CN107061682B - Electric differential mechanism with torque directional distribution function - Google Patents
Electric differential mechanism with torque directional distribution function Download PDFInfo
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- CN107061682B CN107061682B CN201710266031.5A CN201710266031A CN107061682B CN 107061682 B CN107061682 B CN 107061682B CN 201710266031 A CN201710266031 A CN 201710266031A CN 107061682 B CN107061682 B CN 107061682B
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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
- F16H48/08—Differential gearings with gears having orbital motion comprising bevel gears
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
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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 with a torque directional distribution function, which comprises the following components: a main driving mechanism; bevel gear differential mechanism; a TV control driving mechanism for outputting control power; the first sun gear is supported on the first half shaft by a bearing, the first gear ring is fixedly connected with the first half shaft coaxially, and the first planet carrier is connected with the control output end; the second single-row planetary gear train is arranged on the driving axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is supported on the first half shaft by a bearing; the third sun gear is fixedly connected with the differential shell, the third planet carrier is fixedly connected with the second annular gear, and the third annular gear is fixedly connected with the first half shaft; 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 directionally distributed 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 energy crisis and the increasing importance of environmental protection, new energy automobiles are the reverse of future automobiles, and electric automobiles are rapidly developed worldwide. Compared with the traditional internal combustion engine automobile, the electric automobile has better economical efficiency and environmental protection, and the characteristics of zero emission are similar to the characteristics of the electric automobile, so that the electric automobile has remarkable advantages in the aspect of environmental protection. 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 motor rotating speed and torque are easy to obtain, and the electric automobile can be controlled more accurately. Therefore, electric automobiles have great development potential.
The electric automobile generally adopts a power assembly formed by a motor and a drive axle or a power assembly formed by a motor, a transmission and the drive axle to drive the automobile to run, and the electric automobile driven by the hub motor is not produced in large scale due to the defects of large unsprung mass, poor heat dissipation of the hub motor and the like, so that the drive axle is mostly contained in the power assembly of the existing electric automobile.
The differential mechanism is an important part in a driving axle, and because of the differential mechanism' differential speed is not poor, the driving torque of an automobile can only be equally distributed on two sides of left and right wheels, so that the ground adhesion force cannot be well utilized under the condition of unequal road surface adhesion, and even unstable working conditions such as wheel slip and the like are easily caused on one side with low adhesion, and the adhesion capability of a driving wheel cannot be exerted. Meanwhile, because the condition that the load is transferred from the inner side wheel to the outer side wheel occurs when the vehicle turns at a high speed, even if the ground is attached well, the attaching capacity of the outer side wheel is higher than that of the inner side wheel, and the inner side wheel can possibly slip when the torque is equally divided to the inner side wheel and the outer side wheel by the traditional differential mechanism, so that the automobile is unstable. If a portion of the torque of the inside wheel is transferred to the outside wheel, the side force margin of the inside wheel can be increased, the wheel slip can be prevented, and an additional yaw moment can be generated for the whole vehicle, which can help to push and guide the vehicle to turn, improving the vehicle turning maneuverability and extreme turning capability. Currently, the technology is applied to some high-end sport cars and high-grade SUVs in the form of a torque-oriented distribution differential, such as a super four-wheel drive system (SH-AWD) of Honda and a super active yaw control System (SAYC) of Mitsubishi, etc., but the technology is not applied to electric automobiles too much.
Disclosure of Invention
The invention aims to solve the defect that the left and right output torques of a differential mechanism are equal and cannot be adjusted, and provides an electric differential mechanism with a torque directional distribution function.
The technical scheme provided by the invention is as follows:
an electric differential with torque vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell to drive the vehicle to run;
a TV control driving 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 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 fixedly connected with the first half shaft coaxially, 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, wherein the second planet carrier is arranged 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 planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the differential shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
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, and the first half shaft is rotatably supported on the hollow output shaft and penetrates the hollow output shaft.
Preferably, the TV deceleration mechanism includes:
the fourth single-row planetary gear train comprises a fourth sun gear, a fourth planet carrier and a fourth gear ring, wherein the fourth sun gear is fixedly connected with the hollow output shaft, and the fourth gear ring is fixed on the driving axle housing;
the fifth single-row planetary gear train comprises a fifth sun gear, a fifth planet carrier and a fifth gear ring, wherein the fifth sun gear is fixedly connected with the fourth planet carrier, the fifth gear ring is fixed on a driving axle housing, and the fifth planet carrier is used as a control output end and is connected with the first planet carrier.
Preferably, the main driving mechanism includes a main driving motor and a main reducing mechanism.
Preferably, the main drive motor has a hollow output shaft, and the second half shaft is rotatably supported on the hollow output shaft and extends out of the hollow output shaft.
Preferably, the final reduction mechanism includes:
the seventh single-row planetary gear train comprises a seventh sun gear, a seventh planet carrier and a seventh gear ring, wherein the seventh sun gear is fixedly connected with an output shaft of the main driving motor, and the seventh gear ring is fixed on the driving axle housing;
the sixth single-row planetary gear train comprises a sixth sun gear, a sixth planet carrier and a sixth gear ring, wherein the sixth sun gear is fixedly connected with the seventh planet carrier, the sixth gear ring is fixed on the driving axle housing, and the sixth planet carrier is fixedly connected with the differential housing.
An electric differential with torque vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell to drive the vehicle to run;
a TV control driving 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 fixedly connected with the first half shaft in a coaxial way, 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 planetary double-stage star wheel, a second planet carrier and a second gear ring, wherein the second planet carrier is arranged 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 planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the differential shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
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 vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell to drive the vehicle to run;
a TV control driving 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 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 fixedly connected with the first half shaft coaxially, 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, wherein the second planet carrier is arranged 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 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 mechanism shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
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 vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell to drive the vehicle to run;
a TV control driving 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 fixedly connected with the first half shaft in a coaxial way, 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 arranged 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 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 mechanism shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
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 invention are as follows:
1. the electric differential with the torque directional distribution function solves the defect that the differential is not poor in torque in the traditional driving axle, so that the driving torque of an automobile can be directionally distributed to the wheels at the left side and the right side according to the control requirement of control logic, the function of unequal distribution of the torques of the wheels at the left side and the right side is realized on the premise of not changing the longitudinal total driving torque, and the turning maneuverability and the driving fun of the automobile are improved.
2. The electric differential with the torque directional distribution function provided by the invention has the advantages that 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 provided by the invention belongs to sprung masses, so that unsprung masses are not obviously increased like an in-wheel motor, and the influence on smoothness of an automobile in running is small.
Drawings
Fig. 1 is a schematic view of an embodiment of an electric differential with torque directional distribution according to the present invention.
Fig. 2 is a schematic diagram of a second embodiment of an electric differential with torque directional distribution according to the present invention.
Fig. 3 is a schematic view of a third embodiment of an electric differential with torque directional distribution according to the present invention.
Fig. 4 is a schematic diagram of a fourth embodiment of an electric differential with torque directional distribution according to the present invention.
Fig. 5 is a schematic diagram of the torque flow direction of the electric differential with the torque directional distribution function according to the present invention when the vehicle is running straight.
Fig. 6 is a schematic diagram of the torque flow direction of the electric differential with the torque directional distribution function according to the present invention during 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 according to the present invention when the automobile is turning left and the torque directional distributor is operating.
Fig. 8 is a schematic diagram of the torque flow direction of the electric differential with the torque directional distribution function according to the present invention when the vehicle is turning right and the torque directional distributor is operating.
Detailed Description
The present invention is described in further detail below with reference to the drawings to enable those skilled in the art to practice the invention by referring to the description.
Example 1
As shown in fig. 1, the present invention provides an electric differential with torque distribution function, consisting essentially of a torque vectoring distributor 2000, a conventional bevel gear differential 1400, a main drive motor reduction mechanism 1500, and a main drive motor 1002.
In this embodiment, the torque directional distributor 2000 is located at the left side of the drive axle (or can be exchanged with the main drive motor 1002 and is disposed at the right side of the drive axle), and mainly comprises a TV control motor 1001, a TV reduction mechanism 1100, a double planetary TV coupling mechanism 1200 and a single planetary differential coupling mechanism 1300.
The TV control motor 1001 is a hollow shaft type inner rotor motor, and a first half shaft 1402 connected to a left wheel penetrates from an inner hole of a hollow rotor shaft thereof, and the hollow shaft type inner rotor is spline-connected with a sun gear 1014 of the fourth planetary gear train 1010, so that an 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 half shaft 1402 via a bearing, and its stator and its housing are fixed to a transaxle case.
The TV reduction mechanism 1100 basically includes a fourth planetary gear train 1010 and a fifth planetary gear train 1020. The fourth planetary gear system 1010 includes a sun gear 1014, three circumferentially-spaced planetary gears 1012, a carrier 1013, and an inner gear ring 1011 fixed to the driving axle housing. Wherein the sun gear 1014 is spline-connected to the hollow shaft inner rotor of the TV control motor 1001, and the carrier 1013 is integral with the sun gear 1024 of the fifth planetary gear train 1020. The fifth planetary gear system 1020 comprises a sun gear 1024, three planetary gears 1022 uniformly distributed on the circumference, a planet carrier 1023 and an inner gear ring 1021 fixed on the driving axle housing. Wherein the sun gear 1024 is supported on the first half shaft 1402 by bearings, and the carrier 1023 is integral with the carrier 1033 of the first planetary gear train 1030.
It is preferred that the TV reduction mechanism 1100 be constituted by a single row planetary gear train, a multiple row planetary gear train, or other forms of reduction mechanism, and thus changing the form of the reduction mechanism 1100 is not considered an innovation of the present invention.
The dual planetary TV coupling mechanism 1200 mainly includes a first planetary gear train 1030 and a second planetary gear train 1040, and their planetary line characteristic parameters must be the same, and the types of planetary lines must be identical. The first planetary gear train 1030 includes a sun gear 1034, three circumferentially-distributed planetary gears 1032, a planet carrier 1033, and an inner gear ring 1031. Wherein the planet carrier 1033 is integral with the planet carrier 1023 of the fifth planetary gear train 1020, the ring gear 1031 is splined to the first half shaft 1402, and the sun gear 1034 is integral with the sun gear 1044 of the second planetary gear train 1040 and supported on the first half shaft by bearings. The second planetary gear train 1040 includes a sun gear 1044, three planetary gears 1042 uniformly distributed on the circumference, a planet carrier 1043, and an inner gear 1041. Wherein the planet carrier 1043 is fixed to the driving axle housing, the sun gear 1044 is integral with the first sun gear 1034 and supported on the first half shaft 1402 by bearings, and the ring gear 1041 is integral with the planet carrier 1053 of the third planetary gear train 1050.
The single row differential coupling mechanism 1300 is comprised primarily of a 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 gear 1051. Wherein sun gear 1054 is fixedly connected with differential housing 1401, planet carrier 1053 is fixedly connected with second ring gear 1041, and ring gear 1051 is splined to first half shaft 1402.
The conventional bevel gear differential 1400 is mainly composed 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 planetary gear shaft 1408. Wherein a first side gear 1404 is splined to the first axle 1402 and a second side gear 1405 is splined to the second axle 1403, the differential housing 1401 is supported on the second axle 1403 by bearings.
The main driving motor reduction mechanism 1500 is located on the right side of the driving axle, and mainly comprises a sixth planetary gear train 1060 and a seventh planetary gear train 1070. The sixth planetary gear system 1060 includes a sun gear 1064, three planetary gears 1062 uniformly distributed around the sun gear, a planet carrier 1063, and an inner gear ring 1061 fixed on the driving axle housing. With carrier 1063 integral with differential housing 1401, sun gear 1064 integral with carrier 1073 of seventh planetary gear train 1070, and sun gear 1064 bearing supported on second axle shaft 1403. 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 gear ring 1071 fixed on the driving axle housing. Wherein sun gear 1074 is splined to the hollow inner rotor shaft of main drive motor 1002.
It is preferred that the main drive motor reduction mechanism 1500 be constructed of a single planetary gear train, multiple planetary gear trains, or other form of reduction mechanism, and thus 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 is a hollow shaft type inner rotor motor, and the second half shaft 1403 connected to the right wheel passes out of the inner hole of the hollow rotor shaft. The hollow shaft inner rotor is splined to the 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 onto the differential housing 1401 for eventual halving to the first half shaft 1402 and the second half shaft 1403. The main driving motor 1002 is supported on the second half shaft 1403 through a bearing, and the stator and the shell thereof are fixed with the driving 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 gear train TV coupling mechanism 1200 are all single planetary gear trains, and the third planetary gear train 1050 in the single planetary gear train differential coupling mechanism 1300 is a double planetary gear train, and the schematic diagram is shown in the drawing.
Example III
As shown in fig. 3, in the present embodiment, the first planetary gear train 1030 and the second planetary gear train 1040 in the double planetary gear train TV coupling mechanism 1200 are two-stage planetary gear rows, and the third planetary gear train 1050 in the single planetary gear train differential coupling mechanism 1300 is a single planetary gear row, and the schematic diagram is shown in the drawing.
In a fourth embodiment of the present invention,
as shown in fig. 4, in the present embodiment, the first planetary gear train 1030 and the second planetary gear train 1040 in the double planetary gear train TV coupling mechanism 1200 are two-stage planetary gear rows, and the third planetary gear train 1050 in the single planetary gear train differential coupling mechanism 1300 is two-stage planetary gear rows, and the schematic diagram is shown.
The solutions shown in fig. 1 to 4 are all the structural solutions of the realizable embodiment of the electric differential with the torque directional distribution function according to the present invention, but the embodiment shown in fig. 1 is the best preferred solution in view of the system inertia loss and the operation efficiency, followed by the solution shown in fig. 3, and again the solutions shown in fig. 2 and 4.
The working principle of the electric differential with the torque directional distribution function is as follows:
the working principle will be described by taking the schematic structural diagram of the embodiment of the electric differential with torque directional distribution function shown in fig. 1 as an example.
When the automobile runs straight, the driving torques of the wheels at the left side and the right side are the same, no torque distribution is needed, so that a control electric signal is not generated in the TV control motor 1001, the TV control motor is not started, the automobile is only driven by the main driving motor 1002, the torque output by the main driving motor 1002 is added to the differential shell 1401 through the torque of the main driving motor reduction mechanism 1500, and the torque applied to the differential shell 1401 is equally divided to the first half shaft 1402 and the second half shaft 1403 due to the principle of equally dividing the torque of the traditional bevel gear differential mechanism 1400, so that the automobile is driven to run. If the rotation direction of the wheels is set to be positive, the rotation direction is set to be negative. 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 planetary gears 1052 of the third planetary gear train 1050 do not spin only with the revolution of the differential case 1401, and therefore, the ring gear 1051 and the carrier 1053 rotate at the same speed. Since the ring gear 1031 of the first planetary gear train 1030 and the ring gear 1051 of the third planetary gear train 1050 have the same rotation speed, the ring gear 1041 of the second planetary gear train 1040 and the carrier 1053 of the third planetary gear train 1050 are integrated, and therefore the ring gear 1031 of the first planetary gear train 1030 and the ring gear 1041 of the second planetary gear train 1040 rotate at the same speed. Since the first planetary gear train 1030 and the second planetary gear train 1040 share the sun gear, the two ring gear speeds are also the same, so that the speed of the carrier 1033 is also the same as the speed of the carrier 1043, and the carrier 1043 is fixed at a speed of 0, so that the speed of the carrier 1033 is also 0. Since the TV speed reducing mechanism 1100 only changes the torque output from the TV control motor 1001, and does not change the positive and negative directions of the torque output, when the vehicle 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, does not output torque, the vehicle is driven by the main drive motor 1002 only, and the torque distribution flow is as shown in fig. 5.
When the automobile normally turns in a differential speed, the driving torques of the wheels at the left side and the right side are the same, no torque distribution is needed, so that a control electric signal is not generated in the TV control motor 1001, the TV control motor is not started, the automobile is only driven by the main driving motor 1002, the torque output by the main driving motor 1002 is added to the differential case 1401 through the torque increase of the main driving motor reduction mechanism 1500, and the torque applied to the differential case 1401 is equally distributed to the first half shaft 1402 and the second half shaft 1403 due to the principle of equally distributing the torque of the traditional bevel gear differential mechanism 1400, so that the automobile is driven to run.
Taking the normal differential left turn of the automobile as an example, if the rotation direction of the wheels is set to be positive during the driving of the automobile, the rotation direction is set to be negative. The differential coupling mechanism 1050 for a single planet row is then derived from the single planet row rotational speed equation:
n S5 +k 5 n R5 -(k 5 +1)n PC5 ＝0
in n S5 For the third planetary gear train 1050 sun gear 1054 speed, n R5 For the third planetary gear train 1051 ring gear speed, n PC5 For the third planetary gear train 1053 carrier speed, k 5 Is a characteristic parameter of a planet row of the third planetary gear train. Since the automobile turns left, the differential case 1401 rotates at a speed greater than that of the first half shaft 1402, so that:
n S5 ＞n R5
so that:
n PC5 ＞n R5
i.e., the rotational speed of carrier 1053 in third planetary gear train 1050 is greater than the rotational speed of ring gear 1051, ring gear 1031 in first planetary gear train 1030 is less than ring gear 1041 in second planetary gear train 1040 for double planetary gear train TV coupling mechanism 1200. Further, since the first planetary gear train 1030 and the second planetary gear train 1040 share a sun gear, the double planetary gear train TV coupling mechanism 1200 includes:
kn R3 -(k+1)n PC3 ＝kn R4 -(k+1)n PC4
in n PC3 Carrier 1033 rotational speed, n, for first planetary gear train 1030 R3 For the rotational speed, n, of the ring gear 1031 of the first planetary gear train 1030 PC4 For the second planetary gear train 1040, carrier 1043 speed, n R4 For the speed of the ring gear 1041 in the second planetary gear set 1040, k is the planet row characteristics of the first planetary gear set 1030 and the second planetary gear set 1040Parameters. Again because:
n R3 ＜n R4 and n is PC4 ＝0
So that:
n PC3 ＜0
that is, the rotation speed of the 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 automobile normally rotates at a differential speed to the left, 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 a negative direction. The torque distribution flow is shown in fig. 6.
Similarly, when the automobile is normally rotated at a differential speed and right, 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 a positive direction. The torque distribution flow is also shown in fig. 6.
When the vehicle turns at high speeds, it is desirable to distribute the inboard wheel torque orientation to the outboard wheel to improve turning maneuverability. If the rotation direction of the wheels is positive when the automobile is driven, and if the rotation direction is negative, the left turn of the automobile is taken as an example for analysis. At this time, the motor controller controls the TV control motor 1001 to output torque-T 0 (T 0 Positive value) that is reduced in speed and increased in torque by the TV reduction mechanism 1100, the torque input to the carrier 1033 of the double-planetary-gear-train TV coupling mechanism 1200 is-iT 0 Where i is the gear ratio of the TV reduction mechanism 1100. So the torque input to the first half shaft 1402 by the ring gear 1031 in the first planetary gear train 1030 is
The torque of the carrier 1053 input into the single row differential coupling mechanism 1300 by the TV control motor 1001 is +.>
The torque input to the first half shaft 1402 by the ring gear 1051 in the third planetary gear train 1050 is
Sun gear1054 the moment input into differential carrier 1401 is +.>
The moment equally divided by the differential case 1401 to 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 composed of the sum of the torque input to the first half shaft 1402 by the ring gear 1031 in the first planetary gear train 1030, the torque input to the first half shaft 1402 by the ring gear 1051 in the third planetary gear train 1050, and the torque equally divided by the differential case 1401 into the first half shaft 1402, and the result is ∈ ->
The torque ultimately fed to the second half shaft 1403 by the TV control motor 1001 is +.>
As can be seen from the above, the torques inputted into the first axle 1402 and the second axle 1403 by the TV control motor 1001 are largely reversed, so that the total longitudinal driving torque is not changed, and the left wheel torque connected to the first axle 1402 is reduced, and the right wheel torque connected to the second axle 1403 is increased, a yaw moment contributing to the left turn can be generated, and the left turn maneuverability of the automobile is improved. In this case, the rotation speed of the TV control motor 1001 is the same as that in normal differential left-hand rotation. The torque distribution flow at this time is shown in fig. 7. If the TV control motor outputs a forward torque at this time, the drive torque is distributed from the right wheel to the left wheel, which is directed, and a yaw moment for preventing the vehicle from oversteering is generated for maintaining the stability of the vehicle.
Similarly, when the automobile turns right at a high speed, the motor controller controls the TV control motor 1001 to output a forward torque, and a yaw moment which is conducive to turning right can be generated on the premise of not changing the total longitudinal driving torque, so that the right turning maneuverability of the automobile is improved. In this case, the rotation speed of the TV control motor 1001 is the same as that in normal differential right-hand turning. The torque distribution flow at this time is shown in fig. 8. If the TV control motor outputs a negative torque at this time, the drive torque is distributed from the left wheel to the right wheel, which is directed, and a yaw moment for preventing the vehicle from oversteering is generated, so that the stability of the vehicle is maintained.
Although embodiments of the present invention have been disclosed above, it is not limited to the details and embodiments shown and described, it is well suited to various fields of use for which the invention would be readily apparent to those skilled in the art, and accordingly, the invention is not limited to the specific details and illustrations shown and described herein, without departing from the general concepts defined in the claims and their equivalents.
Claims (10)
1. An electric differential with torque vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell, and equally divide the rotary power to a first half shaft and a second half shaft of the differential mechanism to drive a vehicle to run;
a TV control driving 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 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 fixedly connected with the first half shaft coaxially, 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, wherein 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 planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the differential shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
wherein the second single-row planetary gear train has the same characteristic parameters as the first single-row planetary gear train.
2. The electric differential with torque vectoring capability of claim 1, wherein the TV control drive mechanism comprises a TV control motor and a TV retarding mechanism.
3. The electric differential with torque vectoring capability of claim 2 wherein the TV control motor has a hollow output shaft with the first axle shaft rotatably supported therein and extending therethrough.
4. The electric differential with torque vectoring function of claim 2, wherein the TV speed reducing mechanism comprises:
the fourth single-row planetary gear train comprises a fourth sun gear, a fourth planet carrier and a fourth gear ring, wherein the fourth sun gear is fixedly connected with the hollow output shaft, and the fourth gear ring is fixed on the driving axle housing;
the fifth single-row planetary gear train comprises a fifth sun gear, a fifth planet carrier and a fifth gear ring, wherein the fifth sun gear is fixedly connected with the fourth planet carrier, the fifth gear ring is fixed on a driving axle housing, and the fifth planet carrier is used as a control output end and is connected with the first planet carrier.
5. The electric differential with torque vectoring capability of claim 1, wherein the primary drive mechanism comprises a primary drive motor and a final drive mechanism.
6. The electric differential with torque vectoring function of claim 5 wherein the main drive motor has a hollow output shaft with a second axle shaft rotatably supported thereon and extending therethrough.
7. The electric differential with torque vectoring function of claim 5, wherein the final drive mechanism comprises:
the seventh single-row planetary gear train comprises a seventh sun gear, a seventh planet carrier and a seventh gear ring, wherein the seventh sun gear is fixedly connected with an output shaft of the main driving motor, and the seventh gear ring is fixed on the driving axle housing;
the sixth single-row planetary gear train comprises a sixth sun gear, a sixth planet carrier and a sixth gear ring, wherein the sixth sun gear is fixedly connected with the seventh planet carrier, the sixth gear ring is fixed on the driving axle housing, and the sixth planet carrier is fixedly connected with the differential housing.
8. An electric differential with torque vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell to drive the vehicle to run;
a TV control driving 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 fixedly connected with the first half shaft in a coaxial way, 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 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 planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the differential shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
wherein the second single-row double-stage planetary gear train has the same characteristic parameters as the first single-row double-stage planetary gear train.
9. An electric differential with torque vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell to drive the vehicle to run;
a TV control driving 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 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 fixedly connected with the first half shaft coaxially, 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, wherein 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 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 mechanism shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
wherein the second single-row planetary gear train has the same characteristic parameters as the first single-row planetary gear train.
10. An electric differential with torque vectoring function, comprising:
the main driving mechanism 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 rotary power to the differential mechanism shell to drive the vehicle to run;
a TV control driving 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 fixedly connected with the first half shaft in a coaxial way, 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 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 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 mechanism shell, the third planet carrier is fixedly connected with the second annular gear, and the third gear ring is fixedly connected with the first half shaft;
wherein the second single-row double-stage planetary gear train has the same characteristic parameters as the first single-row double-stage planetary gear train.
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| CN109723792A (en) * | 2017-10-31 | 2019-05-07 | 罗灿 | Non- bevel differential |
| CN110541921A (en) * | 2018-05-28 | 2019-12-06 | 罗灿 | Double-flow hundred-direction driver |
| CN110541923A (en) * | 2018-05-28 | 2019-12-06 | 罗灿 | Equidirectional transfer differential driver |
| CN113217600B (en) * | 2021-06-01 | 2022-05-06 | 吉林大学 | Automobile differential with torque vector distribution function |
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| JP2006327583A (en) * | 2006-06-15 | 2006-12-07 | Toyota Motor Corp | Drive device for vehicle |
| CN204553754U (en) * | 2015-02-11 | 2015-08-12 | 吉林大学 | With the electric differential mechanism of two-row planetary gear torque fixed direction allocation mechanism |
| WO2016165581A1 (en) * | 2015-04-13 | 2016-10-20 | 南京康尼精密机械有限公司 | Stepless variable transmission for differential speed-regulation planetary gears |
| CN206694520U (en) * | 2017-04-21 | 2017-12-01 | 吉林大学 | A kind of electric differential mechanism with torque fixed direction allocation function |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8544588B2 (en) * | 2007-11-09 | 2013-10-01 | Ford Global Technologies, Llc | Power takeoff for all-wheel-drive systems |
| JP5141605B2 (en) * | 2009-03-12 | 2013-02-13 | 三菱自動車工業株式会社 | Driving force adjustment device |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2006327583A (en) * | 2006-06-15 | 2006-12-07 | Toyota Motor Corp | Drive device for vehicle |
| CN204553754U (en) * | 2015-02-11 | 2015-08-12 | 吉林大学 | With the electric differential mechanism of two-row planetary gear torque fixed direction allocation mechanism |
| WO2016165581A1 (en) * | 2015-04-13 | 2016-10-20 | 南京康尼精密机械有限公司 | Stepless variable transmission for differential speed-regulation planetary gears |
| CN206694520U (en) * | 2017-04-21 | 2017-12-01 | 吉林大学 | A kind of electric differential mechanism with torque fixed direction allocation function |
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