CN108297619B - Electric drive axle for directional torque distribution of duplex planetary gear train - Google Patents
Electric drive axle for directional torque distribution of duplex planetary gear train Download PDFInfo
- Publication number
- CN108297619B CN108297619B CN201810203457.0A CN201810203457A CN108297619B CN 108297619 B CN108297619 B CN 108297619B CN 201810203457 A CN201810203457 A CN 201810203457A CN 108297619 B CN108297619 B CN 108297619B
- Authority
- CN
- China
- Prior art keywords
- gear
- planetary gear
- shaft
- housing
- half shaft
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 230000007246 mechanism Effects 0.000 claims abstract description 34
- 230000009467 reduction Effects 0.000 claims description 13
- 230000005540 biological transmission Effects 0.000 claims description 11
- 230000009977 dual effect Effects 0.000 claims description 7
- 238000005315 distribution function Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 5
- 230000007547 defect Effects 0.000 description 3
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 238000012827 research and development Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000012546 transfer Methods 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
- B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
- B60B35/12—Torque-transmitting axles
- B60B35/121—Power-transmission from drive shaft to hub
- B60B35/122—Power-transmission from drive shaft to hub using gearings
- B60B35/125—Power-transmission from drive shaft to hub using gearings of the planetary type
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K1/00—Arrangement or mounting of electrical propulsion units
- B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
- B60K17/165—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing provided between independent half axles
Abstract
The invention discloses a torque directional distribution electric drive axle of a duplex planetary gear train, which comprises the following components: the power output shaft of the main driving motor is connected with the bevel gear differential shell through a speed reducing mechanism; wherein a first half shaft is rotatably supported on the housing and connected through the housing to a first half shaft gear of the bevel gear differential and a second half shaft is rotatably supported on the housing and connected through the housing to a second half shaft of the bevel gear differential; TV controls the driving motor; the duplex planetary gear train comprises a first sun gear, a second sun gear, a first end planetary gear, a second end planetary gear and a first planet carrier. The arbitrary distribution of the wheel torque on the left side and the right side is realized.
Description
Technical Field
The invention relates to a torque directional distribution electric drive axle of a duplex planetary gear train, and belongs to the technical field of electric automobile transmission.
Background
In recent years, with the improvement of the living standard of people and the continuous progress of technology, people have also put higher and higher demands on the quality of automobiles, and the demands on safety, comfort, economy, driving fun and the like are gradually changed from the demands which are only used as a walking tool at first, so that the demands on high-performance automobiles are also increased year by year, and therefore, research and development investment on the high-performance automobiles is also necessary.
The electric automobile is an important development direction of adapting to energy conservation and emission reduction in future traffic modes, is valued by various countries, and has been well developed in recent years. The development of the Chinese electric automobile starts from large buses and small low-end electric automobiles, however, along with the development of electronic information technology, the electric automobile gradually develops to informatization and high-end, and high-performance and sports electric automobiles represented by Tesla and Biedi Tang are promoted. Therefore, in order to improve the drivability of the electric vehicle, the application of the electric drive axle with the torque directional distribution function is an important means for improving the technical level and the product force of the electric vehicle to develop the electric vehicle with high performance.
The traditional automobile driving axle is positioned at the tail end of a transmission system and mainly comprises a main speed reducer, a differential mechanism, a half shaft, a driving axle housing and the like, wherein the differential mechanism is an important part in the driving axle. Because of the principle of 'differential torque-free' of the differential mechanism, the driving torque transmitted by the engine can only be evenly distributed to wheels on two sides, so that the ground adhesion force can not be well utilized under the condition of uneven road surface adhesion, and even the situation of wheel slip occurs on one side with low adhesion, thereby causing instability of the vehicle. Meanwhile, when the automobile turns at a high speed, the load on the inner side is transferred to the outer side, so that the inner side wheels can reach the attachment limit to generate slip so as to cause instability of the automobile. If the driving torque can be distributed between the wheels at two sides at will, the attachment limit of each wheel can be fully utilized, and the instability working condition can be greatly reduced. In addition, when the road surface at the wheels at the two sides is uneven, the driving torque can be transferred from the low adhesion side to the high adhesion side, so that the working condition of wheel slip at the low adhesion side is eliminated. When the automobile turns at a high speed, if the driving torque is transferred from the inner side wheel to the outer side wheel, the inner side wheel can be prevented from slipping, the lateral force margin of the whole automobile is increased, and meanwhile, an additional yaw moment is generated, and the moment can help to push and guide the automobile to turn, so that the turning maneuverability and the limiting turning capacity of the automobile are improved.
Currently, the technology is applied to some high-end sport cars and 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, but the technology is not excessively applied to electric automobiles, and in addition, the existing torque-oriented distribution differential technology applied to the traditional four-wheel drive automobiles is often used for realizing the transverse transfer distribution of torque by switching two groups of multi-disc electromagnetic or hydraulic clutch control planetary gear mechanisms. Because of the slipping loss when the clutch is combined and disconnected, the system power consumption is increased. Moreover, the clutch locking torque is limited, and response lag exists in the action, which influences the execution effect and quality of the torque directional distribution. In addition, the prior art generally requires two sets of left and right clutches to control the left or right split of torque, which increases system cost and axial length, and requires high space requirements. Therefore, in order to solve the defects, the invention provides an electric drive axle for realizing a torque directional distribution function based on a duplex planetary gear train, aiming at increasing the driving pleasure, the limiting turning capability and the maneuverability of an electric automobile.
Disclosure of Invention
The invention designs and develops the electric drive axle for directional torque distribution of the duplex planetary gear trains, which can solve the defects that the output torques at two sides of a differential mechanism in the traditional drive axle are equal and cannot be regulated, and the directional torque distribution of wheels at two sides is realized without a clutch, so that the structure is simple.
The technical scheme provided by the invention is as follows:
A dual planetary gear train torque directional distribution electric drive axle comprising:
The power output shaft of the main driving motor is connected with the bevel gear differential shell through a speed reducing mechanism;
Wherein a first half shaft is rotatably supported on the housing and connected through the housing to a first half shaft gear of the bevel gear differential and a second half shaft is rotatably supported on the housing and connected through the housing to a second half shaft of the bevel gear differential;
TV controls the driving motor;
The double planetary gear train comprises a first sun gear, a second sun gear, a first end planetary gear, a second end planetary gear and a first planet carrier;
The first sun gear is connected with the first half shaft, and the second sun gear is rotatably supported on the first half shaft and fixedly connected with the bevel gear differential shell; the first end planetary gear and the second end planetary gear are coaxially arranged on a planetary shaft, and the planetary shaft is connected with a power output shaft of the TV control driving motor through the first planet carrier.
Preferably, the first end planetary gears are uniformly distributed around the first sun gear in the circumferential direction and meshed with the first sun gear, and the second end planetary gears are uniformly distributed around the second sun gear in the circumferential direction and meshed with the second sun gear.
It is preferred that the composition of the present invention,
The bevel gear differential further includes:
A planetary gear shaft passing through the center of the bevel gear differential housing and rotatably supported on the bevel gear differential housing;
a first conical planetary gear fixedly mounted on the planetary gear shaft and simultaneously externally engaged with the first side gear and the second side gear;
a second conical planetary gear fixedly mounted on the planetary gear shaft and simultaneously externally engaged with the first side gear and the second side gear;
The first conical planetary gear and the second conical planetary gear are symmetrically arranged.
Preferably, the first half shaft and the second half shaft respectively penetrate from center holes on two sides of the bevel gear differential housing and are rotatably supported on the housing.
Preferably, the bevel gear differential housing is rotatably supported on the transaxle housing.
Preferably, the speed reducing mechanism includes:
the first single-row planetary gear train comprises a third sun gear, a first planet gear, a second planet carrier and a first gear ring; the first gear ring is fixed on a driving axle shell, the third sun gear is rotatably supported on a second half shaft, and the second planet carrier is fixedly connected with the shell of the bevel gear differential mechanism;
The second single-row planetary gear train comprises a fourth sun gear, a second planet gear, a third planet carrier and a second gear ring; the fourth sun gear is rotatably supported on the second half shaft and is in spline connection with a power output shaft of the main driving motor, the second gear ring is fixed on the driving axle shell, and the third planet carrier is fixedly connected with the third sun gear.
Preferably, the first half shaft and the second half shaft are respectively connected with wheels on two sides of the vehicle.
Preferably, the transmission ratio of the first sun gear to the first end planetary gear and the transmission ratio of the second sun gear to the second end planetary gear are not equal.
Preferably, the TV driving motor is a hollow shaft type inner rotor motor, comprising:
a rotor fixedly connected to the power output shaft;
And the stator is fixedly connected with the TV driving motor shell.
Preferably, the TV drive motor housing is fixedly connected to the drive axle housing.
The beneficial effects of the invention are as follows:
1. The electric drive axle with the torque directional distribution function solves the defect of 'differential torque lack' of the traditional differential mechanism, so that the driving torque of an automobile can be directionally distributed to the left and right wheels of a rear axle according to the control requirement of control logic, the torque can be transferred from the wheel with the high rotating speed to the wheel with the low rotating speed, and the torque can be transferred from the wheel with the low rotating speed to the vehicle with the high rotating speed. Through the design of the planetary gear ratio, the random distribution of the wheel torque at the left side and the right side can be realized on the premise of not changing the longitudinal total driving torque, and the turning maneuverability and the driving pleasure of the vehicle are improved.
2. The electric drive axle with the torque directional distribution function provided by the invention uses the TV control motor as a driving power source of the torque directional distribution mechanism, realizes the function of torque directional distribution by matching with a single planetary row, simplifies the structure of the torque directional distribution mechanism compared with the prior art, and has high system integration level, compact structure and small space occupation. The control for realizing the torque directional distribution function is simpler and more reliable. And the traditional bevel gear differential mechanism which is the same as the existing automobile drive axle is adopted, and the product process inheritance is good.
3. Compared with a hub motor distributed driving system which can realize free torque distribution, the electric drive axle with the torque directional distribution function does not increase unsprung mass and does not influence the smoothness of an automobile.
Drawings
Fig. 1 is a schematic diagram of an electric drive axle with a torque directional distribution function according to the present invention.
Fig. 2 is a schematic diagram of the torque flow of the electric drive axle with torque vectoring capability according to the present invention when there is no torque demand.
Fig. 3 is a schematic diagram of the torque flow direction of the electric drive axle with torque directional distribution function according to the present invention when the drive torque is distributed by the second half-axis to the first half-axis.
Fig. 4 is a schematic diagram of the torque flow direction of the electric drive axle with torque directional distribution function according to the present invention when the drive torque is distributed by the first half shaft to the second half shaft.
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.
As shown in fig. 1, the present invention provides a torque directional distribution electric drive axle of a duplex planetary gear train, which is mainly composed of a torque directional distributor 2000, a bevel gear differential mechanism 1300, a main drive motor reduction mechanism 1000 and a main drive motor 1001.
The torque directional distributor 2000 is located on the left side of the drive axle (or can be exchanged with the main power source assembly composed of the main drive motor 1001 and the main drive motor reducing mechanism 1000, and is arranged on the right side of the drive axle), and mainly comprises a TV control motor 1002 and a duplex planetary gear train 1400.
The TV control motor 1002 is a hollow shaft type inner rotor motor, and the first half shaft 1301 connected to the left wheel is rotatably supported in the hollow rotor shaft hole of the TV control motor through the hollow rotor shaft hole thereof. The hollow shaft inner rotor of the TV control motor 1002 is fixedly connected to the carrier 1404 of the tandem planetary gear set 1400, and the output torque of the TV control motor 1002 can be transmitted to the tandem planetary gear set 1400 through the carrier 1404. The stator of the TV control motor 1002 and its housing are fixed to the driving axle housing.
The tandem planetary gear train 1400 mainly includes a first sun gear 1401, three pairs of circumferentially distributed tandem planetary gears 1402, a second sun gear 1403 and a carrier 1404. The double planetary gear 1402 mainly comprises a first end planetary gear 1405 and a second end planetary gear 1406, which are fixedly connected and can be integrally processed. Wherein a first sun gear 1401 is splined to a first half shaft 1301 and a second sun gear 1403 is fixedly connected to a differential housing 1308 for rotation with the differential housing 1308.
It should be noted that, a reduction mechanism may be formed by adding a gear transmission between the TV control motor 1002 and the double planetary gear train 1400 to amplify the torque output by the TV control motor 1002, so adding any form of reduction mechanism, clutch or torque converter between the TV control motor 1002 and the double planetary gear train 1400 cannot be a substantial innovation to the present invention.
The bevel gear differential mechanism 1300 is mainly composed of a first half shaft 1301, a second half shaft 1302, a first half shaft gear 1303, a second half shaft gear 1304, two conical planetary gears 1305 and 1306, a planetary gear shaft 1307, and a differential case 1308. Wherein the first half shaft gear 1303 is spline-connected to the first half shaft 1301 connecting the left wheel. The second side gear 1304 is spline-connected to a second half shaft 1302 that connects the right-side wheels, and the first half shaft 1301 and the second half shaft 1302 are respectively penetrated out from the center holes on both sides of the differential case 1308 and rotatably supported on the differential case 1308, and finally power is output to the left-and right-side wheels through constant velocity joints (not shown in the figure). The differential housing 1308 rotatably supports the transaxle housing, and the left end face of the differential housing 1308 is fixedly connected to the second output driven gear 1302. A pinion shaft 1307 is rotatably supported on the differential case 1308 through the center of the differential case 1308, and two conical pinion gears 1305 and 1306 are installed in the middle thereof. Two conical planetary gears 1305 and 1306 are arranged face to face on both sides of the center of the differential, and are externally meshed with a first side gear 1303 and a second side gear 1304 arranged on both left and right sides thereof, respectively.
The main driving motor reduction mechanism 1000 is located on the right side of the drive axle and is mainly composed of a first planetary gear train 1100 and a second planetary gear train 1200. The first planetary gear system 1100 includes a first ring gear 1101, three first planetary gears 1102 uniformly distributed around the circumference, a third sun gear 1103, and a second planet carrier 1104. Wherein the first ring gear 1101 is fixed on the drive axle housing, the third sun gear 1103 is rotatably supported on the second half shaft 1302 and fixedly connected to the third planet carrier 1204 of the second planetary gear train 1200, and the second planet carrier 1104 is fixedly connected to the differential housing 1308. The second planetary gear train 1200 comprises a second annular gear 1201, three second planetary gears 1202 uniformly distributed on the circumference, a fourth sun gear 1203 and a third planetary gear 1204. With the second ring gear 1201 fixed to the drive axle housing and the fourth sun gear 1203 rotatably supported on the second half shaft 1302 and splined to the hollow inner rotor shaft of the main drive motor 1001.
It is preferred that the main drive motor reduction mechanism 1000 be formed of a single row planetary gear train, a multiple row planetary gear train, or other form of reduction mechanism, and thus changing the form of the main drive motor reduction mechanism 1000 is not considered an innovation of the present invention.
The main drive motor 1001 is located on the right side of the main drive motor reduction mechanism 1000, which is a hollow shaft inner rotor motor, and the second half shaft 1302 connected to the right wheel passes out of the hollow rotor shaft inner hole thereof. The hollow shaft inner rotor is in spline connection with the sun gear 1203 of the second planetary gear train 1200, and the main driving motor 1001 can transmit driving torque to the main driving motor reduction mechanism 1000 through the sun gear 1203, and acts on the differential case 1308, and finally is equally divided onto the first half shaft 1301 and the second half shaft 1302, so as to drive the automobile to run. The hollow inner rotor of the main driving motor 1001 is rotatably supported on the second half shaft 1302, and the stator and the housing thereof are fixedly connected with the driving axle housing.
The working principle is as follows:
Taking the schematic structural diagram of the embodiment of the electric drive axle based on torque directional distribution of the dual-rotor motor as shown in fig. 1 as an example, the working principle is described.
(1) When the automobile works in a normal straight running condition and has no torque distribution requirement, a control signal is not generated in the TV control motor 1002, the TV control motor is not started, the automobile is only driven by the main driving motor 1001, the torque output by the main driving motor 1001 is increased to act on the differential case 1308 through the speed reducing mechanism 1000 of the main driving motor, and the torque acted on the differential case 1308 is equally divided to the first half shaft 1301 and the second half shaft 1302 due to the principle of equally dividing the torque of the bevel gear differential 1300, so that the automobile is driven to run. At this time, since the vehicle travels straight, the rotational speeds of the left and right wheels are the same, and thus the rotational speeds of the first half shaft 1301, the second half shaft 1302, and the differential case 1308 are the same. Further, since the first sun gear 1401 of the double planetary gear train 1400 is spline-connected to the first half shaft 1301, the first sun gear 1401 has the same rotation speed as the first half shaft 1301. Since the second sun gear 1403 of the double planetary gear train 1400 is fixedly connected with the differential case 1308, the rotation speed of the second sun gear 1403 is the same as that of the differential case 1308, so that the rotation speeds of the first sun gear 1401 and the second sun gear 1403 of the double planetary gear train 1400 are the same, and the rotation speed formula of the double planetary gear train is as follows:
Wherein n PC is the rotation speed of the planet carrier of the duplex planetary gear train, n S1 is the rotation speed of the first sun gear, n S1 is the rotation speed of the first sun gear, r 1 is the pitch circle radius of the first sun gear, r 2 is the pitch circle radius of the first end planetary gear, r 3 is the pitch circle radius of the second end planetary gear, r 4 is the pitch circle radius of the second sun gear, and the relation between the transmission ratio of the first sun gear 1401 to the first end planetary gear 1405 and the transmission ratio of the second sun gear 1403 to the second end planetary gear 1406 must be satisfied
As can be seen from the above rotation speed formula, when the rotation speeds of the first sun gear 1401 and the second sun gear 1403 of the double planetary gear train 1400 are the same, i.e., n S1＝nS2, there is n PC＝nS1＝nS2, i.e., the rotation speed of the carrier 1404 is the same as the rotation speeds of the first sun gear 1401 and the second sun gear 1403, and at this time, the first end planetary gear 1405 and the second end planetary gear 1406 do not rotate but revolve at the same speed as the two sun gears. Further, since the carrier 1404 is fixedly connected to the inner rotor of the TV control motor, the rotation speed of the inner rotor of the TV control motor is the same as the rotation speeds of the first sun gear 1401 and the second sun gear 1403 and the rotation speed of the first half shaft 1301, and the TV control motor 1002 idles with the following operation, but does not start or output torque. The torque distribution flow is shown in fig. 2.
(2) When the automobile normally turns at a differential speed, the driving torques of the wheels at the left and right sides are the same, and torque distribution is not needed, so that the TV control motor 1002 does not have a control signal, the TV control motor is not started, no torque is output, the torque output by the main driving motor 1001 is added to the differential case 1308 through the speed reducing mechanism 1000 of the main driving motor, and the torque is equally distributed to the first half axle 1301 and the second half axle 1302 to drive the automobile to run. The torque distribution flow is also shown in fig. 2.
(3) When the vehicle is operated under the condition that the driving torque is distributed from the second half shaft 1302 to the first half shaft 1301, if the rotation direction of the wheels is set to be positive when the vehicle is running forward, the rotation direction is set to be negative otherwise. At this time, the TV control motor 1002 is started by receiving the control signal, and starts to output torque to the outside.
The conservation of power from the input into the duplex planetary gear train is available:
T PCnPC+TS1nS1+TS2nS2 =0 (2), where T PC is torque externally input into the carrier of the tandem planetary gear train, T S1 is torque externally input into the first sun gear, T S2 is torque externally input into the second sun gear, n PC is the rotational speed of the carrier of the tandem planetary gear train, n S1 is the rotational speed of the first sun gear, and n S1 is the rotational speed of the first sun gear. The torque formula of the duplex planetary gear train can be deduced from the formula (1) and the formula (2) as follows:
Where r 1 is the first sun pitch radius, r 2 is the first end planet pitch radius, r 3 is the second end planet pitch radius, and r 4 is the second sun pitch radius.
If the TV control motor output torque is T 0(T0 positive), the torque input into the first half shaft 1301 through the first sun gear 1401 of the double planetary gear train 1400 is the torque as obtained by the torque formula shown in the formula (3)Torque input into differential housing 1308 through second sun gear 1403 is/>By the principle of equally dividing the torque by the bevel differential mechanism 1300, the torque acting on the differential case 1308 is equally divided to the first half shaft 1301 and the second half shaft, and therefore, the torque obtained by the first half shaft 1301 is the sum of the torque input by the first sun gear 1401 and the torque input by the bevel differential mechanism 1300, and the result is/>The torque available from the second half shaft 1302 is the torque input by the bevel gear differential 1300, and as a result/>Torque increase of first half shaft 1301/>Torque reduction/>, of the second half-shaft 1302The distribution of drive torque from the second half shaft 1302 to the first half shaft 1301 is achieved. In designing the duplex planetary gear train 1400, the transmission ratio/>, of the first sun gear 1401 and the first end planetary gear 1405, is reasonably designedRatio with second sun gear 1403 and second end planet gear 1406/>Relationship between them such that/>And/>When the amounts of torque change in the first half shaft 1301 and the second half shaft 1302 are substantially the same but are not substantially the same, the torque can be distributed from the second half shaft 1302 to the first half shaft 1301 while maintaining the total driving torque in the vehicle longitudinal direction substantially unchanged. The torque distribution flow is shown in fig. 3.
(4) When the vehicle is operated under the condition that the driving torque is distributed from the first half shaft 1301 to the second half shaft 1302, if the rotation direction of the wheels is set to be positive when the vehicle is running forward, the rotation direction is set to be negative otherwise. At this time, the TV control motor 1002 is started by receiving the control signal, and starts to output torque to the outside. Similarly, if the TV control motor output torque is positive for-T 0(T0), the torque input into the first half shaft 1301 through the first sun gear 1401 of the tandem planetary gear train 1400 is as follows, which is obtained by the torque formula shown in formula (3)Torque input into differential housing 1308 through second sun gear 1403 is/>By the principle of equally dividing the torque by the bevel differential mechanism 1300, the torque acting on the differential case 1308 is equally divided to the first half shaft 1301 and the second half shaft, and therefore, the torque obtained by the first half shaft 1301 is the sum of the torque input by the first sun gear 1401 and the torque input by the bevel differential mechanism 1300, with the result thatThe torque available from the second half shaft 1302 is the torque input by the bevel gear differential 1300, and as a result/>Torque reduction of first half shaft 1301Torque increase of the second half shaft 1302/>The distribution of drive torque from the first half shaft 1301 to the second half shaft 1302 is achieved. In designing the duplex planetary gear train 1400, the transmission ratio/>, of the first sun gear 1401 and the first end planetary gear 1405, is reasonably designedRatio with second sun gear 1403 and second end planet gear 1406/>Relationship between them such that/>And/>When the amounts of torque change in the first half shaft 1301 and the second half shaft 1302 are substantially equal but not equal, the torque can be distributed from the first half shaft 1301 to the second half shaft 1302 while maintaining the total driving torque in the vehicle longitudinal direction substantially unchanged. The torque distribution flow is shown in fig. 4.
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 (8)
1. A twin planetary gear train torque directional distribution electric drive axle, comprising:
The main driving motor is a hollow shaft type inner rotor motor and is arranged at one side of the driving axle, and a power output shaft of the main driving motor is connected with the bevel gear differential shell through a speed reducing mechanism;
Wherein a first half shaft is rotatably supported on the housing and connected through the housing to a first side gear of the bevel gear differential and a second half shaft is rotatably supported on the housing and connected through the housing to a second side gear of the bevel gear differential; the second half shaft penetrates out of an inner hole of the hollow rotor shaft of the main driving motor to be connected with a right wheel;
The TV control driving motor is a hollow shaft type inner rotor motor and is used for realizing directional distribution of driving torque on the first half shaft and the second half shaft as a power source, the motor is arranged on the other side of the driving axle, and the first half shaft penetrates out of an inner hole of a hollow rotor shaft of the motor to be connected with a left wheel;
The double planetary gear train comprises a first sun gear, a second sun gear, a first end planetary gear, a second end planetary gear and a first planet carrier;
The first sun gear is connected with the first half shaft, and the second sun gear is rotatably supported on the first half shaft and fixedly connected with the bevel gear differential shell; the first end planetary gear and the second end planetary gear are coaxially arranged on a planetary shaft, and the planetary shaft is connected with a power output shaft of the TV control driving motor through the first planet carrier; the transmission ratio r 2/r1 of the first sun gear and the first end planetary gear and the transmission ratio r 3/r4 of the second sun gear and the second end planetary gear are close to each other but not equal, namely r 2/r1≠r3/r4;
Wherein r 1 is the first sun gear pitch circle radius, r 2 is the first end planet gear pitch circle radius, r 3 is the second end planet gear pitch circle radius, and r 4 is the second sun gear pitch circle radius.
2. The dual planetary gear train torque vectoring electric drive axle of claim 1 wherein the first end planets are evenly circumferentially arranged around and engaged with the first sun and the second end planets are evenly circumferentially arranged around and engaged with the second sun.
3. The dual planetary gear train torque vectoring electric drive axle as claimed in claim 2, wherein,
The bevel gear differential further includes:
A planetary gear shaft passing through the center of the bevel gear differential housing and rotatably supported on the bevel gear differential housing;
a first conical planetary gear fixedly mounted on the planetary gear shaft and simultaneously externally engaged with the first side gear and the second side gear;
a second conical planetary gear fixedly mounted on the planetary gear shaft and simultaneously externally engaged with the first side gear and the second side gear;
The first conical planetary gear and the second conical planetary gear are symmetrically arranged.
4. The dual planetary gear train torque vectoring electric drive axle of claim 3 wherein the first half axle and the second half axle each extend through central bores on either side of the bevel gear differential housing and are rotatably supported on the housing.
5. The dual planetary torque vectoring electric drive axle of claim 4 wherein the bevel gear differential housing is rotatably supported on the drive axle housing.
6. The twin planetary gear train torque vectoring electric drive axle of claim 1 or 2, wherein the reduction mechanism comprises:
the first single-row planetary gear train comprises a third sun gear, a first planet gear, a second planet carrier and a first gear ring; the first gear ring is fixed on a driving axle shell, the third sun gear is rotatably supported on a second half shaft, and the second planet carrier is fixedly connected with the shell of the bevel gear differential mechanism;
The second single-row planetary gear train comprises a fourth sun gear, a second planet gear, a third planet carrier and a second gear ring; the fourth sun gear is rotatably supported on the second half shaft and is in spline connection with a power output shaft of the main driving motor, the second gear ring is fixed on the driving axle shell, and the third planet carrier is fixedly connected with the third sun gear.
7. The dual planetary gear train torque vectoring electric drive axle of claim 1 wherein the TV-controlled drive motor is a hollow-shaft inner rotor motor comprising:
a rotor fixedly connected to the power output shaft;
and the stator is fixedly connected with the TV control driving motor shell.
8. The dual planetary gear train torque vectoring electric drive axle of claim 1 wherein the housing of the TV control drive motor is fixedly connected to the drive axle housing and the housing of the main drive motor is fixedly connected to the drive axle housing.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810203457.0A CN108297619B (en) | 2018-03-13 | 2018-03-13 | Electric drive axle for directional torque distribution of duplex planetary gear train |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810203457.0A CN108297619B (en) | 2018-03-13 | 2018-03-13 | Electric drive axle for directional torque distribution of duplex planetary gear train |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108297619A CN108297619A (en) | 2018-07-20 |
| CN108297619B true CN108297619B (en) | 2024-04-19 |
Family
ID=62849820
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810203457.0A Active CN108297619B (en) | 2018-03-13 | 2018-03-13 | Electric drive axle for directional torque distribution of duplex planetary gear train |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108297619B (en) |
Families Citing this family (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109774452B (en) * | 2019-03-04 | 2024-04-12 | 吉林大学 | Bevel gear type oil-electricity series-parallel hybrid power system |
| CN114537045B (en) * | 2022-03-28 | 2024-02-27 | 重庆嘉陵全域机动车辆有限公司 | Coaxial electric drive axle assembly with self-locking and disengaging functions and working method |
| CN116494743B (en) * | 2023-06-12 | 2024-04-16 | 中国重汽集团济南动力有限公司 | Electric drive axle system and car |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5409425A (en) * | 1992-02-10 | 1995-04-25 | Honda Giken Kogyo Kabushiki Kaisha | Torque distributing mechanism in differential |
| CN2644191Y (en) * | 2003-08-09 | 2004-09-29 | 上汽集团奇瑞汽车有限公司 | Front axle of four-wheel driven car |
| CN1727730A (en) * | 2004-07-29 | 2006-02-01 | 迪姆肯公司 | Differential with torque vectoring capabilities |
| CN103770623A (en) * | 2014-02-20 | 2014-05-07 | 合肥工业大学 | Gasoline-electric and hydraulic compound hybrid power transmission system |
| CN104827898A (en) * | 2015-05-11 | 2015-08-12 | 合肥工业大学 | Two-gear speed changing power system of electric automobile |
| CN104842781A (en) * | 2015-06-17 | 2015-08-19 | 清华大学苏州汽车研究院（相城） | Middle-engine integrated electric bridge with driving force distribution function |
| CN205632081U (en) * | 2016-05-30 | 2016-10-12 | 福建工程学院 | Electricelectric moves vehicle power assembly |
| CN106809054A (en) * | 2017-01-25 | 2017-06-09 | 吉林大学 | A kind of torque fixed direction allocation electric drive axle method for designing |
| CN106965659A (en) * | 2017-04-21 | 2017-07-21 | 吉林大学 | A kind of bi-motor coupling driving bridge with torque fixed direction allocation function |
| CN107061677A (en) * | 2017-04-21 | 2017-08-18 | 吉林大学 | A kind of electric differential mechanism with torque fixed direction allocation function |
| CN207916462U (en) * | 2018-03-13 | 2018-09-28 | 吉林大学 | A kind of duplex planet train torque fixed direction allocation electric drive axle |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012208926B4 (en) * | 2012-05-29 | 2020-03-12 | Schaeffler Technologies AG & Co. KG | Electric axle for a vehicle |
| US8998764B2 (en) * | 2013-03-13 | 2015-04-07 | E-Aam Driveline Systems Ab | Drive module having planetary transmission with nested ring gears |
-
2018
- 2018-03-13 CN CN201810203457.0A patent/CN108297619B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5409425A (en) * | 1992-02-10 | 1995-04-25 | Honda Giken Kogyo Kabushiki Kaisha | Torque distributing mechanism in differential |
| CN2644191Y (en) * | 2003-08-09 | 2004-09-29 | 上汽集团奇瑞汽车有限公司 | Front axle of four-wheel driven car |
| CN1727730A (en) * | 2004-07-29 | 2006-02-01 | 迪姆肯公司 | Differential with torque vectoring capabilities |
| CN103770623A (en) * | 2014-02-20 | 2014-05-07 | 合肥工业大学 | Gasoline-electric and hydraulic compound hybrid power transmission system |
| CN104827898A (en) * | 2015-05-11 | 2015-08-12 | 合肥工业大学 | Two-gear speed changing power system of electric automobile |
| CN104842781A (en) * | 2015-06-17 | 2015-08-19 | 清华大学苏州汽车研究院（相城） | Middle-engine integrated electric bridge with driving force distribution function |
| CN205632081U (en) * | 2016-05-30 | 2016-10-12 | 福建工程学院 | Electricelectric moves vehicle power assembly |
| CN106809054A (en) * | 2017-01-25 | 2017-06-09 | 吉林大学 | A kind of torque fixed direction allocation electric drive axle method for designing |
| CN106965659A (en) * | 2017-04-21 | 2017-07-21 | 吉林大学 | A kind of bi-motor coupling driving bridge with torque fixed direction allocation function |
| CN107061677A (en) * | 2017-04-21 | 2017-08-18 | 吉林大学 | A kind of electric differential mechanism with torque fixed direction allocation function |
| CN207916462U (en) * | 2018-03-13 | 2018-09-28 | 吉林大学 | A kind of duplex planet train torque fixed direction allocation electric drive axle |
Non-Patent Citations (1)
| Title |
|---|
| 黄茂林.《机械原理》.机械工业出版社,2010,215-217. * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108297619A (en) | 2018-07-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN108297618B (en) | Electric drive axle for directional torque distribution of duplex planetary gear train | |
| US10814720B2 (en) | Centralized full-time electric four-wheel drive system | |
| CN106965661B (en) | Double-motor coupling drive axle with torque directional distribution function | |
| CN106965659B (en) | Dual-motor coupling drive axle with torque directional distribution function | |
| CN106965662B (en) | Dual-motor coupling drive axle with torque directional distribution function | |
| CN113400864B (en) | Multi-mode torque vectoring electric drive axle using one-way clutch | |
| CN113415107B (en) | Dual-mode electric drive axle capable of carrying out torque parallel connection and torque directional distribution | |
| CN107035846B (en) | Electric differential mechanism with torque directional distribution function | |
| CN108297620B (en) | Torque directional distribution electric drive axle based on double-rotor motor | |
| CN107013654B (en) | Electric differential mechanism with torque directional distribution function | |
| CN106979308B (en) | Electric differential mechanism with torque directional distribution function | |
| CN106870682B (en) | Electric differential mechanism with torque directional distribution function | |
| CN107420516B (en) | Electric differential mechanism with torque directional distribution function | |
| CN113696676B (en) | Torque directional distribution electric drive axle using planetary row plus double gear | |
| CN107035847B (en) | Electric differential mechanism with torque directional distribution function | |
| CN113103826B (en) | Torque directional distribution electric drive axle adopting double-planet-wheel cylindrical gear differential mechanism | |
| CN108297619B (en) | Electric drive axle for directional torque distribution of duplex planetary gear train | |
| CN107061681B (en) | Electric differential mechanism with torque directional distribution function | |
| CN107061682B (en) | Electric differential mechanism with torque directional distribution function | |
| CN107061675B (en) | Electric differential mechanism with torque directional distribution function | |
| CN107061676B (en) | Electric differential mechanism with torque directional distribution function | |
| CN207916462U (en) | A kind of duplex planet train torque fixed direction allocation electric drive axle | |
| CN107061683B (en) | Electric differential mechanism with torque directional distribution function | |
| CN107061677B (en) | Electric differential with torque directional distribution function | |
| CN106870683B (en) | Electric differential mechanism with torque directional distribution function |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |