to distribute torque orientation to the left and right wheels can greatly improve the vehicle's cornering maneuverability. For this purpose, the differential according to the invention is equipped with a torque directional distribution device 60 . Upon receiving a control signal, the torque directional distribution device 60 can distribute an additional torque via the first planetary gear 12 and the second planetary gear 14 to the first output shaft 62 and the second output shaft 64 . The torque directional distribution device 60 essentially includes a coupling drive 50 and a differential motor 70 .

The coupling gear 50 of the torque directional distribution device 60 includes a first planetary gear train 30 and a second planetary gear train 40 . Referring to FIG. 2 together, the first planetary gear train 30 has a fixed third sun gear 44 that cannot rotate around the X-axis. The first planetary gear train 30 also has two rotatable around the sun gear 44, the third planetary gear 34 and the fourth planetary gear 24 that are mutually meshed but not shared, the three sun gears 44 are only meshed with the third planetary gear 34 and not meshes with the fourth planetary gear 24. Wherein, the fourth planetary gear 24 shares the second planetary carrier 36 with the second planetary gear 14 of the differential, and its gear outer end is connected with the part where the second planetary gear 14 protrudes from the hole 15 of the differential case 22 Together. In this way, the fourth planetary gear 24 can be integrated with the second planetary gear 14 , and the torque directional distribution device 60 can control the torque of the differential by controlling the torque of the fourth planetary gear 24 .

The third planetary gear 34 of the first planetary gear train 30 also has a third planet carrier 42 for connection with the second planetary gear train 40 . The first planetary gear train 30 also has a freely rotatable first ring gear 28, which is also used in connection with the planetary gear train 40. The first ring gear 28 meshes with the fourth planetary gear 24 but does not mesh with the third planetary gear. 34 engagement.

The second planetary gear train 40 of the coupling transmission mechanism 50 has a second ring gear 32 that can rotate freely, and the second ring gear 32 is connected with the first ring gear 28, and the second ring gear 32 of the planetary gear train 40 is connected with the first ring gear 28. The first ring gear 28 of the first planetary gear train 30 can be processed as a whole. The second planetary gear train 40 also includes a fourth sun gear 56 for connecting to the differential motor 70 of the torque vectoring device 60 . The planetary gear train 40 also has a fifth planet gear 52 located between and meshing with the second ring gear 32 and a fourth sun gear 56 . The fourth planetary carrier 54 of the fifth planetary gear 52 of the second planetary gear train 40 is connected with the third planetary carrier 42 of the third planetary gear 34 of the first planetary gear train 30, as preferably, the second planetary gear train 40 The fourth planetary carrier 54 and the third planetary carrier 42 of the first planetary gear train 30 can be processed as a whole.

The differential motor 70 of the torque directional distributing device 60 includes a hollow-shaft motor 46 and a motor rotor 58 , and the above-mentioned second output shaft 64 protrudes outward from the hollow of the hollow-shaft motor 46 and is connected to the wheel. The hollow shaft motor 46 is stationary, and the motor rotor 58 can rotate about the X axis to output torque. The motor rotor 58 of the differential motor 70 is connected to the fourth sun gear 56 of the second planetary gear train 40 of the coupling transmission mechanism 50 . Preferably, the fourth sun gear 56 can be processed as a whole with the motor rotor 58 .

When the hollow-shaft motor 46 receives the control signal, the motor rotor 58 will rotate around the X-axis, and the fourth sun gear 56 on the motor rotor 58 will also rotate around the X-axis. The magnitude of the torque acting on the motor rotor 58 can be controlled according to the motor controller.

When the automobile is running straight, the torque control function is closed, and the motor rotor 58 does not rotate, which does not affect the distribution of the driving torque of the automobile. At this time, the differential case 22 and the first planetary carrier 26 and the second planetary carrier 36 thereon, the first sun gear 16 and the second sun gear 18 and the first output shaft 62 and the second output shaft 64 are all in the same speed rotation. Further, the first planetary gear 12 and the second planetary gear 14 only revolve around the X-axis at the same speed without rotation, and then the fourth planetary gear 24 of the first planetary gear train 30 connected to the second planetary gear 14 revolves around the X axis. The X-axis revolves at the same speed but does not rotate, and then the fourth planetary gear 24 of the first planetary gear train 30 rotates its first ring gear 28 to rotate around the X-axis at the same speed. Furthermore, the second ring gear 32 of the second planetary gear train 40 also rotates at the same speed. With reference to Fig. 3, at this time, the effect of the revolution of the fourth planetary gear 24 on the third planetary gear 34 can be regarded as the effect of the rotation of a ring gear 38 on the third planetary gear 34, as shown in Fig. 3, that is, the ring gear 38 , the third planetary gear 34 and the sun gear 44 form a planetary gear train 20 and the rotation speed of the ring gear 38 is the same as the revolution speed of the third planetary gear 34 . The revolution speed of the planetary gear 34 is different from the revolution speed of the ring gear 38, so the revolution speeds of the planetary gears 24 and 34 are different, that is, the revolution speed of the third planetary gear 34 is slightly faster than that of the fourth planetary gear 24. revolution speed. Here, the number of third planetary gears 34 is designed to be five, while the number of fourth planetary gears 24 is four. When the meshing range of the teeth of the fourth planetary gear 24 and the third planetary gear 34 was greater than 18 degrees, the third planetary gear 34a could be smoothly connected to the third planetary gear 34b before breaking away from the fourth planetary gear 24a. Four planetary gears 24b meshing and transmission, similarly, according to the tooth profile and the number of teeth of the ring gear 38 to design the tooth profile of the fourth planetary gear 24 and the condition of the number of teeth between any fourth planetary gear 24, the third planetary gear 34 Both of them can transmit each other smoothly without taking off the teeth or beating the teeth. And works like a normal planetary gear train.

At this time, it is necessary to ensure that the planetary gear train 20 is composed of the third sun gear 44 , the third planetary gear 34 and the ring gear 38 and the second planetary gear train 20 is composed of the fourth sun gear 56 , the fifth planetary gear 52 and the second ring gear 32 . The characteristic parameters of the planetary rows of the gear train 40 are consistent, because the third planet carrier 42 of the third planetary gear 34 of the planetary gear train 20 is connected with the fourth planet carrier 54 of the fourth planet gear 52 of the second planetary gear train 40 , That is, the third planetary carrier 42 and the fourth planetary carrier 54 of the planetary gear trains 20 and 40 have the same rotational speed at any moment. Simultaneously, the ring gear 38 of the planetary gear train 20 and the second ring gear 32 of the second planetary gear train 40 rotate at the same speed. According to the motion formula of planetary gears, at this moment, the third sun gear 44 of the planetary gear train 20 and The fourth sun gear 56 of the planetary gear train 40 has the same rotational speed. While the third sun gear 44 is fixed and does not rotate, it can be seen that the fourth sun gear 56 of the second planetary gear train 40 does not rotate at this time. That is, the motor rotor 58 is not rotating at this time.

When the torque control function is turned on, the hollow-shaft motor 46 of the torque directional distribution device 60 receives the control signal, and the motor rotor 58 and the fourth sun gear 56 on it will rotate, thereby coupling the second planetary gear train of the transmission mechanism 50 The fourth planetary gear 52 of 40 will revolve in the same direction, and then the fourth planetary carrier 54 thereof will rotate in the same direction, while the second ring gear 32 of the second planetary gear train 40 will rotate in the opposite direction. Then the third planet carrier 42 of the third planetary gear 34 of the first planetary gear train 30 rotates in the same direction, and then the third planetary gear 34 thereon revolves and rotates in the same direction, and the first planetary gear train 30 The first ring gear 28 rotates in the same direction as the second ring gear 32 of the second planetary gear train 40 but in the opposite direction to the third planet gears 34 . Thus, the fourth planetary gear 24 meshing with the first ring gear 28 and the third planetary gear 34 rotates. Furthermore, the first planetary gear 12 and the second planetary gear 14 also rotate. In this sense, when the vehicle is going straight and the hollow-shaft motor 46 of the torque directional distribution device 60 does not receive the control signal, the motor rotor 58 does not rotate, which does not affect the distribution of the driving torque of the vehicle. When the vehicle is turning or other operating conditions require torque distribution, the torque on the first output shaft 62 and the second output shaft 64 can be specifically distributed by controlling the forward rotation or reverse rotation of the motor rotor 58 . That is, when the rotational speeds of the wheels on both sides are the same, the motor rotor 58 is in a static state, and only rotates to provide torque when actively distributing torque.

Generally, when the differential is running, the hollow-shaft motor 46 does not receive a control signal, and its motor rotor 58 does not rotate around the X-axis, which is especially suitable for straight-line driving of the vehicle. In this case, the drive torque provided by the drive shaft 72 is equally divided between the first output shaft 62 and the second output shaft 64 and the wheels they drive. This is the same as a conventional differential. At this point, the differential can essentially operate as a conventional differential, transferring all torque and power from the bevel ring gear 66 to the differential case 22 and then rotating. The first planet carrier 26 and the second planet carrier 36 on it, and then the first planet wheel 12 and the second planet wheel 14 inside the differential revolve around the X axis without rotation, and then the first planet wheel 12 and the second planet wheel The two planetary gears 14 rotate the first sun gear 16 and the second sun gear 18 respectively meshed with them, and then respectively rotate the first output shaft 62 and the second output shaft 64 , as shown in FIG. 4 . Since the quill motor 46 does not receive a control signal, the motor rotor 58 does not rotate, the torque directional distribution device 60 does not transmit any torque, and does not otherwise affect the normal operation of the differential.

When the vehicle is turning, especially when turning at a high speed, the hollow shaft motor 46 of the torque direction distribution device 60 should receive a control signal to rotate the motor rotor 58 so that more torque direction is transmitted to the outer wheels of the vehicle. superior. For example, when the vehicle enters a right curve, it is assumed that the direction of rotation of the wheels during driving is positive, and vice versa. At this point, the wheels and first output shaft 62 on the left side of the vehicle will rotate faster than the wheels and second output shaft 64 on the right side of the vehicle. The hollow-shaft motor 46 of the torque directional distribution device 60 receives the control signal, so that the motor rotor 58 and the fourth sun gear 56 on it rotate in the opposite direction, and then couple the fifth gear of the second planetary gear train 40 of the transmission mechanism 50 . The planetary gear 52 rotates in the opposite direction, and the fourth planetary carrier 54 of the fifth planetary wheel 52 will rotate in the reverse direction, so that the second ring gear 32 of the second planetary gear train 40 coupled with the transmission mechanism 50 will produce a positive direction. rotation. Further, the third planetary carrier 42 of the first planetary gear train 30 of the coupling transmission mechanism 50 will rotate in the opposite direction, and then the third planetary gear 34 thereon will also produce a revolution in the reverse direction and rotate itself, while the first planetary gear train 30 will rotate in the opposite direction. The first ring gear 28 will rotate in the positive direction, and the fourth planetary gear 24 between the third planetary gear 34 and the first ring gear 28 and meshing with it will rotate in the positive direction. In this way, the second planetary gear 14 and the first planetary gear 12 connected thereto no longer only revolve freely around the X-axis, but generate positive rotation and reverse rotation respectively. Further, torques in opposite directions and in positive directions are generated to the second sun gear 18 and the first sun gear 16 meshed with them respectively and the second output shaft 64 and the first output shaft 62 respectively connected thereto. In fact, the coupling transmission mechanism 50 of the torque directional distribution device 60 acts as a torque multiplier, which can apply a much larger torque to the fourth sun gear 56 than the torque applied by the hollow shaft motor 46 to the fourth sun gear 56. On the first planetary wheel 12 and the second planetary wheel 14. Since the second planetary gears 14 and the first planetary gears 12 produce obstructive resistance and actuating power to the second output shaft 64 and the first output shaft 62 respectively, they convert the driving torque from the differential case 22 more onto the first output shaft 62 rather than the second output shaft 64 as shown in FIG. 5 . Therefore, the forced rotation of the second planetary gear 14 and the first planetary gear 12 will cause the first output shaft 62 to rotate at a higher speed. Therefore, at this time, the torque directional distributing device 60 acts to promote the overspeeding of the first output shaft 62 .

Generally speaking, the greater the reverse rotation torque of the hollow shaft motor 46 of the torque directional distribution device 60 , the greater the driving torque transmitted to the first output shaft 62 through the torque directional distribution device 60 .

The degree of action of the torque directional distribution device 60 depends on several conditions, all of which may be monitored by sensors mounted on the vehicle and processed by a processor to control the control signals that operate the hollow shaft motor 46, the monitored Conditions include vehicle speed, yaw rate, vehicle lateral and longitudinal acceleration, steering angle, wheel slip, engine and transmission operating parameters, and hollow shaft motor 46 temperature.

Similarly, when the vehicle enters a left bend, the wheels on the right side of the vehicle and the second output shaft 64 will rotate faster than the wheels and first output shaft 62 on the left side of the vehicle. At this time, the hollow shaft motor 46 of the torque directional distribution device 60 should receive a control signal to make the motor rotor 58 and the fourth sun gear 56 on it rotate in a positive direction. Similarly, at this time, the coupling transmission mechanism 50 will cause the first planetary gear 12 and the second planetary gear 14 to generate driving power and hindering resistance to the first output shaft 62 or the second output shaft 64 respectively. Therefore, more drive torque is transferred to the second output shaft 64 and the second output shaft 64 is given a higher rotational speed.

In addition, if the vehicle enters a slippery road or other roads with poor road conditions, when it is necessary to distribute the torque on the first output shaft 62 and the second output shaft 64 according to specific road conditions, the torque directional distribution device 60 can also be used to The hollow-shaft motor 46 receives electrical signals, and actively distributes the torque on the first output shaft 62 and the second output shaft 64 according to the road conditions so that the vehicle can run stably.

Although the embodiment of the present invention has been disclosed as above, it is not limited to the use listed in the specification and implementation, it can be applied to various fields suitable for the present invention, and it can be easily understood by those skilled in the art Therefore, the invention is not limited to the specific details and examples shown and described herein without departing from the general concept defined by the claims and their equivalents.

Claims (6)

1. An electric active spur gear differential with torque directional distribution function, characterized in that it comprises: a driving motor having a motor output shaft capable of outputting torque; The main differential, which includes a drive shaft, a transmission device, a first output shaft and a second output shaft rotatable around an axis, and the drive shaft will drive the first output shaft and the second output shaft through the transmission device to be able to Rotate in the same direction at the same or different speeds; The coupling transmission device includes a first planetary gear train and a second planetary gear train, the second planetary gear train is connected to the output shaft of the motor, receives the torque output by the output shaft of the motor, and outputs another torque , the first planetary gear train is connected to the second planetary gear train to receive the torque output by the second planetary gear train, the first planetary gear train is connected to the transmission device, and is the first The output shaft and the second output shaft provide torques in opposite directions; The first planetary gear train includes a third sun gear, a third planetary gear, a fourth planetary gear and a first ring gear, the third sun gear is fixed relative to the ground, the third sun gear and the third planetary gear, The fourth planetary gear meshes with the first ring gear in turn, the fourth planetary gear is rotatably connected to the second planetary carrier, and the third planetary wheel is rotatably connected to the third planetary carrier, so that the third planetary The revolution of the planetary wheels is output through the third planetary carrier. 2. The electric active spur gear differential possessing torque-oriented distribution function according to claim 1, wherein said transmission device comprises: a first sun gear coaxially fixedly connected to the first output shaft for common rotation with the first output shaft; a second sun gear coaxially fixedly connected to the second output shaft for common rotation with the second output shaft; a first planet gear meshing with the first sun gear; a second planet gear meshing with the second sun gear; a first planet carrier, which is rotatably connected to the first planet wheel; The second planetary carrier is also rotatably connected to the second planetary wheel, and the second planetary carrier is shared by the fourth planetary wheel and the second planetary wheel; a differential case, which is rotatably connected to the first planetary carrier and the second planetary carrier, and the drive shaft drives the differential case to rotate through a pair of meshed gears, so that the first planetary gear and the second planetary carrier The second planetary gears revolve around the first sun gear and the second sun gear respectively. 3. The electric active spur gear differential with torque directional distribution function according to claim 2, characterized in that, the second planetary gear train comprises a fourth sun gear, a fifth planetary gear, a second ring gear , the fourth sun gear is coaxially fixedly connected with the motor output shaft, so that the fourth sun gear and the motor output shaft rotate together, and the fifth planetary gear is respectively connected with the fourth sun gear and the motor output shaft. The second ring gear is meshed, the fifth planetary gear is rotatably connected with a fourth planetary carrier, so that the revolution of the fifth planetary wheel is output through the fourth planetary carrier, and the third planetary carrier and The fourth planet carrier is fixedly connected, and the first ring gear is fixedly connected to the second ring gear. 4 . The electric active spur gear differential with torque directional distribution function according to claim 3 , wherein the third planetary carrier and the fourth planetary carrier are integrally formed. 5 . The electric active spur gear differential with torque directional distribution function according to claim 3 , wherein the first ring gear and the second ring gear are integrally formed. 6. An automobile, characterized in that it comprises the electric active spur gear differential with torque directional distribution function according to any one of claims 1-5.