CN106838199B - An Electric Differential with Torque Orientation Distribution Function - Google Patents

Abstract

The invention discloses an electric differential with torque orientation distribution function, comprising: a main drive mechanism; a bevel gear differential; a TV control drive mechanism for outputting control power; a first single-row planetary gear train, The first sun gear is supported by bearings on the first semi-shaft, the first ring gear is fixedly connected coaxially with the first semi-shaft, the first planet carrier is connected to the control output end; the second single-row planetary gear train, the second planet carrier Fixed on the drive axle case, the second sun gear is fixedly connected with the first sun gear; the second sun gear is supported by bearings on the first half shaft; the third single-row planetary gear train, the third sun gear and the first half shaft Fixedly connected, the third planet carrier is fixedly connected to the second ring gear, and the third ring gear is fixedly connected to the differential case; wherein, the second single-row planetary gear train has the same characteristic parameters as the first single-row planetary gear train. The invention enables the driving torque of the automobile to be directional distributed to the wheels on the left and right sides according to the control requirements of the control logic.

Description

An Electric Differential with Torque Orientation Distribution Function

technical field

The invention belongs to the technical field of electric vehicle transmission, and in particular relates to an electric differential with torque orientation distribution function.

Background technique

Due to the energy crisis and the increasing emphasis on environmental protection, new energy vehicles are the reverse of the development of future vehicles, and electric vehicles have achieved rapid development worldwide. Compared with traditional internal combustion engine vehicles, electric vehicles are more economical and environmentally friendly, and the characteristics of nearly zero emissions make electric vehicles have significant advantages in environmental protection. At the same time, electric vehicles have better acceleration performance due to the characteristics of fast response of the drive motor, low speed and high torque, and the motor speed and torque are easy to obtain, which can control the electric vehicle more precisely. Therefore, electric vehicles have great potential for development.

Electric vehicles generally use a powertrain composed of a motor and a drive axle or a powertrain composed of a motor, a transmission and a drive axle to drive the vehicle. The electric vehicle driven by a wheel hub motor is not suitable due to the shortcomings of large unsprung mass and poor heat dissipation of the wheel hub motor. It has not been mass-produced, so most of the powertrains of existing electric vehicles contain drive axles.

The differential is an important part of the drive axle. Due to the principle of "differential speed and no torque" of the differential, the driving torque of the car can only be equally distributed on both sides of the left and right wheels, so that it cannot It makes good use of the ground adhesion, and even on the low adhesion side, it is easy to cause unstable conditions such as wheel slippage, and the adhesion ability of the driving wheel cannot be exerted. At the same time, because the load will be transferred from the inner wheel to the outer wheel when the vehicle turns at high speed, even if the ground adhesion is good, the adhesion of the outer wheel will be higher than that of the inner wheel. At this time, the traditional differential is equally divided. Torque to the inner and outer wheels may cause the inner wheel to reach the adhesion limit and slip, causing the car to become unstable. If part of the torque of the inner wheel is transferred to the outer wheel, the lateral force margin of the inner wheel can be increased to prevent the wheel from slipping, and an additional yaw moment can be generated for the whole vehicle, which can help push and guide The vehicle turns, which improves the turning maneuverability and extreme turning ability of the vehicle. At present, this technology is used in some high-end sports cars and high-end SUVs in the form of torque-oriented distribution differentials, such as Honda's super four-wheel drive system (SH-AWD) and Mitsubishi's super active yaw control system (SAYC ), etc. However, this technology is not widely used in electric vehicles.

Contents of the invention

The purpose of the present invention is to solve the defect that the left and right output torques of the differential are equal and cannot be adjusted, and provide an electric differential with a torque directional distribution function.

The technical scheme provided by the invention is:

An electric differential with torque directional distribution, comprising:

The main drive mechanism is arranged on one side of the differential, and its output end is connected to the differential case, which can transmit the rotational power to the differential case to drive the vehicle;

TV control driving mechanism, which is arranged on the other side of the differential, and is used to output torque distribution and control power;

The first single-row planetary gear train includes a first sun gear, a first planet gear, a first planet carrier, and a first ring gear, the first sun gear is rotatably supported on a first half shaft, and the first sun gear is rotatably supported on a first axle shaft. A ring gear is coaxially and fixedly connected to the first half shaft, and the first planet carrier is connected to the output end of the TV control drive mechanism;

The second single row planetary gear train includes a second sun gear, a second planetary gear, a second planet carrier and a second ring gear, the second planet carrier is fixed on the drive axle case, the second sun gear and the first The sun gear is fixedly connected; the second sun gear is rotatably supported on the first half shaft;

The third single-row planetary gear train includes a third sun gear, a third planet gear, a third planet carrier, and a third ring gear, the third sun gear is fixedly connected to the first half shaft, and the third planet carrier is connected to the first half shaft. The two ring gears are fixedly connected, and the third ring gear is fixedly connected to the differential case;

Wherein, the second single-row planetary gear train has the same characteristic parameters as the first single-row planetary gear train.

Preferably, the TV control drive mechanism includes a TV control motor and a TV deceleration mechanism.

Preferably, the TV control motor has a hollow output shaft, the first half shaft is rotatably supported on the hollow output shaft, and passes through the hollow output shaft.

Preferably, the TV deceleration mechanism includes:

The fourth single-row planetary gear train includes a fourth sun gear, a fourth planetary gear, a fourth planet carrier, and a fourth ring gear. The fourth sun gear is fixedly connected to the hollow output shaft, and the fourth ring gear is fixedly connected to the hollow output shaft. on the drive axle housing;

The fifth single-row planetary gear train includes a fifth sun gear, a fifth planetary gear, a fifth planet carrier, and a fifth ring gear, the fifth sun gear is fixedly connected to the fourth planet carrier, and the fifth ring gear It is fixed on the drive axle case, and the fifth planet carrier is connected with the first planet carrier as a control output end.

Preferably, the main drive mechanism includes a main drive motor and a main reduction mechanism.

Preferably, the main drive motor has a hollow output shaft, the second half shaft is rotatably supported on the hollow output shaft, and passes through the hollow output shaft.

Preferably, the main reduction mechanism includes:

The seventh single-row planetary gear train, which includes the seventh sun gear, the seventh planetary gear, the seventh planet carrier and the seventh ring gear, the seventh sun gear is fixedly connected to the output shaft of the main drive motor, and the seventh gear The ring is fixed on the drive axle housing;

The sixth single-row planetary gear train includes a sixth sun gear, a sixth planetary gear, a sixth planet carrier and a sixth ring gear, the sixth sun gear is fixedly connected to the seventh planet carrier, and the sixth ring gear It is fixed on the drive axle case, and the sixth planet carrier is fixedly connected with the differential case.

An electric differential with torque directional distribution, comprising:

The main drive mechanism is arranged on one side of the differential, and its output end is connected to the differential case, which can transmit the rotational power to the differential case to drive the vehicle;

TV control driving mechanism, which is arranged on the other side of the differential, and is used to output torque distribution and control power;

The first single-row double-stage planetary gear train includes a first sun gear, a first double-stage planetary gear, a first planet carrier, and a first ring gear, and the first sun gear is rotatably supported on a first axle shaft , the first ring gear is coaxially fixedly connected to the first half shaft, and the first planet carrier is connected to the output end of the TV control drive mechanism;

The second single-row double-stage planetary gear train includes a second sun gear, a second row of double-stage planetary gears, a second planet carrier and a second ring gear, the second planet carrier is fixed on the drive axle case, and the second The sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;

The third single-row planetary gear train includes a third sun gear, a third planet gear, a third planet carrier, and a third ring gear, the third sun gear is fixedly connected to the first half shaft, and the third planet carrier is connected to the first half shaft. The two ring gears are fixedly connected, and the third ring gear is fixedly connected to the differential case;

Wherein, the second single-row planetary gear train has the same characteristic parameters as the first single-row planetary gear train.

An electric differential with torque directional distribution, comprising:

The main drive mechanism is arranged on one side of the differential, and its output end is connected to the differential case, which can transmit the rotational power to the differential case to drive the vehicle;

TV control driving mechanism, which is arranged on the other side of the differential, and is used to output torque distribution and control power;

The first single-row planetary gear train includes a first sun gear, a first planet gear, a first planet carrier, and a first ring gear, the first sun gear is rotatably supported on a first half shaft, and the first sun gear is rotatably supported on a first axle shaft. A ring gear is coaxially and fixedly connected to the first half shaft, and the first planet carrier is connected to the output end of the TV control drive mechanism;

The second single row planetary gear train includes a second sun gear, a second planetary gear, a second planet carrier and a second ring gear, the second planet carrier is fixed on the drive axle case, the second sun gear and the first The sun gear is fixedly connected; the second sun gear is rotatably supported on the first half shaft;

The third single-row double-stage planetary gear train includes a third sun gear, a third double-stage planetary gear, a third planet carrier, and a third ring gear, the third sun gear is fixedly connected to the first half shaft, and the third The planet carrier is fixedly connected to the second ring gear, and the third ring gear is fixedly connected to the differential case;

Wherein, the second single-row planetary gear train has the same characteristic parameters as the first single-row planetary gear train.

An electric differential with torque directional distribution, comprising:

The main drive mechanism is arranged on one side of the differential, and its output end is connected to the differential case, which can transmit the rotational power to the differential case to drive the vehicle;

TV control driving mechanism, which is arranged on the other side of the differential, and is used to output torque distribution and control power;

The first single-row double-stage planetary gear train includes a first sun gear, a first double-stage planetary gear, a first planet carrier, and a first ring gear, and the first sun gear is rotatably supported on a first axle shaft , the first ring gear is coaxially fixedly connected to the first half shaft, and the first planet carrier is connected to the output end of the TV control drive mechanism;

The second single-row double-stage planetary gear train includes a second sun gear, a second double-stage planetary gear, a second planet carrier, and a second ring gear. The second planet carrier is fixed on the drive axle case, and the second sun gear The wheel is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;

The third single-row double-stage planetary gear train includes a third sun gear, a third double-stage planetary gear, a third planet carrier, and a third ring gear, the third sun gear is fixedly connected to the first half shaft, and the third The planet carrier is fixedly connected to the second ring gear, and the third ring gear is fixedly connected to the differential case;

Wherein, the second single-row planetary gear train has the same characteristic parameters as the first single-row planetary gear train.

The beneficial effects of the present invention are reflected in the following aspects:

1. The electric differential with torque-oriented distribution function provided by the present invention solves the disadvantage of "differential speed is not bad" of the differential in the traditional drive axle, so that the driving torque of the car can be controlled according to the control logic The demand-oriented distribution to the left and right wheels realizes the function of unequal distribution of left and right wheel torque without changing the total longitudinal driving torque, which improves the turning maneuverability and driving pleasure of the vehicle.

2. In the electric differential with torque-oriented distribution function provided by the present invention, the TV control motor and the main drive motor are coaxially arranged, so that the structure is more compact and the layout space is reduced.

3. The electric differential with torque-oriented distribution function provided by the present invention belongs to the sprung mass, so it does not significantly increase the unsprung mass like the hub motor, and has little influence on the ride comfort of the car.

Description of drawings

Fig. 1 is a structural schematic diagram of Embodiment 1 of an electric differential with torque directional distribution function according to the present invention.

Fig. 2 is a structural schematic diagram of Embodiment 2 of the electric differential with torque directional distribution function according to the present invention.

Fig. 3 is a structural schematic diagram of Embodiment 3 of the electric differential with torque directional distribution function according to the present invention.

Fig. 4 is a structural schematic diagram of Embodiment 4 of the electric differential with torque directional distribution function according to the present invention.

Fig. 5 is a schematic diagram of the torque flow of the electric differential with torque directional distribution function according to the present invention when the car is running straight.

Fig. 6 is a schematic diagram of the torque flow of the electric differential with the torque directional distribution function according to the present invention when the car is turning normally.

Fig. 7 is a schematic diagram of the torque flow of the electric differential with torque directional distribution function according to the present invention when the car turns left and the torque directional distributor is working.

Fig. 8 is a schematic diagram of the torque flow of the electric differential with torque directional distribution function according to the present invention when the vehicle turns right and the torque directional distributor is working.

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.

Embodiment one

As shown in Figure 1, the present invention provides an electric differential with torque distribution function, which mainly consists of a torque directional distributor 2000, a traditional bevel gear differential 1400, a main drive motor reduction mechanism 1500 and a main drive The motor 1002 constitutes.

In this embodiment, the torque directional distributor 2000 is located on the left side of the driving axle (it can also be exchanged with the main driving motor 1002, and it is arranged on the right side of the driving axle), and the TV control motor 1001 and the TV reduction mechanism are mainly used. 1100, double planetary row TV coupling mechanism 1200 and single planetary row differential coupling mechanism 1300 constitute.

The TV control motor 1001 is a hollow shaft inner rotor motor, the first half shaft 1402 connected to the left wheel passes through the inner hole of the hollow rotor shaft, the hollow shaft inner rotor and the sun gear of the fourth planetary gear train 1010 1014 is splined to input the output torque of the TV control motor 1001 to the fourth planetary gear train 1010 . The TV control motor 1001 is supported on the first axle shaft 1402 through bearings, and its stator and its housing are fixed with the drive axle housing.

The TV reduction mechanism 1100 mainly includes a fourth planetary gear train 1010 and a fifth planetary gear train 1020 . The fourth planetary gear train 1010 includes a sun gear 1014, three planetary gears 1012 uniformly distributed around the circumference, a planetary carrier 1013 and an inner ring gear 1011 fixed on the drive axle housing. The sun gear 1014 is spline connected with the hollow shaft inner rotor of the TV control motor 1001 , and the planet carrier 1013 is integrated with the sun gear 1024 of the fifth planetary gear train 1020 . The fifth planetary gear train 1020 includes a sun gear 1024, three planetary gears 1022 uniformly distributed around the circumference, a planetary carrier 1023 and an inner ring gear 1021 fixed on the drive axle housing. The sun gear 1024 is supported on the first axle shaft 1402 through bearings, and the planet carrier 1023 is integrated with the planet carrier 1033 of the first planetary gear train 1030 .

Preferably, the TV deceleration mechanism 1100 can be composed of a single-row planetary gear train, a multi-row planetary gear train or other forms of deceleration mechanisms, so changing the form of the deceleration mechanism 1100 is not regarded as an innovation to the present invention.

The double planetary row TV coupling mechanism 1200 mainly includes a first planetary gear train 1030 and a second planetary gear train 1040 , and their planetary row characteristic parameters must be the same, and the planetary row types must be consistent. The first planetary gear train 1030 includes a sun gear 1034 , three planetary gears 1032 uniformly distributed around the circumference, a planet carrier 1033 and an inner ring gear 1031 . Wherein the planetary carrier 1033 is integrated with the planetary carrier 1023 of the fifth planetary gear train 1020, the ring gear 1031 is spline connected with the first half shaft 1402, the sun gear 1034 is integrated with the sun gear 1044 of the second planetary gear train 1040, and Supported by bearings on the first half shaft. The second planetary gear train 1040 includes a sun gear 1044 , three planetary gears 1042 uniformly distributed around the circumference, a planet carrier 1043 and an inner ring gear 1041 . The planetary carrier 1043 is fixed on the drive axle housing, the sun gear 1044 and the first sun gear 1034 are integrated, and are supported on the first axle shaft 1402 through bearings, the inner ring gear 1041 and the planetary carrier 1053 of the third planetary gear train 1050 as one.

The single planetary differential coupling mechanism 1300 is mainly composed of the third planetary gear train 1050 . The third planetary gear train 1050 includes a sun gear 1054 , three planetary gears 1052 uniformly distributed around the circumference, a planet carrier 1053 , and an inner ring gear 1051 integrated with the differential case 1401 . The sun gear 1054 is splined to the first half shaft 1402 , and the planet carrier 1053 is integrated with the ring gear 1041 of the second planetary gear train 1040 .

The traditional bevel gear differential 1400 is mainly composed of a differential case 1401, a first half shaft 1402, a second half shaft 1403, a first side gear 1404, a second side gear 1405, two conical planetary gears 1406 and 1407, the planetary gear shaft 1408 constitutes. The first side gear 1404 is splined to the first side shaft 1402 , the second side gear 1405 is splined to the second side shaft 1403 , and the differential case 1401 is supported on the second side shaft 1403 through bearings.

The main driving motor reduction mechanism 1500 is located on the right side of the drive axle, and is mainly composed of a sixth planetary gear train 1060 and a seventh planetary gear train 1070 . The sixth planetary gear train 1060 includes a sun gear 1064, three planetary gears 1062 uniformly distributed around the circumference, a planet carrier 1063 and an inner ring gear 1061 fixed on the drive axle housing. The planet carrier 1063 is integrated with the differential case 1401 , the sun gear 1064 is integrated with the planet carrier 1073 of the seventh planetary gear train 1070 , and the sun gear 1064 is supported on the second half shaft 1403 through bearings. The seventh planetary gear train 1070 includes a sun gear 1074, three planetary gears 1072 uniformly distributed around the circumference, a planet carrier 1073 and an inner ring gear 1071 fixed on the drive axle housing. Wherein the sun gear 1074 is spline connected with the hollow inner rotor shaft of the main driving motor 1002 .

Preferably, the main drive motor reduction mechanism 1500 can be composed of a single-row planetary gear train, a multi-row planetary gear train or other forms of reduction mechanisms, so changing the form of the main drive motor reduction mechanism 1500 is not considered an innovation of the present invention.

The main drive motor 1002 is located on the right side of the drive axle, and it is a hollow shaft inner rotor motor, and the second half shaft 1403 connected to the right wheel passes through the inner hole of the hollow rotor shaft. The hollow-shaft inner rotor is spline-connected to the sun gear 1074 of the seventh planetary gear train 1070, and the main drive motor 1002 can input the driving torque into the main drive motor reduction mechanism 1500 through the sun gear 1074, and then act on the differential case 1401 , and finally equally divided into the first semi-axis 1402 and the second semi-axis 1403 . The main drive motor 1002 is supported on the second half-shaft 1403 through bearings, and its stator and its housing are fixed with the driving axle housing.

Embodiment two

As shown in Figure 2, in this embodiment, the first planetary gear train 1030 and the second planetary gear train 1040 in the double planetary row TV coupling mechanism 1200 are both single planetary gear planetary row, and the single planetary row differential coupling mechanism 1300 The third planetary gear train 1050 is a double-stage planetary gear planetary row, and the structure diagram is as shown in the figure.

Embodiment three

As shown in Figure 3, in this embodiment, the first planetary gear train 1030 and the second planetary gear train 1040 in the double planetary row TV coupling mechanism 1200 are both double-stage planetary gear planetary rows, and the single planetary row differential coupling mechanism The third planetary gear train 1050 in 1300 is a single planetary gear planetary row, as shown in the figure.

Embodiment four,

As shown in Figure 4, in this embodiment, the first planetary gear train 1030 and the second planetary gear train 1040 in the double planetary row TV coupling mechanism 1200 are both double-stage planetary gear planetary rows, and the single planetary row differential coupling mechanism The third planetary gear train 1050 in 1300 is a double-stage planetary gear planetary row, and its structure diagram is shown in the figure.

The schemes shown in Fig. 1 to Fig. 4 are all realizable embodiment structural schemes of the electric differential with torque directional distribution function according to the present invention, but considering the system inertia loss and operating efficiency, the scheme shown in Fig. 1 The embodiment scheme shown is the best preferred scheme, followed by the scheme shown in Figure 3, and again the scheme shown in Figure 2 and Figure 4.

The working principle of the electric differential with torque directional distribution function according to the present invention is as follows:

Taking the simplified structure diagram of an embodiment of an electric differential with torque directional distribution function shown in FIG. 1 as an example, the working principle is described.

When the car is running straight, the driving torque of the wheels on the left and right sides is the same, and there is no need for torque distribution. Therefore, there is no control electric signal in the TV control motor 1001, and the TV control motor does not start. The car is only driven by the main drive motor 1002, and the main drive motor 1002 The output torque acts on the differential case 1401 through the torque increase of the main drive motor reduction mechanism 1500. Due to the principle of equal torque division of the traditional bevel gear differential mechanism 1400, the torque acting on the differential case 1401 is equally divided into the first On the half shaft 1402 and the second half shaft 1403, the vehicle is driven to run. If the rotation direction of the wheel is set as the positive direction when the car is driven, otherwise it is the negative direction. At this time, the rotation speeds of the differential case 1401, the first half shaft 1402 and the second half shaft 1403 are the same, and the planetary gear 1052 of the third planetary gear train 1050 only revolves with the differential case 1401 but does not rotate. Therefore, the planetary The frame 1053 and the sun gear 1054 rotate at the same speed. Since the ring gear 1031 of the first planetary gear train 1030 has the same rotation speed as the sun gear 1054 of the third planetary gear train 1050, the ring gear 1041 of the second planetary gear train 1040 and the planet carrier of the third planetary gear train 1050 1053 is integrated, so the ring gear 1031 in the first planetary gear train 1030 and the ring gear 1041 in the second planetary gear train 1040 rotate at the same speed. Because the first planetary gear system 1030 and the second planetary gear system 1040 share the same sun gear, the speed of the two ring gears is also the same, so the speed of the planet carrier 1033 and the speed of the planet carrier 1043 are also the same, the planet carrier 1043 is fixed, and the speed is 0 , so the rotational speed of the planet carrier 1033 is also 0. Since the TV deceleration mechanism 1100 only changes the output torque of the TV control motor 1001, and does not change the positive and negative directions of the output torque, therefore, when the car is going straight, the inner rotor speed of the TV control motor 1001 is also 0, and the TV control motor does not start, Without torque output, the vehicle is only driven by the main drive motor 1002, and the torque distribution flow is shown in FIG. 5 .

When the car is turning at a normal differential speed, the driving torque of the wheels on the left and right sides is the same, and no torque distribution is required. Therefore, there is no control electric signal in the TV control motor 1001, and the TV control motor does not start. The car is only driven by the main drive motor 1002, and the main drive The torque output by the motor 1002 acts on the differential case 1401 through the torque increase of the main drive motor reduction mechanism 1500. Due to the principle of equal torque division of the traditional bevel gear differential mechanism 1400, the torque acting on the differential case 1401 is equally divided. to the first half shaft 1402 and the second half shaft 1403 to drive the car.

Taking the car turning left at a normal differential speed as an example, if the rotation direction of the wheels is set to be positive when the car is driving, and negative if it is not. Then, for the single planetary row differential coupling mechanism 1050, the single planetary wheel planetary row speed formula is obtained:

n _S5 +k ₅ n _R5 -(k ₅ +1)n _PC5 ＝0

In the formula, n _S5 is the rotation speed of the third planetary gear system 1050 sun gear 1054, n _R5 is the rotation speed of the third planetary gear system 1051 ring gear, n _PC5 is the rotation speed of the third planetary gear system 1053 planet carrier, k ₅ is the third planetary gear The characteristic parameters of the planetary arrangement of the system. Since the car turns left, the rotational speed of the differential case 1401 is greater than the rotational speed of the first half shaft 1402, so:

n _S5 <n _R5

so:

n _S5 < n _PC5

That is, the rotation speed of the sun gear 1054 in the third planetary gear system 1050 is smaller than that of the planet carrier 1053, so for the double planetary row TV coupling mechanism 1200, the rotation speed of the ring gear 1031 in the first planetary gear system 1030 is smaller than that of the second planetary gear system 1041 speeds of ring gear in 1040. And because the first planetary gear train 1030 and the second planetary gear train 1040 have a common sun gear, so the double planetary row TV coupling mechanism 1200 has:

kn _R3 -(k+1)n _PC3 ＝kn _R4 -(k+1)n _PC4

In the formula, n _PC3 is the rotation speed of the first planetary gear system 1030 and the planet carrier 1033, n _R3 is the rotation speed of the first planetary gear system 1030 and the inner ring gear 1031, n _PC4 is the rotation speed of the second planetary gear system 1040 and the planet carrier 1043, and n _R4 is the second The rotational speed of the ring gear 1041 of the planetary gear set 1040 , k is the characteristic parameter of the planetary row of the first planetary gear set 1030 and the second planetary gear set 1040 . also because:

n _R3 <n _R4 , and n _PC4 =0

so:

n _PC3 <0

That is, the rotation speed of the planet carrier 1033 of the first planetary gear train 1030 is negative, so the rotation speed of the inner rotor of the TV control motor 1001 is also negative. Therefore, when the vehicle turns left at a normal differential speed, the TV control motor 1001 has no electric signal input and no torque output, and the hollow-shaft inner rotor of the TV control motor is dragged by the torque distributor 2000 to rotate in a negative direction. The torque distribution flow is shown in Fig. 6.

In the same way, when the vehicle turns right at a normal differential speed, the TV control motor 1001 has no electric signal input and no torque output, and the hollow-shaft inner rotor of the TV control motor is dragged by the torque distributor 2000 to rotate in the positive direction. The torque distribution flow is also shown in FIG. 6 .

则TV控制电机1001输入进单行星排差速器耦合机构1300中的行星架1053的力矩为

所以第三行星轮系1050中的太阳轮1054输入第一半轴1402的力矩为

内齿圈1051输入进差速器壳1401的力矩为

由差速器壳1401等分至第一半轴1402和第二半轴1403的力矩为

所以最终由控制电机1001输入第一半轴1402的力矩是由第一行星轮系1030中内齿圈1031输入第一半轴1402的力矩、第三行星轮系1050中太阳轮1054输入第一半轴1402的力矩、差速器壳1401等分至第一半轴1402的力矩三部分之和构成，其结果为为

由TV控制电机1001最终输入第二半轴1403的力矩为

如上可以看出，由TV控制电机1001输入进第一半轴1402和第二半轴1403的力矩等大反向，因此不改变总的纵向驱动转矩，且与第一半轴1402相连的左侧车轮转矩减少，与第二半轴1403相连的右侧车轮转矩增加，可以产生一个有助于左转的横摆力矩，提高了汽车的左转弯机动性。需要说明的是，此时TV控制电机1001的转速与正常差速左转时相同。此时的转矩分配流如图7所示。需要说明的是，若TV控制电机在此时输出正向转矩，则驱动转矩将定向的由右侧车轮分配到左侧车轮，将产生一个防止车辆过度转向的横摆力矩，用于保持汽车稳定性。When the car is cornering at medium and high speeds, it is necessary to distribute the torque direction of the inner wheel to the outer wheel to improve cornering maneuverability. If the rotation direction of the wheel is set as the positive direction when the car is driving, and vice versa, take the car turning left as an example for analysis. At this time, the motor controller controls the TV to control the motor 1001 to output torque -T ₀ (T ₀ is a positive value). After the torque is decelerated and increased by the TV reduction mechanism 1100, it is input to the planet carrier 1033 in the double planetary row TV coupling mechanism 1200. The torque is -iT ₀ , where i is the transmission ratio of the TV reduction mechanism 1100 . Therefore, the torque input to the first half shaft 1402 by the ring gear 1031 in the first planetary gear train 1030 is

Then the torque of the planet carrier 1053 input into the single planetary differential coupling mechanism 1300 by the TV control motor 1001 is

Therefore, the torque of the sun gear 1054 in the third planetary gear train 1050 input to the first half shaft 1402 is

The moment that the ring gear 1051 inputs into the differential case 1401 is

The moment equally divided by the differential case 1401 to the first half shaft 1402 and the second half shaft 1403 is

Therefore, the final torque input by the control motor 1001 to the first half shaft 1402 is the torque input to the first half shaft 1402 by the ring gear 1031 in the first planetary gear train 1030, and the torque input to the first half shaft by the sun gear 1054 in the third planetary gear train 1050 The moment of the shaft 1402, the sum of the three parts of the moment of the differential case 1401 equally divided to the first half shaft 1402, the result is

The torque that is finally input to the second half shaft 1403 by the TV control motor 1001 is

As can be seen above, the torque input into the first half shaft 1402 and the second half shaft 1403 by the TV control motor 1001 is equal and reversed, so the total longitudinal driving torque does not change, and the left side connected to the first half shaft 1402 The torque of the side wheels is reduced, and the torque of the right wheel connected to the second half shaft 1403 is increased, which can generate a yaw moment that is helpful for turning left, and improves the maneuverability of the car when turning left. It should be noted that the rotation speed of the TV control motor 1001 at this time is the same as that of the normal differential left rotation. The torque distribution flow at this time is shown in FIG. 7 . It should be noted that if the TV control motor outputs positive torque at this time, the driving torque will be directional distributed from the right wheel to the left wheel, and a yaw moment will be generated to prevent the vehicle from oversteering, which is used to maintain car stability.

In the same way, when the car turns right at medium and high speed, the motor controller controls the TV to control the motor 1001 to output positive torque, which can generate a yaw that is helpful to the right turn without changing the total longitudinal drive torque torque, improving the right-turn maneuverability of the car. It should be noted that the rotation speed of the TV control motor 1001 at this time is the same as that of normal differential right rotation. The torque distribution flow at this time is shown in FIG. 8 . It should be noted that if the TV control motor outputs negative torque at this time, the driving torque will be directional distributed from the left wheel to the right wheel, and a yaw moment will be generated to prevent the vehicle from oversteering, which is used to maintain car stability.

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 (10)

1. An electric differential with torque directional distribution, comprising:

the main driving mechanism is arranged on one side of the differential mechanism, the output end of the main driving mechanism is connected with the differential mechanism shell, the main driving mechanism can transmit the rotary power to the differential mechanism shell, and the rotary power is transmitted to the first half shaft and the second half shaft of the differential mechanism after being equally divided to drive the vehicle to run;

a TV control drive mechanism provided on the other side of the differential for outputting torque distribution control power;

the first single-row planetary gear train comprises a first sun gear, a first planetary gear, a first planet carrier and a first gear ring, wherein the first sun gear is rotatably supported on a first half shaft, the first gear ring is coaxially and fixedly connected with the first half shaft, and the first planet carrier is connected with the output end of the TV control driving mechanism;

the second single-row planetary gear train comprises a second sun gear, a second planet carrier and a second gear ring, the second planet carrier is fixed on the drive axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;

the third single-row planetary gear train comprises a third sun gear, a third planetary gear, a third planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the first half shaft, the third planet carrier is fixedly connected with the second gear ring, and the third gear ring is fixedly connected with the differential shell;

wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters.

2. The electric differential with torque vectoring function as claimed in claim 1, wherein said TV control drive mechanism comprises a TV control motor and a TV speed reduction mechanism.

3. An electric differential with torque directional distribution as set forth in claim 2 wherein said TV control motor has a hollow output shaft, said first half shaft being rotatably supported on and extending out of said hollow output shaft.

4. The electric differential with torque vectoring function as claimed in claim 2, wherein said TV speed reduction mechanism comprises:

the fourth single-row planetary gear train comprises a fourth sun gear, a fourth planetary gear, a fourth planet carrier and a fourth gear ring, the fourth sun gear is fixedly connected with the hollow output shaft, and the fourth gear ring is fixed on the drive axle housing;

and the fifth single-row planetary gear train comprises a fifth sun gear, a fifth planetary gear, a fifth planet carrier and a fifth gear ring, the fifth sun gear is fixedly connected with the fourth planet carrier, the fifth gear ring is fixed on the driving axle housing, and the fifth planet carrier is connected with the first planet carrier as a control output end.

5. An electric differential with torque vectoring function as claimed in claim 1, wherein said primary drive mechanism comprises a primary drive motor and a primary reduction mechanism.

6. An electric differential with torque directional distribution as set forth in claim 5 wherein said primary drive motor has a hollow output shaft with a second axle shaft rotatably supported thereon and extending therefrom.

7. The electric differential with torque directional distribution function according to claim 5, characterized in that the final drive mechanism includes:

the seventh single-row planetary gear train comprises a seventh sun gear, a seventh planet carrier and a seventh gear ring, the seventh sun gear is fixedly connected with the output shaft of the main driving motor, and the seventh gear ring is fixed on the driving axle housing;

a sixth single-row planetary gear train comprising a sixth sun gear, a sixth planet carrier and a sixth ring gear, the sixth sun gear being fixedly connected with the seventh planet carrier, the sixth ring gear being fixed on the drive axle housing, the sixth planet carrier being fixedly connected with the differential housing.

8. An electric differential with torque directional distribution, comprising:

the main driving mechanism is arranged on one side of the differential mechanism, the output end of the main driving mechanism is connected with the differential mechanism shell, and the main driving mechanism can transmit the rotary power to the differential mechanism shell to drive the vehicle to run;

a TV control drive mechanism provided on the other side of the differential for outputting torque distribution control power;

the first single-row double-stage planetary gear train comprises a first sun gear, a first double-stage planetary gear, a first planet carrier and a first gear ring, wherein the first sun gear is rotatably supported on a first half shaft, the first gear ring is coaxially and fixedly connected with the first half shaft, and the first planet carrier is connected with the output end of the TV control driving mechanism;

the second single-row double-stage planetary gear train comprises a second sun gear, a second double-stage planetary gear, a second planet carrier and a second gear ring, the second planet carrier is fixed on the driving axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;

the third single-row planetary gear train comprises a third sun gear, a third planetary gear, a third planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the first half shaft, the third planet carrier is fixedly connected with the second gear ring, and the third gear ring is fixedly connected with the differential shell;

the second single-row double-stage planetary gear train and the first single-row double-stage planetary gear train have the same characteristic parameters.

9. An electric differential with torque directional distribution, comprising:

a main driving mechanism which is arranged at one side of the differential mechanism, the output end of the main driving mechanism is connected with the differential mechanism shell, and the main driving mechanism can transmit the rotary power to the differential mechanism shell to drive the vehicle to run;

a TV control drive mechanism provided on the other side of the differential for outputting torque distribution control power;

the first single-row planetary gear train comprises a first sun gear, a first planetary gear, a first planet carrier and a first gear ring, wherein the first sun gear is rotatably supported on a first half shaft, the first gear ring is coaxially and fixedly connected with the first half shaft, and the first planet carrier is connected with the output end of the TV control driving mechanism;

the second single-row planetary gear train comprises a second sun gear, a second planet carrier and a second gear ring, the second planet carrier is fixed on the drive axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;

the third single-row double-stage planetary gear train comprises a third sun gear, a third double-stage planetary gear, a third planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the first half shaft, the third planet carrier is fixedly connected with the second inner gear ring, and the third gear ring is fixedly connected with the differential shell;

wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters.

10. An electric differential with torque directional distribution, comprising:

the main driving mechanism is arranged on one side of the differential mechanism, the output end of the main driving mechanism is connected with the differential mechanism shell, and the main driving mechanism can transmit the rotary power to the differential mechanism shell to drive the vehicle to run;

a TV control drive mechanism provided on the other side of the differential for outputting torque distribution control power;

the first single-row double-stage planetary gear train comprises a first sun gear, a first double-stage planetary gear, a first planet carrier and a first gear ring, wherein the first sun gear is rotatably supported on a first half shaft, the first gear ring is coaxially and fixedly connected with the first half shaft, and the first planet carrier is connected with the output end of the TV control driving mechanism;

the second single-row double-stage planetary gear train comprises a second sun gear, a second double-stage planetary gear, a second planet carrier and a second gear ring, wherein the second planet carrier is fixed on the drive axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;

the third single-row double-stage planetary gear train comprises a third sun gear, a third double-stage planetary gear, a third planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the first half shaft, the third planet carrier is fixedly connected with the second inner gear ring, and the third gear ring is fixedly connected with the differential shell;

the second single-row double-stage planetary gear train and the first single-row double-stage planetary gear train have the same characteristic parameters.

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