CN106870685B - Electric differential mechanism with torque directional distribution function - Google Patents
Electric differential mechanism with torque directional distribution function Download PDFInfo
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- CN106870685B CN106870685B CN201710265581.5A CN201710265581A CN106870685B CN 106870685 B CN106870685 B CN 106870685B CN 201710265581 A CN201710265581 A CN 201710265581A CN 106870685 B CN106870685 B CN 106870685B
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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 mechanism with a torque directional distribution function, which comprises: a main drive mechanism; a bevel gear differential; a TV control drive mechanism for outputting control power; the first single-row planetary gear train is characterized in that a first planet carrier is coaxially and fixedly connected with a first half shaft, a first gear ring is connected with a control output end, and a first sun gear is supported on the first half shaft through a bearing; the second single-row planetary gear train is characterized in that a second gear ring is fixed on the drive axle housing, and a 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; a third sun gear is fixedly connected with the second planet carrier, the third planet carrier is fixedly connected with the differential case, and a third gear ring is fixedly connected with the first half shaft; the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters. The invention enables the driving torque of the automobile to be directionally distributed to the left wheel and the right wheel 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 reversal 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 economical efficiency and environmental protection, and has the characteristic of almost zero emission, 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 fast 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 that 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, even if the ground adhesion is good, the adhesion capability of the outer wheel is higher than that of the inner wheel, 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 of the inner wheels is transferred to the outer wheels, the lateral force margin of the inner wheels can be increased, the wheels are prevented from slipping, and an additional yaw moment can be generated on the whole vehicle, and the moment can help to push and guide the vehicle to turn, so that the turning maneuverability and the ultimate turning capability of the vehicle are improved. 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, 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 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, 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, the first planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
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 drive axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;
the third single-row planetary gear train comprises a third sun gear, a third planetary gear, a third planet carrier and a third gear ring, the third sun gear is fixedly connected with the second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
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;
and the sixth single-row planetary gear train comprises a sixth sun gear, a sixth planet carrier and a sixth gear ring, 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 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 planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
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 sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;
the third single-row planetary gear train comprises a third sun gear, a third planetary gear, a third planet carrier and a third gear ring, the third sun gear is fixedly connected with the second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
and 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:
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, the first planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
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 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 second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
and 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:
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, the first planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
the second single-row double-stage planetary gear train comprises a second sun gear, a second double-stage planetary gear, a second planet carrier and a second gear ring, the second gear ring 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 second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
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 of differential speed differential torque difference of the differential in the traditional drive axle, 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 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 electric differential with a torque directional distribution function according to an embodiment of 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 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 spline-connected 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 comprises a sun gear 1034, three planetary gears 1032 which are evenly distributed on the circumference, a planet carrier 1033 and an inner gear 1031. The ring gear 1031 is integrated with a planet carrier 1023 of the fifth planetary gear train 1020, the planet carrier 1033 is in spline connection with the first half shaft 1402, the sun gear 1034 is integrated with a sun gear 1044 of the second planetary gear train 1040, and the sun gear 1034 is supported on the first half shaft 1402 through a bearing. 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 planet carrier 1043 is integrated with the sun gear 1054 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 and the second planet carrier 1043 are integrated and supported on the first half shaft 1402 through a bearing, the planet carrier 1053 is fixedly connected with the differential case 1401, and the ring gear 1051 is in spline connection with the first half shaft 1402.
The conventional bevel gear differential 1400 is basically constructed 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 spline-connected to a first half shaft 1402, a second side gear 1405 is spline-connected to a second half shaft 1403, and a differential case 1401 is supported on the second half 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 on the circumference, a planet carrier 1073 and an inner gear ring 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 with 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 speed reducing mechanism 1500 through the sun gear 1074, and acts on the differential case 1401, and finally equally divides 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 of the present invention, the following,
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 planetary gears 1052 of the third planetary gear train 1050 rotate only with the revolution of the differential case 1401 without rotating on the axis, so that the ring gear 1051 and the sun gear 1054 rotate at the same speed. Since the rotational speeds of the carrier 1033 of the first planetary gear train 1030 and the ring gear 1051 of the third planetary gear train 1050 are the same, and the carrier 1043 of the second planetary gear train 1040 and the sun gear 1054 of the third planetary gear train 1050 are integrated, the carrier 1033 of the first planetary gear train 1030 and the carrier 1043 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 the sun gear and the rotational speeds of both carriers 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, the rotational speed is 0, and 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 torque distribution is not needed, so that a TV control motor 1001 has no control electric signal, the TV control motor is not started, the automobile is driven by a main driving motor 1002 only, the torque output by the main driving motor 1002 is added through a main driving motor speed reducing mechanism 1500 and acts on a differential shell 1401, and due to the principle of torque equal division of a traditional bevel gear differential mechanism 1400, the torque acting on the differential shell 1401 is equally divided into a first half shaft 1402 and a 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 R5 ＜n PC5
therefore:
n S5 ＞n R5
i.e., the sun gear 1054 in the third planetary gear train 1050, is faster than the ring gear 1051, the carrier 1033 in the first planetary gear train 1030 is slower than the carrier 1043 in the second planetary gear train 1040 for the double row TV coupling 1200. Since the first planetary gear train 1030 and the second planetary gear train 1040 share the sun gear, the double planetary TV coupling mechanism 1200 includes:
kn R3 -(k+1)n PC3 ＝kn R4 -(k+1)n PC4
in the formula n PC3 For the first planetary train 1030 Planet Carrier 1033 speed, n R3 For the first planetary gear train 1030 the speed, n, of the ring gear 1031 PC4 Is the rotational speed, n, of the planet carrier 1043 of the second planetary gear train 1040 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 PC3 ＜n PC4 and n is R4 ＝0
So that:
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.
Similarly, when the vehicle 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 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 rotation direction of the wheels is set to be a positive direction when the automobile is driven, and the rotation direction is a negative direction when the automobile is driven, 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. So the torque input to the first half-axle 1402 from the planet carrier 1033 in the first planetary gear train 1030 is
The TV control motor 1001 inputs a torque into the sun gear 1054 in the single row differential coupling 1300 that is->
So that the torque of the input of the inner gear 1051 in the third planetary gear train 1050 to the first half axle 1402 is
The planet carrier 1053 is input into the differential case 1401Has a moment of->
The 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 into the first half-shaft 1402 by the control motor 1001 is composed of the sum of the torque input into the first half-shaft 1402 from the planetary carrier 1033 in the first planetary gear train 1030, the torque input into the first half-shaft 1402 from the ring gear 1051 in the third planetary gear train 1050, and the torque equally divided into the first half-shaft 1402 by the differential case 1401, and the result is ÷ or>
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 forward 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 the stability of the vehicle.
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 a 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 the stability of the vehicle.
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:
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 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, the first planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
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 drive axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;
the third single-row planetary gear train comprises a third sun gear, a third planetary gear, a third planet carrier and a third gear ring, the third sun gear is fixedly connected with the second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
wherein the second single-row planetary gear train and the first single-row planetary gear train have the same characteristic parameters.
2. The electric differential with torque vectoring function as claimed in claim 1, wherein said TV control drive mechanism comprises a TV control motor and a TV speed reduction mechanism.
3. An electric differential with torque directional distribution as set forth in claim 2 wherein said TV control motor has a hollow output shaft, said first half shaft being rotatably supported on and extending out of said hollow output shaft.
4. The electric differential with torque vectoring function as claimed in claim 2, wherein said TV speed reduction mechanism comprises:
the fourth single-row planetary gear train comprises a fourth sun gear, a fourth planetary gear, a fourth planet carrier and a fourth gear ring, the fourth sun gear is fixedly connected with the hollow output shaft, and the fourth gear ring is fixed on the drive axle housing;
and the fifth single-row planetary gear train comprises a fifth sun gear, a fifth 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 directional distribution as set forth in claim 1 wherein said primary drive mechanism includes 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:
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 planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
the second single-row double-stage planetary gear train comprises a second sun gear, a second double-stage planetary gear, a second planet carrier and a second gear ring, the second gear ring is fixed on the driving axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;
the third single-row planetary gear train comprises a third sun gear, a third planetary gear, a third planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
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, the first planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
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 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 second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
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 planet carrier is coaxially and fixedly connected with a first half shaft, the first gear ring is connected with the output end of the TV control driving mechanism, and the first sun is rotatably supported on the first half shaft;
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 drive axle housing, and the second sun gear is fixedly connected with the first sun gear; the second sun gear is rotatably supported on the first half shaft;
the third single-row double-stage planetary gear train comprises a third sun gear, a third double-stage planetary gear, a third planet carrier and a third gear ring, wherein the third sun gear is fixedly connected with the second planet carrier, the third planet carrier is fixedly connected with the differential case, and the third gear ring is fixedly connected with the first half shaft;
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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| CN201710265581.5A CN106870685B (en) | 2017-04-21 | 2017-04-21 | Electric differential mechanism with torque directional distribution function |
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| CN201710265581.5A CN106870685B (en) | 2017-04-21 | 2017-04-21 | Electric differential mechanism with torque directional distribution function |
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| CN106870685B true CN106870685B (en) | 2023-04-07 |
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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 |
| GB0819272D0 (en) * | 2007-11-09 | 2008-11-26 | Ford Global Tech Llc | Power take-off for all-wheel-drive systems |
| CN104675951A (en) * | 2015-02-11 | 2015-06-03 | 吉林大学 | Electric differential with double-row planetary gear torque directional distribution mechanism |
Family Cites Families (1)
| 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 |
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2017
- 2017-04-21 CN CN201710265581.5A patent/CN106870685B/en active Active
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 |
| GB0819272D0 (en) * | 2007-11-09 | 2008-11-26 | Ford Global Tech Llc | Power take-off for all-wheel-drive systems |
| CN104675951A (en) * | 2015-02-11 | 2015-06-03 | 吉林大学 | Electric differential with double-row planetary gear torque directional distribution mechanism |
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