CN107035847B - Electric differential mechanism with torque directional distribution function - Google Patents
Electric differential mechanism with torque directional distribution function Download PDFInfo
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- CN107035847B CN107035847B CN201710265582.XA CN201710265582A CN107035847B CN 107035847 B CN107035847 B CN 107035847B CN 201710265582 A CN201710265582 A CN 201710265582A CN 107035847 B CN107035847 B CN 107035847B
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/38—Constructional details
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Abstract
The invention discloses an electric differential mechanism with a torque directional distribution function, which comprises: a main drive mechanism; a bevel gear differential; a TV control driving mechanism for outputting control power; the first single-row planetary gear train is characterized in that a first sun gear is coaxially and fixedly connected with a first half shaft, and a first gear ring is connected with the control output end; the second single-row planetary gear train is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; the second sun gear is supported on the first half shaft through a bearing; a third single-row planetary gear train, a third sun gear is fixedly connected with the differential case, a third planet carrier is in splined connection with the first half shaft, and a third gear ring is fixedly connected with the second sun gear; wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters. The invention can distribute the driving torque of the automobile to the left and right wheels according to the control requirement of the control logic.
Description
Technical Field
The invention belongs to the technical field of electric automobile transmission, and particularly relates to an electric differential with a torque directional distribution function.
Background
Due to the energy crisis and the increasing importance of environmental protection, new energy automobiles are the development direction of future automobiles, and electric automobiles are rapidly developed in the world. Compared with the traditional internal combustion engine automobile, the electric automobile has better economy and environmental protection, and has the obvious advantage in the aspect of environmental protection due to the characteristic of nearly zero emission. Meanwhile, the electric automobile has better acceleration performance due to the characteristics of quick response, low speed, large torque and the like of the driving motor, the rotating speed and the torque of the motor are easy to obtain, and the electric automobile can be controlled more accurately. Therefore, the electric automobile has great development potential.
The electric automobile generally adopts a power assembly consisting of a motor and a drive axle or a power assembly consisting of the motor, a transmission and the drive axle to drive the automobile to run, and the electric automobile driven by the hub motor is not mass-produced due to the defects of large unsprung mass, poor heat dissipation of the hub motor and the like, so the drive axle is mostly contained in the power assembly of the existing electric automobile.
The differential is an important part in a drive axle, and due to the principle of differential and no differential torque of the differential, the driving torque of an automobile can only be equally distributed on the two sides of the left wheel and the right wheel, so that the ground adhesion force cannot be well utilized under the condition of uneven road surface adhesion, even unstable working conditions such as wheel slip and the like are easily caused on the side with low adhesion, and the adhesion capability of the driving wheels cannot be exerted. Meanwhile, when the vehicle turns at a high speed, the load is transferred from the inner wheel to the outer wheel, so that the adhesion capability of the outer wheel is higher than that of the inner wheel even under the condition of good ground adhesion, and at the moment, when the torque is equally distributed to the inner wheel and the outer wheel by the traditional differential, the inner wheel reaches the adhesion limit to generate slip, so that the vehicle is unstable. If part of the torque at the inner wheels is transferred to the outer wheels, the lateral force margin at the inner wheels can be increased, preventing the wheels from slipping, and an additional yaw moment can be generated for the entire vehicle, which can help to propel and steer the vehicle, improving vehicle cornering mobility and ultimate cornering ability. At present, the technology is applied to some high-end sports cars and high-end SUVs in the form of a torque directional distribution differential, such as the super four-wheel drive system (SH-AWD) of honda and the super active yaw control System (SAYC) of mitsubishi, etc., but the technology is not applied to electric vehicles too much.
Disclosure of Invention
The invention aims to solve the defect that the left and right output torques of a differential are equal and cannot be adjusted, and provides an electric differential with a torque directional distribution function.
The technical scheme provided by the invention is as follows:
an electric differential with torque directional distribution functionality, 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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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, wherein the second gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential case, the third planet carrier is in spline connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters.
Preferably, the TV control drive mechanism includes a TV control motor and a TV speed reduction mechanism.
Preferably, the TV control motor has a hollow output shaft, and the first half shaft is rotatably supported on and protrudes from the hollow output shaft.
Preferably, the TV deceleration mechanism includes:
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 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 gear ring as a control output end.
Preferably, the main drive mechanism includes a main drive motor and a main speed reduction mechanism.
Preferably, the main drive motor has a hollow output shaft, and the second axle shaft is rotatably supported on and extends out of the hollow output shaft.
Preferably, the main speed reducing 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.
An electric differential with torque directional distribution functionality, 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 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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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 planet double-stage planetary gear, a second planet carrier and a second gear ring, wherein the second gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential case, the third planet carrier is in spline connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters.
An electric differential with torque directional distribution functionality, 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 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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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, wherein the second gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential shell, the third planet carrier is in spline connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters.
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 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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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 gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential case, the third planet carrier is in splined connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters.
The beneficial effects of the invention are shown in the following aspects:
1. the electric differential with the torque directional distribution function provided by the invention overcomes the defect that the differential in the traditional drive axle is not differential and not torque-differential, so that the driving torque of an automobile can be directionally distributed to the left and right wheels according to the control requirement of control logic, the function of unequal distribution of the wheel torque of the left and right wheels is realized on the premise of not changing the longitudinal total driving torque, and the turning maneuverability and the driving pleasure of the automobile are improved.
2. According to the electric differential with the torque directional distribution function, the TV control motor and the main driving motor are coaxially arranged, the structure is more compact, and the arrangement space is reduced.
3. The electric differential with the torque directional distribution function belongs to sprung mass, so that unsprung mass cannot be obviously increased like a hub motor, and the influence on the smoothness of an automobile in running is small.
Drawings
FIG. 1 is a schematic structural diagram of an embodiment of an electric differential with torque directional distribution according to the present invention.
FIG. 2 is a schematic structural diagram of an embodiment of an electric differential with a torque directional distribution function according to the present invention.
FIG. 3 is a schematic diagram of an embodiment of an electric differential with torque directional distribution according to the present invention.
FIG. 4 is a schematic structural diagram of an electric differential with a torque directional distribution function according to the fourth embodiment of the present invention.
FIG. 5 is a schematic diagram of the torque flow direction of the electric differential with the torque directional distribution function in the straight running of the automobile.
FIG. 6 is a schematic diagram of the torque flow direction of the electric differential with the torque directional distribution function in normal turning of the automobile.
Fig. 7 is a schematic diagram of the torque flow direction of the electric differential with the torque directional distribution function in the invention when the automobile turns left and the torque directional distribution device works.
FIG. 8 is a schematic diagram of the torque flow direction of the electric differential with the torque directional distribution function when the automobile turns right and the torque directional distribution device works.
Detailed Description
The present invention is further described in detail below with reference to the attached drawings so that those skilled in the art can implement the invention by referring to the description text.
Example one
As shown in FIG. 1, the present invention provides an electric differential with torque distribution function, which mainly comprises a torque directional distributor 2000, a conventional bevel gear differential 1400, a main drive motor speed reducing mechanism 1500 and a main drive motor 1002.
In the present embodiment, the torque directional divider 2000 is located on the left side of the driving axle (which may be exchanged with the main driving motor 1002 and disposed on the right side of the driving axle), and mainly comprises a TV control motor 1001, a TV speed reduction mechanism 1100, a double-row TV coupling mechanism 1200, and a single-row differential coupling mechanism 1300.
The TV control motor 1001 is a hollow shaft type inner rotor motor, the first half shaft 1402 connected with the left wheel penetrates through an inner hole of the hollow rotor shaft, the hollow shaft type inner rotor is in spline connection with the sun gear 1014 of the fourth planetary gear train 1010, and the output torque of the TV control motor 1001 is input to the fourth planetary gear train 1010. The TV control motor 1001 is supported on a first axle shaft 1402 by bearings, the stator of which and its housing are fixed to the transaxle case.
The TV reduction gear 1100 mainly includes a fourth planetary gear train 1010 and a fifth planetary gear train 1020. The fourth planetary gear train 1010 comprises a sun gear 1014, three planetary gears 1012 uniformly distributed on the circumference, a planet carrier 1013 and an inner gear ring 1011 fixed on a drive axle housing. The sun gear 1014 is splined to a hollow shaft type inner rotor of the TV control motor 1001, and the carrier 1013 is integrated with the sun gear 1024 of the fifth planetary gear train 1020. The fifth planetary gear train 1020 comprises a sun gear 1024, three planetary gears 1022 uniformly distributed on the circumference, a planet carrier 1023 and a ring gear 1021 fixed on the drive axle housing. The sun gear 1024 is supported on the first half shaft 1402 by a bearing, and the planet carrier 1023 is integrated with the ring gear 1031 of the first planetary gear train 1030.
It is preferable that the TV reduction mechanism 1100 be constituted by a single row planetary gear train, a multiple row planetary gear train, or other form of reduction mechanism, and therefore the form of shifting the reduction mechanism 1100 is not regarded as an innovation of the present invention.
The double row TV coupling 1200 mainly comprises a first planetary gear train 1030 and a second planetary gear train 1040, which have to have the same row characteristic parameters and the same row type. The first planetary gear train 1030 includes a sun gear 1034, three planetary gears 1032 which are evenly distributed circumferentially, a planet carrier 1033, and a ring gear 1031. The ring gear 1031 is integrated with the planet carrier 1023 of the fifth planetary gear train 1020, the sun gear 1034 is connected with the first half shaft 1402 through a spline, and the planet carrier 1033 is integrated with the planet carrier 1043 of the second planetary gear train 1040. The second planetary gear train 1040 includes a sun gear 1044, three planetary gears 1042 uniformly distributed circumferentially, a planet carrier 1043, and an annulus gear 1041 fixed on a drive axle housing. The sun gear 1044 is integrated with the ring gear 1051 of the third planetary gear train 1050, and the sun gear 1044 is supported on the first half shaft 1402 through a bearing.
The single planetary row differential coupling mechanism 1300 is mainly composed of a third planetary gear train 1050. The third planetary gear train 1050 includes a sun gear 1054, three planetary gears 1052 circumferentially and uniformly distributed, a planet carrier 1053, and an inner gear ring 1051. The sun gear 1054 is fixedly connected with the differential case 1401, the planet carrier 1053 is connected with the first half shaft 1402 through a spline, and the ring gear 1051 is fixedly connected with the second sun gear 1044.
The conventional bevel gear differential 1400 is primarily made up of a differential case 1401, a first half shaft 1402, a second half shaft 1403, a first half shaft gear 1404, a second half shaft gear 1405, two conical planetary gears 1406 and 1407, and a pinion shaft 1408. Wherein a first side gear 1404 is splined to a first axle shaft 1402, a second side gear 1405 is splined to a second axle shaft 1403, and a differential case 1401 is supported on the second axle shaft 1403 by bearings.
The main drive motor speed reduction mechanism 1500 is located on the right side of the transaxle and mainly comprises 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 circumferentially, a planet carrier 1063, and an annulus gear 1061 fixed on the drive axle housing. In which a carrier 1063 is integrated with the differential case 1401, a sun gear 1064 is integrated with a carrier 1073 of the seventh planetary gear train 1070, and the sun gear 1064 is supported on the second half shaft 1403 by a bearing. The seventh row planetary gear train 1070 comprises a sun gear 1074, three planet gears 1072 uniformly distributed circumferentially, a planet carrier 1073, and an annular gear 1071 fixed on a drive axle housing. Wherein the sun gear 1074 is splined to the hollow inner rotor shaft of the main drive motor 1002.
It is preferable that the primary drive motor reduction mechanism 1500 may be constructed of a single row planetary gear train, a multiple row planetary gear train, or other form of reduction mechanism, and thus the conversion of the form of the primary 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 is a hollow shaft type inner rotor motor, and a second half shaft 1403 connected with the right wheel penetrates through an inner hole of the hollow rotor shaft. The hollow shaft type inner rotor is spline-connected to a sun gear 1074 of the seventh planetary gear train 1070, and the main drive motor 1002 can input drive torque into the main drive motor reduction mechanism 1500 through the sun gear 1074, and act on the differential case 1401, and finally equally divide the drive torque into the first half shaft 1402 and the second half shaft 1403. The main drive motor 1002 is supported on a second axle shaft 1403 via bearings, the stator of which and its housing are fixed to the drive axle housing.
Example two
As shown in fig. 2, in the present 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 rows, and the third planetary gear train 1050 in the single planetary row differential coupling mechanism 1300 is a double planetary row, and the schematic diagram is shown.
EXAMPLE III
In the present embodiment, as shown in fig. 3, 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 planetary gear rows, and the third planetary gear train 1050 in the single planetary row differential coupling mechanism 1300 is a single planetary gear row, and the schematic is shown.
In the fourth embodiment, the first step is that,
in the present embodiment, as shown in fig. 4, the first planetary gear train 1030 and the second planetary gear train 1040 in the double-row TV coupling mechanism 1200 are both double-stage planetary gear rows, and the third planetary gear train 1050 in the single-row differential coupling mechanism 1300 is a double-stage planetary gear row, and the schematic structure is shown in the figure.
The schemes shown in fig. 1 to 4 are all the practical embodiment structural schemes of the electric differential with the torque directional distribution function, but in consideration of the inertia loss and the running efficiency of the system, the scheme shown in fig. 1 is the best preferred scheme, and then the scheme shown in fig. 3, and again the scheme shown in fig. 2 and 4.
The working principle of the electric differential with the torque directional distribution function is as follows:
the operation principle will be described by taking the schematic structure of the embodiment of the electric differential with the torque directional distribution function shown in fig. 1 as an example.
When the automobile runs straight, the driving torque of the left wheel and the right wheel is the same, no torque distribution is needed, so that no control electric signal is generated in the TV control motor 1001, the TV control motor is not started, the automobile is driven only by the main drive motor 1002, the torque output by the main drive motor 1002 is added through the main drive motor speed reducing mechanism 1500 and acts on the differential shell 1401, and due to the principle of torque equal division of the traditional bevel gear differential mechanism 1400, the torque acting on the differential shell 1401 is equally distributed to the first half shaft 1402 and the second half shaft 1403, and the automobile is driven to run. If the rotating direction of the wheels is set to be a positive direction when the automobile is driven, and otherwise, the rotating direction is a negative direction. At this time, the rotational speeds of the differential case 1401, the first half shaft 1402, and the second half shaft 1403 are the same, and the planet gears 1052 of the third planetary gear train 1050 rotate only with the differential case 1401 without rotating on its own axis, so the carrier 1053 and the ring gear 1051 rotate at the same speed. Since the rotational speeds of the sun gear 1034 of the first planetary gear train 1030 and the carrier 1053 of the third planetary gear train 1050 are the same, and the sun gear 1044 of the second planetary gear train 1040 and the ring gear 1051 of the third planetary gear train 1050 are integrated, the sun gear 1034 of the first planetary gear train 1030 and the sun gear 1044 of the second planetary gear train 1040 rotate at a constant speed. Since first planetary gear train 1030 and second planetary gear train 1040 share a carrier and the rotational speeds of both sun gears are also the same, the rotational speed of ring gear 1031 is also the same as the rotational speed of ring gear 1041, ring gear 1041 is fixed and the rotational speed is 0, so the rotational speed of ring gear 1031 is also 0. Since the TV reduction gear 1100 changes only the magnitude of the torque output from the TV control motor 1001 and does not change the positive or negative direction of the output torque, when the automobile is running straight, the rotation speed of the inner rotor of the TV control motor 1001 is also 0, the TV control motor is not started and does not output torque, the automobile is driven only by the main drive motor 1002, and the torque distribution flow is as shown in fig. 5.
When the automobile normally performs differential turning, the driving torque of the left wheel and the right wheel is the same, and no torque distribution is needed, so that no control electric signal is generated in the TV control motor 1001, the TV control motor is not started, the automobile is driven only by the main drive motor 1002, the torque output by the main drive motor 1002 is added through the torque of the speed reducing mechanism 1500 of the main drive motor and acts on the differential shell 1401, and due to the principle of torque equal division of the traditional bevel gear differential mechanism 1400, the torque acting on the differential shell 1401 is equally distributed to the first half shaft 1402 and the second half shaft 1403, and the automobile is driven to run.
Taking the example of the normal differential left-turn of the automobile, if the rotation direction of the wheels is set to be a positive direction when the automobile is driven, and vice versa, the rotation direction is a negative direction. Then the single planet row differential coupling 1050 is given by the single planet row speed formula:
n S5 +k 5 n R5 -(k 5 +1)n PC5 ＝0
in the formula n S5 For the third planetary gear train 1050 sun gear 1054 speed, n R5 Inner gear speed n of a third planetary gear train 1051 PC5 For the third planetary gear 1053 planet carrier speed, k 5 Is the characteristic parameter of the planet row of the third planet gear train. Since the vehicle is turning left, the differential case 1401 rotates at a speed greater than the first half shaft 1402, so that:
n S5 ＞n PC5
therefore:
n R5 ＜n PC5
i.e. the ring gear 1051 in the third planetary gear train 1050, is rotating at a speed less than that of the carrier 1053, the sun gear 1034 in the first planetary gear train 1030 is rotating at a speed greater than the sun gear 1044 in the second planetary gear train 1040 for the double row TV coupling 1200. Since the first planetary gear train 1030 shares a carrier with the second planetary gear train 1040, the double planetary TV coupling mechanism 1200 has:
n S3 +kn R3 ＝n S4 +kn R4
in the formula n S3 For the first planetary gear train 1030 sun gear 1034 rotational speed, n R3 For the first planetary gear train 1030 the speed of the ring gear 1031, n S4 The rotational speed of the sun gear 1044 of the second planetary gear train 1040, n R4 Is the rotational speed of the ring gear 1041 of the second planetary gear train 1040, k is the characteristic parameter of the planetary gear trains of the first planetary gear train 1030 and the second planetary gear train 1040. And because:
n S3 ＞n S4 and n is R4 ＝0
Therefore:
n R3 ＜0
that is, the rotational speed of ring gear 1031 of first planetary gear train 1030 is negative, and therefore the rotational speed of the inner rotor of TV control motor 1001 is also negative. Therefore, when the vehicle normally performs a differential left turn, the TV control motor 1001 has no electric signal input and no torque output, and the hollow shaft type inner rotor of the TV control motor is dragged by the torque divider 2000 to rotate in a negative direction. The torque split flow is shown in fig. 6.
In the same way, when the automobile normally rotates in the right direction at a differential speed, the TV control motor 1001 has no electric signal input and no torque output, and the hollow shaft type inner rotor of the TV control motor is dragged by the torque distributor 2000 to rotate in the positive direction. The torque split flow is also shown in fig. 6.
When the vehicle is turning at high speeds, it is desirable to directionally distribute the inboard wheel torque to the outboard wheels to improve turning maneuverability. If the rotating direction of the wheels is set to be a positive direction when the automobile is driven, and the rotating direction is a negative direction otherwise, the left turning of the automobile is taken 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 Positive value), the torque is reduced and torque is increased through the TV reduction mechanism 1100, and the torque input to the ring gear 1031 in the double planetary TV coupling mechanism 1200 is-iT 0 Where i is the gear ratio of the TV reduction mechanism 1100. The torque input by the sun gear 1034 to the first axle 1402 in the first planetary gear train 1030 is therefore
The torque input by the TV control motor 1001 to the ring gear 1051 in the single planetary row differential coupling mechanism 1300 is then
The torque that the planet carrier 1053 in the third planetary gear train 1050 inputs into the first half-shaft 1402 is £ greater>
The torque input by the sun gear 1054 into the differential housing 1401 is @>
A torque equally divided by the differential case 1401 into the first half-shaft 1402 and the second half-shaft 1403 is>
The torque finally input to the first half shaft 1402 by the control motor 1001 is the torque input to the first half shaft 1402 by the sun gear 1034 in the first planetary gear train 1030The sum of the torque input to the first half-shaft 1402 from the carrier 1053 in the third planetary gear train 1050 and the torque equally divided into the first half-shaft 1402 by the differential case 1401 results in a value of ≧ 5>
The torque which is ultimately input into the second half-shaft 1403 by the TV control motor 1001 is ≥>
As can be seen from the above, the moments inputted into the first half-shaft 1402 and the second half-shaft 1403 by the TV control motor 1001 are equally opposite, so that the total longitudinal driving torque is not changed, and the left-side wheel torque connected to the first half-shaft 1402 is decreased and the right-side wheel torque connected to the second half-shaft 1403 is increased, and a yaw moment contributing to a left turn can be generated, improving the left-turn maneuverability of the automobile. Note that, at this time, the rotational speed of the TV control motor 1001 is the same as that at the normal differential left turn. The torque distribution flow at this time is shown in fig. 7. It should be noted that if the TV control motor outputs a positive torque at this time, the driving torque will be directionally distributed from the right side wheels to the left side wheels, and a yaw moment will be generated to prevent the vehicle from oversteering, for maintaining vehicle stability.
In the same way, when the automobile turns right at a high speed, the motor controller controls the TV control motor 1001 to output a forward torque, and can generate a yaw moment which is beneficial to turning right on the premise of not changing the total longitudinal driving torque, so that the right turning maneuverability of the automobile is improved. Note that, at this time, the rotational speed of the TV control motor 1001 is the same as that at the 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 directionally distributed from the left wheels to the right wheels, and a yaw moment will be generated to prevent the vehicle from oversteering, for maintaining vehicle stability.
While embodiments of the invention have been described above, it is not limited to the applications set forth in the description and the embodiments, which are fully applicable in various fields of endeavor to which the invention pertains, and further modifications may readily be made by those skilled in the art, it being understood that the invention is not limited to the details shown and described herein without departing from the general concept defined by the appended claims and their equivalents.
Claims (10)
1. 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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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, wherein the second gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential case, the third planet carrier is in spline connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
and 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 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 gear ring 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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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 gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential case, the third planet carrier is in spline connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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 gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential shell, the third planet carrier is in spline connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
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:
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 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 coaxially and fixedly connected with a first half shaft, and the first gear ring 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 gear ring is fixed on the driving axle housing, and the second planet carrier is fixedly connected with the first planet carrier; 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 differential case, the third planet carrier is in splined connection with the first half shaft, and the third gear ring is fixedly connected with the second sun gear;
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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| CN201710265582.XA CN107035847B (en) | 2017-04-21 | 2017-04-21 | Electric differential mechanism with torque directional distribution function |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN108394274A (en) * | 2018-05-03 | 2018-08-14 | 吉林大学 | A kind of between centers torque universe actively distributes full-time four-wheel drive system |
| CN108501705A (en) * | 2018-05-10 | 2018-09-07 | 吉林大学 | A kind of between centers torque universe actively distributes full-time four-wheel drive system |
| CN108501712A (en) * | 2018-05-10 | 2018-09-07 | 吉林大学 | A kind of between centers torque universe actively distributes full-time four-wheel drive system |
| CN108501703A (en) * | 2018-05-10 | 2018-09-07 | 吉林大学 | A kind of between centers torque universe actively distributes full-time four-wheel drive system |
| CN108501702A (en) * | 2018-05-10 | 2018-09-07 | 吉林大学 | A kind of between centers torque universe actively distributes in due course four-wheel drive system |
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|---|---|---|---|---|
| EP0025499A2 (en) * | 1979-08-20 | 1981-03-25 | Caterpillar Tractor Co. | Differential for multiplying torquing force and drive train |
| DE102012009346A1 (en) * | 2012-05-09 | 2013-11-14 | ZG-Zahnräder und Getriebe GmbH | Planetary coupler gear structure for electrical drive system of motor car, has first planetary gear whose web is connected to sun gear of second planetary gear, and internal gear is connected to abortive web of second planetary gear |
| CN104670010A (en) * | 2015-02-11 | 2015-06-03 | 吉林大学 | Electric driving spur gear differential with torque directional distribution function |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5141605B2 (en) * | 2009-03-12 | 2013-02-13 | 三菱自動車工業株式会社 | Driving force adjustment device |
| CN104675951B (en) * | 2015-02-11 | 2017-02-01 | 吉林大学 | Electric differential with double-row planetary gear torque directional distribution mechanism |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0025499A2 (en) * | 1979-08-20 | 1981-03-25 | Caterpillar Tractor Co. | Differential for multiplying torquing force and drive train |
| DE102012009346A1 (en) * | 2012-05-09 | 2013-11-14 | ZG-Zahnräder und Getriebe GmbH | Planetary coupler gear structure for electrical drive system of motor car, has first planetary gear whose web is connected to sun gear of second planetary gear, and internal gear is connected to abortive web of second planetary gear |
| CN104670010A (en) * | 2015-02-11 | 2015-06-03 | 吉林大学 | Electric driving spur gear differential with torque directional distribution function |
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