Abstract:
A drive axle of electric distribution torque, comprise of: a drive motor having a output shaft for outputting torque; differential including differential housing, a drive shaft. the left and right drive half axle rotating about an axis of rotation; double row planetary gear mechanism outputting power of the motor output shaft which will be reduced two-stage; double planetary gear torque distribution mechanism connected to the double planetary gear reduction mechanism, receiving the double planetary gear reduction mechanism output torque, and outputs reverse torque in contrast to said torque; single row double planetary gear coupling mechanism providing opposite direction torque to the left and right axle. The electric drive axle with a torque orientation distribution function of the present invention can distribute the transmission of drive torque to both sides of the axles selectively, and when the torque is directional distributed, electric drive axle is willing to follow the best driver input, maintain driving speed cornering, increasing mobility and the driver&#39;s driving pleasure.

Description:
FIELD OF INVENTION 
       [0001]    The present invention belongs to the field of drive axle of automobile in particular to the electric distribution torque drive axle. 
       BACKGROUND OF THE INVENTION 
       [0002]    Drive axle is an important part of automotive driveline, mainly consisting of the main reducer, differential, drive shaft and drive axle shell. As the name implies, the electric drive axle is driven by a motor drive axle. The electric drive axle is an important power transmission unit of the electric car, and the torque directed dispenser is the most important feature of the torque orientation distribution function of the electric drive axle, by controlling the motor and the planetary gear mechanism to achieve the torque coupling of axle differential case and differential, enabling torque distribution between wheels. 
         [0003]    Automotive differentials are the main components of the drive axle, and differentials function is transmitting power in the car left and right axle, at the same time, allowing the drive shaft rotating at different speed, in order to satisfy both sides of the wheel as much as possible with the form of pure rolling, reducing tire friction in the ground. When the car turns, the wheel at the outside of the curve in the corners is faster than the inside wheel. Between the two sides of the drive wheel of the vehicle use a differential to compensate for the different speed of the drive wheel. However, the conventional differential usually evenly distributed torque between both sides of the driving wheel. However, in order to achieve optimum control of the vehicle, the drive wheels on the outside should be output greater torque than on the inside of the curve. In fact, increasing the drive wheels torque on the outside of in the corners can promote and guide the vehicle in turn, which is particularly useful when the high-speed cornering, and greatly reducing understeering, improving mobility and ultimate cornering ability, increasing driving fun. The differential of electric distribution torque is a important configuration with luxury sports car and SUV. 
         [0004]    In addition, the drive wheel may be on different roads with differential adhesion coefficient, namely off the road. In this case, if the adhesive force of the drive wheel is very small for example on ice, the average distribution torque characteristics of the conventional differential causes the side wheel acceleration skid, the other side wheel with the strong adhesion on the ground unable to obtain sufficient driving force so that does not run, then the car will break down, unable to rescue. Of course, anti-slip differential can effectively avoid the low-speed broke down problem, but when the car is on a good road and in high speed cornering, the kind of differential will make both sides wheels tend to the same speed, and limit increasing the torque and speed of the outer wheel, which increases insufficient cornering phenomenon, and limits the ability of the vehicle limit cornering. 
         [0005]    Therefore, base on the basis structure of the drive axle with the conventional bevel gear differential, designs a new electric drive axle having the ability of the torque directional distribution (TV: Torque Vectoring). 
       SUMMARY OF THE INVENTION 
       [0006]    The present invention design and develop a kind of electric drive axle of torque distribution function, to solve only evenly distributed defects of the wheel torque in the prior art, to achieve a torque directional distributed according need to the drive the right and left wheels. 
         [0007]    The present invention technical solutions are: 
         [0008]    A electric differential with a double row planetary gear having directional dispensing torque mechanism, comprising: 
         [0009]    a drive motor having a output shaft for outputting torque; 
         [0010]    a primary differential, comprising of a differential housing, a drive shaft, a first output shaft and the second output shaft rotating about an axis of rotation; said first output shaft and the second output shaft can rotate at the same or different speeds in the same rotation direction; 
         [0011]    a housing; and 
         [0012]    a reduction planetary gear train disposed within said housing, said a reduction planetary gear train connected to said drive motor&#39;s output shaft, receiving the output torque of said the motor output shaft and outputting the torque in the same torque direction; 
         [0013]    a coupled planetary gear set is connected to the reduction planetary gear train, receiving the output torque of the reduction planetary gear train, and outputting the reverse torque in contrast to said output torque; 
         [0014]    a double planetary gear train is connected to said the coupled planetary gear set, receiving the output torque of said the coupled planetary gear set; said double planetary gear train is connected with said main differential, providing said first output shaft and second output shaft torque in the opposite direction. 
         [0015]    Preferably, said reduction planetary gear train including a reduction sun gear, the reduction planetary and a reduction ring gear; said reduction sun gear motor is connected with the motor output shaft coaxially, with the motor output shaft for co-rotation; said the reduction ring gear fixed to said housing; said reduction planetary gear engagement the reduction sun gear and the reduction gear ring respectively, so that the reduction planetary gear and the motor output shaft revolute in the direction, and by reducing planetary carrier to which the reduction planetary gear connected output torque of the revolution. 
         [0016]    Preferably, said coupling planetary gear set comprising: 
         [0017]    a first planetary gear train comprises a first sun gear, a first planetary gear, a first ring gear, said the first ring gear and said the planet carrier is fixedly connected to receive the torque of reduction output planet carrier; said first planetary gear engaged with said first sun gear and the first ring gear respectively; the first carrier is connected to said first planetary gear; the first planet carrier and the first output shaft is connected fixedly; 
         [0018]    a second planetary gear train comprises a second sun gear, a second planetary gear, a second planetary carrier and a second ring gear; the second ring gear is fixedly connected with said housing; said second planetary gear engaged said second sun gear and the second ring gear respectively; the second planetary carrier is connected with the second planetary; 
         [0019]    wherein, the first sun gear and the second sun gear integrated manufacturing, which is connected with the first output shaft rotatably and coaxially. 
         [0020]    Preferably, the double planetary gear train includes a third sun gear, a third planetary gear, the fourth planetary gear, a third ring gear, said third sun gear is coaxially fixedly connected with said first output shaft; said third ring gear is fixedly connected with said differential case; said third sun gear, a third planetary gear the fourth planetary gear, and a third ring gear meshing engaged in turn; the third planetary gear, the fourth planetary gear are respectively connected with the second planetary carrier, to receive the transmissing torque of the second planetary carrier. 
         [0021]    Preferably, said first sun gear and the second sun gear, the first planetary gear and the second planetary gear, a first ring gear and the second ring gear have the same pitch circle structure. 
         [0022]    Preferably, the second ring gear formed integrally with said housing. 
         [0023]    Preferably, the third ring gear formed integrally with the differential case. 
         [0024]    A drive axle of electric distribution torque, comprising: 
         [0025]    a drive motor having a output shaft for outputting torque; 
         [0026]    a planetary gear reduction mechanism receiving the torque of torque distribution control motor&#39;s output shaft, and reducing the speed and increasing the torque; 
         [0027]    a torque distribution mechanism connected to said planetary gear reduction mechanism, receiving the torque of the planetary gear reduction mechanism, and outputting the reverse torque in contrast to said torque; 
         [0028]    a planetary gear coupling mechanism, comprising:
       a carrier receiving said reverse torque of the torque distributing mechanism;   a ring gear is fixedly connected with the differential housing, and the ring gear and the differential housing can rotate together;   a sun gear is fixedly connected with drive half axle.       
 
         [0032]    Preferably, the planetary gear mechanism comprises a parallel arrangement of the left deceleration planetary gear train and right deceleration planetary gear train, which have a common ring gear fixed on the drive axle housing, said carrier of left deceleration planetary gear train and said sun gear of right deceleration planetary gear train fixedly connected, said the sun gear of left deceleration planetary train and the output shaft of torque distribution control motor fixedly connected; the carrier of right deceleration planetary gear train output power. 
         [0033]    Preferably, the torque distribution mechanism is the double row planetary gear torque distribution mechanism, including a left torque distribution planetary gear train and the right torque distribution planetary gear train having a common sun gear, said the common sun gear rotatably sleeved on said drive half axle, said ring gear of left torque distribution planetary gear train fixed connection with the carrier of right deceleration planetary gear train, the carrier of the left torque distribution planetary gear train connecting fixed said drive half axle, said ring gear of right torque distribution planetary gear train is stationary, a carrier of right torque distribution planetary gear train output power. 
         [0034]    Preferably, the planetary gear coupling mechanism is a single row of double planetary gear train, the double planetary gear train comprises: 
         [0035]    a common carrier connected with said carrier of right torque distribution planetary gear fixedly; two intermeshing planet gears shared said the common carrier; 
         [0036]    a ring gear is fixedly connected with the differential housing, and the ring gear and the differential housing can rotate together; 
         [0037]    a sun gear is fixedly connected with drive half axle. 
         [0038]    Preferably, said left and right deceleration planetary gear reduction train having the same configuration parameters. 
         [0039]    Preferably, the motor output shaft has an axial through hole, said drive half axle through said axial through hole. 
         [0040]    A drive axle of electric distribution torque, comprising 
         [0041]    a drive motor having a output shaft for outputting torque; 
         [0042]    a torque distribution mechanism connected to said planetary gear reduction mechanism, receiving the torque of the planetary gear reduction mechanism, and outputting the reverse torque in contrast to said torque; 
         [0043]    a single row double planetary gear coupling mechanism connected double planetary gear torque distribution mechanism, receiving the reverse torque of the double planetary gear torque distribution mechanism, and providing additional torque to the drive half axle and the differential housing. 
         [0044]    Preferably, the motor output shaft has an axial through hole, said drive half axle through said axial through hole. 
         [0045]    Preferably, the torque distribution mechanism is the double row planetary gear torque distribution mechanism, including a left torque distribution planetary gear train and the right torque distribution planetary gear train having a common sun gear, said the common sun gear rotatably sleeved on said drive half axle, said ring gear of left torque distribution planetary gear train fixed connection with the carrier of right deceleration planetary gear train, the carrier of the left torque distribution planetary gear train connecting fixed said drive half axle, said ring gear of right torque distribution planetary gear train is stationary, a carrier of right torque distribution planetary gear train output power. 
         [0046]    Preferably, said single row of double planetary gear train having two intermeshing planet gears which use a common planet carrier, said common planet carrier is connected with said the carrier of right torque distribution planetary gear train fixedly. 
         [0047]    Preferably, said left and right deceleration planetary gear train having the same configuration parameters. 
         [0048]    Preferably, said the ring gear of right torque distribution planetary gear train and the drive axle housing are integrally forming. 
         [0049]    Preferably, the third ring gear formed integrally with the differential case. 
         [0050]    The beneficial effects of the present invention are: 
         [0051]    1, Electric drive axle with a torque orientation distribution function of the present invention can distribute the transmission of drive torque to both sides of the axle selectively, and when the torque is distributed, electric drive axle is willing to follow the best driver input, maintain driving speed cornering, increase mobility and the driver&#39;s driving pleasure. 
         [0052]    2, Using a double planetary gear mechanism can be simultaneously both torque coupling function and deceleration function, reduce torque demand of TV motor. Torque distribution control motor can be arranged coaxially, and the motor is not rotating when torque distribution does not follow. Only when active torque distribution is required, the motor rotate to provide directional distribution of torque, which makes for motor selection matching program easily, saving energy and wear, compact, small footprint. 
         [0053]    3, Only a torque distribution control motor can be directed to achieve rationing, compact structure, easy to control, that is, just to control rotor of torque distribution control motor forward and reverse can be oriented output torque distribution on the left and right drive shaft, so you can control the left and right axle torque difference. While the other based on the clutch or brake with differential gear coupled need have two sets of clutch or brake as a power source simultaneously, too many parts, complex structure, and the power consumption large. 
         [0054]    4, The present invention is wide range of applications. Although the present invention is designed in accordance with the electric drive axle, but if the composition of the traditional internal combustion engine and transmission powertrain replaces to drive motor of the present invention, so that the device can also be applied to a conventional power source car. 
         [0055]    5, Since the present invention improve the design of the existing foundation cone structure commonly used on gear differential, it has a low cost of the transformation process, the manufacturing process and process inherit good features. 
     
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         [0056]      FIG. 1 : the overall construction of the drive axle of the present invention having power torque orientation distribution function. 
           [0057]      FIG. 2 : a partial cross-sectional view of the dual planetary gear mechanism coupled to a single row. 
           [0058]      FIG. 3 : a partial expanded view of a single row of double planetary gear mechanism. 
           [0059]      FIG. 4 : a axial expanded of the drive axle of the present invention having power torque orientation distribution function. 
           [0060]      FIG. 5 : a three-dimension expanded view of a single row of double planetary gear coupling mechanism and double planetary gear torque distribution mechanism. 
           [0061]      FIG. 6 : a expanded view of a double-row planetary gear mechanism and the planetary gear mechanism of the torque distribution at the right side member. 
           [0062]      FIG. 7 : a expanded view of a double-row planetary gear mechanism and the planetary gear mechanism of the torque distribution at the left side member. 
           [0063]      FIG. 8 : a axial expanded view of a torque distribution control motor. 
           [0064]      FIG. 9 : a axial expanded view of a differential and main reducer. 
           [0065]      FIG. 10 : a schematic diagram of the drive axle of the present invention having power torque orientation distribution function. 
           [0066]      FIG. 11 : a schematic diagram of power flow of the drive axle of the present invention having power torque orientation distribution function when the car is straight. 
           [0067]      FIG. 12 : a schematic diagram of power flow of the drive axle of the present invention having power torque orientation distribution function when the car turns right. 
       
    
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
       [0068]    Below in conjunction with the accompanying drawings of the present invention will be further described in detail so as to enable those skilled in the reference implement according to the instruction text. 
         [0069]    Shown in  FIG. 1  and  FIG. 4 , the present invention provides a electric drive axle having an orientation distribution function, including a drive motor  1036 , the main reducer, differential  1019 , directional torque dispenser  1040 , drive axle housing. 
         [0070]    The main reducer promote the driving torque of motor  1036  amplify, and then by the differential  1019  torque distribution to the car left axle  1061  and right axle  1027 . The inner splines of left axle  1061  on the left end connect to external splines of the end of left shaft  1076  of the left flange, and drive torque transmit to left axle  1076  of the left flange, thus, which makes both sides of the wheel rotation. The electric drive axle according to the present invention, since the differential is provided with directed dispenser  1040 , has a torque output to the left and right drive half shaft  1076 ,  1027  conditions on the ability to selectively assign torque according that the right and left wheel occur torque unequal distribution range, the driving torque difference. The difference increase torque on the vehicle&#39;s ultimate driving ability to effectively adjust the car&#39;s driving posture. 
         [0071]    Shown in  FIG. 1  and  FIG. 4 , the left side of drive motor  1036  is positioned, and the output shaft  1036   b  is the inner spline permanent magnet synchronous motor, which is vehicle power source. The axis of motor parallel to the axle axis arranged to save space. Driving motor  1036  is fixedly connected in the right end of the drive axle housing by 12 circumferentially uniform bolt  1037 , and by the left side surface of drive motor with the convex circular spigot position. Driving motor  1036  is disposed in the left side of the right drive axle to balance the weight of the orientation torque dispenser, to balance of the bridge on both sides of the wheel load. 
         [0072]    Shown in  FIG. 4 , the main reducer is a two-stage helical gear reducer, which includes a first shaft  1021   b  of reducer, a drive gear  1021   a , a second shaft  1025  of reducer, a first stage driven gear  1041 , two stage active gear  1042  and two stage ring driven gears  1111 . The end of main gear first shaft  1021   b  by a spline connected to the output shaft  1036  of drive motor, and using a pair of tapered roller bearings  1020 , 1022  face to face support in the drive axle main housing  1030  and the right end cover  1031  of drive axle. At the right end  1022  of cone roller bearings, the sink holes at right end face of the drive axle&#39;s right end cap is disposed lip seals  1023 , which are arranged on the plain shaft of the journal at the right end of main gear first shaft  1021 , to achieve the drive axle housing lubricating oil sealed in vivo. Said primary drive gear  1021   a  is a helical cylindrical gear, in fact, primary drive gear  1021   a  formed a main reducer first shaft  1021   b  integral, the main reducer first shaft  1021  is a whole gear shaft. The primary driven gear  1041  is a helical cylindrical gear, which is connected with the main reducer second shaft  1025  by the flat key. The secondary drive gear  1042  is a helical cylindrical gear, which is connected with the main reducer second shaft  1025  by the flat keys, and engaged the second ring gear  1111  fixed to the left end of the flange on the differential case. Two ends of the main reducer second shaft  1025  are supported on drive axle housing  1030  and the axle right end cap  1031  by a pair of facing installation taper roller bearings  1024 ,  1026 . 
         [0073]    Shown in  FIG. 1 ,  FIG. 4 ,  FIG. 9 , differential  1019  is a conventional bevel gear differential including differential case  1112 , two left and right half shaft bevel gears  1116  and  1124 , two half shaft gears thrust washer  1115  and  1125 , spring pins  1121  and  1123 , planetary gear shaft  1118 , two cones planetary gears  1119  and  1122 , and two planetary gear spherical washer  1117  and  1120 . Said differential case  1112  is a unitary housing; there are two square windows open easy to install and input the oil lubrication. Main reducer two stage driven gear  1111  connection with the differential housing  1112  left circular flange by six bolts  1110 , spring washers  1113  and hex nuts bolt  1114 . The differential housing  1112  interior cavity load left half shaft gears  1116 , the left half shaft gear thrust washer  1115 , and right half shaft gears  1124 , the right half shaft gear thrust washer  1125 , the up planetary gears  1122 , the up planetary gear spherical sheet  1117 , down the planetary gears  1119 , down planetary gear spherical shaft washer  1120  and the planetary gear shaft  1118 , and the left and right half shaft gears  1116 ,  1124  are mounted on both sides of the differential case  1112  lumen, and at the same time up planetary gears  1122  and down the planetary gears  1119  mesh with each other. The both ends of said planetary gear shaft  1118  installed the up planetary gear  1122 , the down planetary gear spherical washer  1117  and the down planetary gears  1119 , down the planetary gear spherical washer  1120 , and by the up spring pins  1123  and down flexible cylindrical pin  1121  fixed to the differential case  1112 . Two ends of the main reducer  1019  are supported on drive axle housing  1030  and the drive axle right end cap  1031  by a pair of facing installation taper roller bearings  1017 ,  1028 . 
         [0074]    When the driving motor  1036  is working, the output shaft  1036   b  of the drive motor  1036  transfer driving torque to a main reducer first gear shaft  1021 , and by one stage reduction gear and two stage reduction gear of the main reducer, the amplified drive torque is transmitted to the differential case  1112 ; differential case  1112  will be the rotated about its axis, thereby the planetary gear shaft  1118  bring the up planet gear  1122  and the down planet gear  1119  on its revolves around the axle axis. Since the teeth engaging relationship, meshing with the left and right half shaft gears  1116 , 1124  rotate about the axle axis simultaneously, and then driving torque average assigned to the left half shaft  1061  and the right half shaft  1027  spline connected the left and right half shaft gears  1116 , 1124 , driving the vehicle. When the left half shaft  1061  and right half shaft  1027  are different speed, for example, when the vehicle turns, the upper and lower planetary gears  1122 ,  1119  will be revolution while rotating about the planetary gear shaft  1118 , but also the driving torque approximate average passed to the left and right half drive shaft gears  1116 , 1124 , and its spline were connected with left half shaft  1061  and right half shaft  1027 , driving the vehicle. 
         [0075]    Shown in  FIG. 1 ,  FIG. 4 , the torque directed dispenser  1040  located on the left of drive axle, including a single row double planetary gear coupling mechanism  1014   b , double planetary gear torque distribution mechanism  1039 , double planetary gear torque reduction mechanism  1011   a , torque distribution control motor  1038 , etc. 
         [0076]    Shown in  FIG. 1 ,  FIG. 2 ,  FIG. 3  and  FIG. 5 , said a single row double planetary gear coupling mechanism  1014   b  includes a sun gear  1061   b , three pairs of planetary gears  1064  and  1056 , carrier  1057  and differential shell ring  1058  meshing with each other. Said the sun gear  1061   a  and left axle connected left half shaft gear  1061   b  formed integrally, therefore, the left axle connected left half shaft gear is actually a whole gear shaft  1061 . As shown in  FIG. 5 , due to the right end of the gear shaft  1061  is splines, which connect with the inner spline of left half shaft gear  1116  of differential case  1112 , so the sun gear  1061   b  of single row double planetary gear mechanism  1014   b  and the left half shaft gears  1116  within the differential housing  1112  synchronous rotation, the direct transferring drive torque from left half shaft supported on the differential. Shown in  FIG. 3  and  FIG. 5 , the ring gear  1058  of the differential case is one end of a ring gear and hollow shaft having external splines formed integrally to obtain. Shown in  FIG. 1 , external splines  1058  at the shaft end of ring gear of differential case connect to internal splines on the left side of the differential case  1112 , the inner wall is axially against on the right shoulder of the gear shaft  1061  connected to the left half shaft gears, in order to reduce the wear between them, install a liner in the shoulder  1059  at shoulder in the left the left half shaft  1061 . In addition, shown in  FIG. 5 , the bottom of ring groove associated differential housing ring gear  1058  is arranged an annular ring portion of the thrust needle roller bearing  1060  axially supported at a right end surface of the carrier  1056  to reduce the friction when the relative rotation. As shown in  FIG. 1 ,  FIG. 4  and  FIG. 5 , on the back of the differential case ring gear portion  1058  support on an annular ring groove needle roller thrust bearings  1016  embedded inside the left cavity  1030  of the drive axle housing, and to reduce friction during the relative rotation. In addition, shown in  FIG. 1 ,  FIG. 4 , the hollow shaft with external splines connected to the differential housing ring gear  1058  and drive axle housing  1030  left inside the cavity holes equipped with four lip seals  1018 , the drive axle housing  1030  about two cavities separated, to avoid the main gear oil in the right chamber mixing with lightweight gear oils of the left chamber. 
         [0077]    The three pairs of planetary gears meshing with each other are the inner and outer planet gears  1057 ,  1064 , which evenly mounted on between said sun gear  1061   b  and the differential case ring gear  1058 . Those are mounted the carrier  1056  together by a pin  1065 , 1066 , and their rotation around their pins, wherein the outer planetary gear  1057  engage with the differential housing ring gear  1058  without engaging with the sun gear  1061   b  Inner planetary gears  1064  meshing with the sun gear  1061   b  but without engaging with differential case ring gears  1058 , in addition, each pair of inner planet gears  1064  and outer planet gears  1057  assembly in pairs, and engaged with each other. Therefore, from the differential case  1112  drive torque transfer to the differential case ring gears  1058 , the driving torque on the differential case ring gears  1058  through the inner and outer planetary gears  1064  and  1057  is passed to the sun gear  1061   b , it is passed to the left half drive shaft  1061  with the left half shaft gears, that is, from the ring gear  1058  connected to the differential case transfer any drive torque on the sun gear  1061   b  will make the left drive shaft  1061  and right half shaft  1076  in the same direction of rotation with differential housing  1112  rotation direction. For each gear and size selection of the double planetary gear train  1014   b , select the appropriate parameters of the planetary row according to the maximum designed torque distribution ratio of the torque directed dispenser; then according to the size select the number of teeth of each gears primaries. 
         [0078]    Shown in  FIG. 1 ,  FIG. 5 ,  FIG. 4 , said double planetary gear torque distribution mechanism  1039  include share a long sun gear  1050  and the right torque distribution planetary gear train  1014   a  and left torque distribution planetary gear train  1011   b  having the same characteristic parameters planetary gear. 
         [0079]    Shown in  FIG. 1 ,  FIG. 5 , the right torque distribution planetary gear train  1014   a  comprise of said long sun gear  1050 , three planet gears  1055 , the ring gear  1056  and the planet carrier  1054 . Wherein said the long sun gear  1050  by the needle bearing  1053  placing in the right side of inside the hole is mounted on the left of half drive shaft journal  1061  with the half gears, so between the long sun gear  1050  and left half shaft with the half gears  1061  can be relatively rotated; Shown in  FIG. 1 ,  FIG. 4 , the inner ring  1054  interference fit manner fixedly connected the left side of the inner diameter of drive axle housing  1030 , and axially fixed with a hole with an elastic ring  1013 , so that the inner ring  1054  relative drive axle housing  1030  is not relative motion, if necessary, take welding ring gear  1054  connected to the drive axle housing  1030  to overcome the driving torque; said the three planetary gear  1055  mounted evenly between the long sun gear  1050  and the ring gear  1054 , and each rotation around the pin  1062  on the planetary carrier  1056 , simultaneously the three planetary gears  1055  respectively engages the long sun gear  1050  and the ring gear  1054 . The planet carrier  1056  is actually connected by a single row of double planetary gear coupling mechanism  1014   b  and the right torque distribution planetary gear  1014   a  of double planetary gear TV mechanism  1039  shared, both co-frame, so in fact, a single row double planetary gear coupling mechanism  1014   b  and the right torque distribution planetary gear  1014   a  of double planetary gear TV mechanism  1039  assembled into a unit  1014 . The middle of the carrier  1056  by empty sleeve bushing  1052  is supported on the second shoulder of the left half drive shaft  1061  with the left gears, the support of the left side by a copper washer  1051  abuts the right end surface of the long sun gear  1050 . In addition, the carrier  1056  the right end face by embedding to thrust needle roller bearings  1060  at the bottom of inner wall groove of the differential housing ring gear  1058  support at the bottom of the differential ring gear  1058 . The copper gaskets  1051 , bushings  1052 , and thrust needle roller bearings  1060  are used to reduce contact wear relative movement. 
         [0080]    Shown in  FIG. 1 ,  FIG. 6 ,  FIG. 7 , the left torque distribution planetary gear train  1011   b  comprise of said long sun gear  1050 , three planet gears  1082 , the ring gear  1075   b  and the planet carrier  1081 . The inner gear ring  1075   b  is connected to the planet carrier  1075   a  of the double planetary gear reducer  1011   a  right planetary gear train. In fact, the inner ring gear  1075   b  and double rows of the planetary gear deceleration mechanism  1011   a  right carrier  1075   a  form integral, which is a ring gear  1075  with the carrier, arranged in most left position of driving axle case  1030 , and the needle roller bearing  1079  support on the left end of the shaft neck of the planet carrier  1081 . The three planetary gear  1082  evenly installed between the sun gear  1050  and ring gear  1075   b , and their respective around a planet carrier  1081  pin  1083  rotation, three planetary gear  1082  respectively at the same time meshed with the long sun gear  1050  and ring gear  1075   b . Said the carrier  1081  left journal bore by the inner spline connect with left half shaft  1076  on the left side of the flange, the inner and outer side walls on both sides by anti-friction pads  1073 , 1080  are against the left side of long sun gear  1050  and right side of the inner wall of the inner ring  1075   b  respectively. Because the left half shaft  1076  on the left side of the flange and the left half shaft  1061  of half shaft gear by spline connected together. Therefore, the planet carrier  1081 , left half shaft  1076  with left flange, the left half shaft  1061  with left half shaft gear, differential left half axle gear  1116  and a left wheel connected together in synchronous rotation. 
         [0081]    As shown in  FIG. 1 ,  FIG. 6 ,  FIG. 7 ,  FIG. 8 , the double row planetary gear deceleration mechanism  1011   a  composed of share a ring gear  1070  and left and right planetary gears trains with the same planetary characteristics parameters, that is, left the deceleration planetary gear train and a right gear planetary gear train. 
         [0082]    Shown in  FIG. 1 ,  FIG. 6 ,  FIG. 7 , said the right deceleration planetary gear train comprise of said sun gear  1072   b , three planet gears  1074 , the planet carrier  1075   a  and the ring gear  1070 . Wherein, said the sun gear  1072   b  and the carrier  1072   a  of left deceleration planetary gear train formed integral, which by a needle bearing  1078  support on of the first section on the axis at the right end of left half drive shaft  1076  connected with left flange; Said the three planetary gear  1074  is uniformly arranged between the sun gear  1072   b  and the inner ring gear  1070 , and each rotating round planetary gear  1075   a  pin shaft  1085 , respectively with the sun gear  1072   b  and the inner gear ring  1070  meshing at the same time; Said planet carrier  1075   a  and the inner gear ring  1075   b  of left planetary gear train  1011   b  in double row planetary gear planetary gear TV mechanism  1039  formed integral, which is inner ring gear  1075  connected the carrier. The double row planetary gear reducer  1011   a  and left planetary gear  1011   b  in double row planetary gear planetary gear TV mechanism  1039  are together and became an independent member  1011 . The inner ring gear  1075  connected to planet carrier by needle roller bearings  1079  support on the planetary carrier  1081  of left planetary gear train  1011   b  in the double row planetary gear TV mechanism  1039 . In this way, the planetary carrier  1075   a  can relative planetary carrier  1081  rotate, that is, the planetary carrier  1075   a  can relatively rotate on the left half axle  1076  of left side flange. In addition, the planet carrier  1075   a  right end close to the planet rack  1081  left face of left planetary gear train  1011   b  in double rows planetary gear TV mechanism  1039 , in order to decrease wear and tear between the two relative motion caused, in both support added an antifriction spacer  1080 . In the gear ring  1070 , double rows planetary gear reducer  1011   a  and the planetary gear train share a ring gear. In the ring gear  1070  in over fit installed on the right side of the inside diameter in the driving bridge case  1008  and hole with circlip  1012  is axially fixed, so that the inner gear ring  1070  is not motion relative to the driving bridge left case  1008 , when necessary, adopt the welding mode is connected with an inner gear ring  1070  and driving bridge left case  1008 . 
         [0083]    Shown in  FIG. 1 ,  FIG. 7 ,  FIG. 8 , said the left deceleration planetary gear train comprise of said sun gear  1095   b , three planet gears  1071 , the planet carrier  1072   a  and the inner ring gear  1070 . Wherein, the sun gear  1095   b  and inner rotor  1095   a  of torque distribution control motor  1038  processed into one. By needle roller bearings  1077  support on the left half axle  1076  connected to the left side of the flange; Said the three planetary gear  1071  evenly installed between the sun gear  1095   b  and the inner gear ring  1070 , and respective rotate around the planet bracket  1072   a  pin  1084 , respectively meshed with the sun gear  1095   b  and the inner gear ring  1070  simultaneously; Said the inner gear ring  1070 , double rows planetary gear deceleration mechanism  1011   a  and the right planetary gear train share a inner gear ring, and which fixed on the driving bridge left shell inside. 
         [0084]    As shown in  FIG. 1 ,  FIG. 4  and  FIG. 8 , said the torque distribution control motor  1038  of torque direction distribution is a hollow shaft type internal rotor motor, which is composed of an inner rotor  1095  and a stator  1094 . Wherein, the torque distribution control motor  1038  is installed on the left cavity of drive axle left housing  1008 , the right end surface of the stator  1094  against rib plate in the inside of the drive left case axle  1008 , the left end surface of the stator  1094  fixed by 10 bolts  1043  and left end cap  1005  and paper gasket  1006  gluing together, relative to the drive axle so that it can not be movement relative to left case  1008 ; the left half shaft  1076  connected to the left flange disposed in by its right of double rows needle roller bearings  1093  at three sections of the smooth axis of the journal supported in the internal bore of the left end of the rotor  1095  within the torque distribution control motor  1038  the rotor  1095  can be rotate freely on left half shaft  1076  connected to the left flange. In fact, a sun gear  1095   b  of the left planetary gear train of double planetary gear mechanism  1011   a  in the torque directed dispenser  1040  and the rotor  1095   a  of torque distribution control motor  1038  formed integrally, to become an independent member  1095 . 
         [0085]    Shown in  FIG. 1 ,  FIG. 4 ,  FIG. 5 ,  FIG. 8 , said half shaft comprise of a left axle  1061  connected to the left half shaft gear, the left and right half shaft  1027   1076  connected to left flange. Among them, the right end of the left axle  1061  connected to left half shaft gears by splines connected with the left half shaft gears  1116 , which left by inner splines and external splines at the right end of left half shaft connected to the left flange, mutual support to each other; said left half shaft  1076  connected to the left side of the flange is a stepped hollow spline shaft, which right and left ends are the splines, the intermediate shaft consists of a shoulder, the smooth axis of three sections. The left half shaft  1076  connected to the left flange insert from the rotor  1095  hollow of the torque distribution control motor  1038 , the left half shaft  1076  connected to the left flange arranged in the right of the third paragraph smooth axis journal&#39;s the roll needle bearing  1093  is supported on the torque distribution control motor  1038  rotor  1095  left hole, needle roller bearings  1093  against the left half shaft shoulder  1076  connected to the left flange. The left half shaft  1076  connected to the left flange by external spline in the end of shaft engage inner spline of the left flange  1003 , and by the bolt head taper of left long bolt  1001  lock end of left half shaft  1076  connected to the left flange  1003  tightly. To prevent the left half shaft  1061  connected to left the half shaft gears, left half shaft  1076  connected to the left flange axially moving, said the left long bolt  1001  from the left flange  1003  started, successively pass through the left half shaft  1076  connected to left flange and left half shaft  1061  concentric hole connected to left half shaft gears, left long bolt  1001  head cone pressed left flange  1003  end surface of the cone, end of the left long bolt  1001  having a length of small diameter external thread, by screwing connected to anti-left rotation nut  1126 . The anti-left rotation nut  1126  by an interference fit connect with spline hole  1116  of the left half shaft gear, which flanging on the end face of the left half shaft gear  1116  is axially limit. The right axle  1027  is a few short ladder hollow spline shaft, the left and right ends equipped the spline, the middle comprising of the two smooth axis. The left end of half shaft  1027  is connected right half shaft gears  1124   by  a spline. The differential housing  1112  by antifriction spacer  1044  against in the right half shaft  1027  shoulder, external spindle in right side of right half shaft  1027  connected with inner spline of right flange  1032 , the end of right flange  1032  against right end shaft of the right half shaft  1027 , and the right side of long bolt  1033  mate locking cone surface centered on the right half shaft  1027 . In order to prevent axial movement of the right half shaft  1027  and the right flange, said long bolts  1033  from the right start flange  1032  is inserted bore in the right side of the right half shaft  1027 , the right long bolt  1033  cone shaped head is pressed against the tapered end surface of right flange  1032 , the right long bolt  1033  shaft portion having a length of small-diameter external thread, by screwing in the anti-right rotation nut  1127 . The anti-right rotation nut  1127  by an interference fit connect with spline of the right half shaft gear  1124  with small-diameter mating, which flanging on the end face of the right half shaft gear  1124 . 
         [0086]    Working principles of the invention as follows: 
         [0087]    The torque distribution motor  1038  of directional torque control dispenser  1040  mounted between the left cavity the drive axle housing  1008  and left end cap  1005 . When the torque distribution control motor  1038  receives an electrical signal, the torque distribution control motor  1038  internal rotor  1095  starts rotating, thus which will lead to the sun gear  1095   b  on the inner rotor  1095  forward or reverse rotation to output directional distribution torque, the torque distribution control motor  1038  is controlled by motor controller, control command from the motor controller is issued by the vehicle drive controller. 
         [0088]    As shown in  FIG. 10 , when the vehicle is traveling straight, wheel speed on both sides of the axle of the vehicle is substantially equal, torque distribution control motor drive controller  1038  does not receive instructions of controller, then torque directional distribution dispenser  1040  can ensure torque control distribution motor  1038  inner rotor  1095  without following wheel rotation, thereby reducing the induced electromotive force, to improve driving efficiency and reduce the burden on the motor controller hardware. In this case, the torque direction dispenser  1040  does not affect the approximate average distribution of drive torque at the left and right axle. At this time, the differential case  1112 , ring gear  1058  connected to differential shell, left half shaft  1061  connected to half shaft gears and sun gear  1061   a , carrier  1056  are in the same rotational speed. Thus, the double planetary gears of single row double planetary gear coupling mechanism  1014   b  are at the same speed around the sun gear  1061   a  revolution without rotation occurs. Meanwhile, the carrier  1081  of left planetary gear train  1011   b  in the double rows planetary gear TV mechanism  1039  by the spline connected with the left half shaft  1076  connected to the left flange fixedly, the left half shaft  1076  connected to\the left flange connected with the left half shaft with left half shaft gear solid company, so single row double planetary gear coupling TV mechanism  1014   b  and double rows planetary TV mechanism  1014   a  shared common carrier  1056 , which is the same speed with the carrier  1081  of left planetary gears train  1011   b  in double rows planetary TV mechanism  1039 . Meanwhile, the left and right planetary gear train  1011   b ,  1014   a  in the double planetary gear TV mechanism  1039 , have the same characteristic parameter in the design, that is, planetary gear  1082 , 1055  of the left and right planetary gear  1011   b ,  1014   a  and inner ring gear  1075   b ,  1054  are the same parameters. According to the kinematic equations of planetary gear train, the inner ring gear  1075   b ,  1014   a  of left and right planetary gear  1011   b  is the same speed, while the ring gear  1054  of the right planetary gear train  1014   a  is connected to the drive axle housing  1030  and its speed is zero, therefore, the ring gear  1075   b  of left planetary gear train  1011   b  is also zero. The carrier  1075   a  of the right planetary gear train in double planetary gear mechanism  1011   a  and the inner ring  1075   b  of left planetary gear train  1011   b  in double planetary gear TV mechanism  1039  formed integral, and left and right two planetary gear trains of double planetary gear mechanism  1011   a  shared the common ring gear  1070 , which is fixedly connected with the drive axle left housing  1008 . Therefore, right planetary gear train in the double planetary gear reduction mechanism  1011   a  does not rotate, the sun gear  1072   b  does not rotate, and because the carrier  1072   a  of left and right planetary trains in the double planetary gear reduction mechanism  1011   a  and the sun gear  1072   a  is one, therefore the carrier  1072   a  of the left planetary gear train in double planetary gear mechanism  1011   a  does not rotate, so left planetary gear train of double planetary gear deceleration mechanism  1011   a  does not rotate, the sun gear  1095   b  does not rotate, namely the rotor  1095  of the torque distribution control motor  1038  does not rotate. In other words, when the torque distribution control motor  1038  of the torque directional dispenser  1040  receives electrical signals to work, the inner rotor  1038  of the torque distribution control motor  1095  and the sun gear  1095   b  start rotating, the planetary gear  1071  of left planetary gear train in double rows planetary gear mechanism  1011   a  revolution around the sun gear  1095   b  at the same directional turn, the carrier  1072   a  deceleration output power, the planetary gears  1074  of right planetary gear train  1074  in double planetary gear mechanism  1011   a  is driven by the sun gear  1072   b  to the same directional turn, the carrier  1075   a  of right planetary gear train that is, inner ring  1075   b  of left planetary gear train  1011   b  in double planetary gear TV mechanism  1039  reduce together at the direction of rotation to output power. Therefore, the inner ring  1075   b  of left and right planetary gear train  1011   b ,  1014   a  in the double planetary gear TV mechanism  1039  have a different speed (since inner ring gear  1054  speed is zero), and left and right planetary gear  1011   b ,  1014   a  of double planetary gear TV mechanism  1039  having a common long sun gear  1050 , that is, the sun gear  1050  of the left and right planetary gear  1011   b ,  1014   a  are the same rotation speed, according to the planetary gear train kinematic formula, the carrier  1081  and  1056  of the left and right planetary gear train  1011   b ,  1014   a  produce different speed, namely the speed difference. Further, since the planet carrier  1081  of left planetary gear train in the double planetary gear TV mechanism  1039  is connected to left half shaft by splines (left half shaft  1061  connected to left half shaft gear and the left half shaft  1076  connected to the left flange). Therefore, the planet carrier  1081  in double planetary gear TV mechanism  1039  and the sun gear  1061   b  of single row planetary gear coupling mechanism  1014   b  is the same rotation speed. At this time, different speed of the sun gear  1061   b  and the carrier  1056  will be forced to lead the planetary gear  1057  of single row double planetary gear coupling mechanism  1014   b  to differential rotate, that is, when the car go straight, which causes differential at the different speed, that is, the side of the wheel speed acceleration, while the other side wheel deceleration, but when the car go straight according to car kinematics, left and right sides of wheels rotate at the same speed inevitable, so that the difference speed led to the left and right sides of different driving torque, thus achieving directional distribution torque. 
         [0089]    Thus, under normal circumstances, when the vehicle is straight, the torque distribution control motor  1038  does not receive electrical signals, the inner rotor  1095  does not rotate, at this time the differential  1019  is the same as the conventional differential, the driving motor  1036  transmitted to the power and drive torque is equally distributed to the left half shaft (left half shaft  1061  connected to left half shaft gears and the left half shaft  1076  connected to the left flange) and right half shaft  1027 . Driving torque and power from the driving motor  1036  by main reducer two stage driven gear  1111  is passed to the differential case  1112 , then being passed to the planetary gear shaft  1118  fixed to the differential case  1112  on. When the planetary gear shaft  1118  rotates together with the differential case  1112 , the left and right half shaft gears  1116  and  1124  are at the same rotation speed on the left and right half shaft  1061 , 1027  respectively. However, due to the torque distribution control motor  1038  had not received electrical signal, the torque distribution control motor  1038  does not start, torque directional dispenser  1040  does not output any torque, which does not affect the normal operation of the differential  1019 , at this time the torque distribution relationship is shown in  FIG. 11 . However, when the car is to perform interference instability, according to the actual situation the vehicle controller can send torque directional distribution instruction, which can control inner rotor  1095  of the torque distribution control motor  1038  forward or reverse rotation by the motor controller, so that the orientation distribution torque passes to the left half shaft (left half shaft  1061  connected to left half shaft gears and the left half shaft  1076  connected to the left flange) and the right half shaft&#39;s  1027  drive torque, resulting in a yaw moment of couple to correct vehicle attitude to ensure the stability of straight running, at this time the torque distribution relationship is shown in  FIG. 12 . 
         [0090]    As shown in  FIG. 12 , when the vehicle is cornering, especially when carried out at high speed cornering, the motor controller will send an electrical signal to torque distribution control motor  1038  of the torque directional distribution dispenser  1040 , the inner rotor of the torque control distribution motor  1038  starts rotating, at the role of the torque directional distribution dispenser  1040 , more torque directionally transferred to the outside wheels. If the direction of the wheel rotation while the car driving is defined as a positive direction, so if the car enters a curve to the right, the left wheels of the car and left half shaft (left half shaft  1061  connected to the left half shaft gears and left half shaft  1076  connected to left flange) rotate faster than the right wheels and right half shaft  1027  of cars the difference speed will be more than normal cornering difference speed determined by differential, which led to transmit drive torque to the outside wheel more. Specifically, torque distribution control motor  1038  of the torque directional dispenser  1040  receives an electrical signal, the inner rotor  1095  of the torque distribution control motor  1038  and the sun gear  1095   b  generates the positive direction of rotation, thus planetary gear  1071  of left planetary gear train in double rows planetary gear reduction mechanism  1011   a  produce positive directional revolution, the carrier  1072   a  produce positive direction revolution, together with sun wheel  1072   b  connected with the carrier  1072   a  also produce positive direction of rotation, the planetary gear  1074  of right planetary gear train in double rows planetary gear mechanism  1011   a  generate positive direction revolution, so the planetary gear  1082  of left planetary gear  1011   b  in double rows the planetary gear TV mechanism  1039  produce positive direction of rotation, while the planetary gear  1055  of right planetary gear train  1014   a  produce opposite directional revolution, that is, the carrier  1056  will produce rotational resistance to hinder differential case  1112  movement. In fact, double rows planetary gear mechanism  1011   a  and double planetary gear TV mechanism  1039  plays torque amplification effect, therefore, the torque applied to the carrier  1056  is much more than the torque distribution control motor  1038  applied to the inner rotor  1095  and the sun gear  1095   b , which can reduce the torque distribution control motor size. In this case, the planetary gears  1057  and  1064  of single row double planetary gear coupling mechanism  1014   b  no longer connect with ring gear  1058  having the half shaft and sun gear  1061   b  of double planetary gears train  1014   b , which is freely idling. Due to the carrier  1056  applied to impede the differential housing  1112  rotation resistance, the carrier  1056  takes torque control distribution motor  1038  transmitted torque from the differential case  1112  spreading to the sun gear  1061   b  and left half shaft (left half shaft  1061  connected to left half shaft gears and the left half shaft  1076  connected to left flange), so that the role of the left half shaft (left half shaft  1061  connected to left half shaft gears and the left half shaft  1076  connected to left flange) on drive torque larger than in the right half shaft  1027  driving torque. In other words, ring gear  1058  of the differential housing by the planetary gear  1057  and  1064  drive the sun gear  1061   b , namely, to give the left half shaft  1076  higher speed. Therefore, at this time the torque directional dispenser  1040  played a overspeed device role in the left half shaft  1076 . If the car enters a curve to the left, the motor controller sends to the torque control distribution motor  1038  an electrical signal in the opposite rotation direction, the inner rotor  1095  and the sun gear  1095   b  start reversing rotation, the same token, at this time the carrier  1056  of the planetary gear  1055  of the right planetary gear train  1014   a  in double rows planetary gear TV mechanism  1039  generates a promotion rotational force to the differential case  1112 , therefore, under the torque directional dispenser  1040  control, there is more the drive torque transmitted from the differential case  1112  to right half shaft  1027 . 
         [0091]    Therefore, in general, following the torque distribution control motor  1038  of torque directional dispenser  1040  positive direction rotation torque more larger, the torque commutator  1041  transmitted to the left half shaft  1076  greater torque. 
         [0092]    The torque directional dispenser  1040  depends on several conditions, all of these conditions may be mounted on the vehicle sensor monitor, and processed by a processor to control the torque control distribution motor  1038  electric signal, the conditions monitored including vehicle speed, yaw rate, lateral and longitudinal acceleration of the vehicle, the steering angle, wheel slip ratio, engine and transmission operating parameters, and temperature of the torque distribution control motor  1038  and the like. 
         [0093]    In addition, experience with the straight running disturbance instability hazardous situation, if the vehicle turns into the slippery pavement or some other poor road pavement, when concrete pavement conditions to the torque distribution of left and right half shaft  1076  on  1027 , also allows torque distribution control motor  1038  of torque directional dispenser  1040  receive an electrical signal, actively distributing drive torque left half shaft  1076  and the right half shaft  1027  in order that the vehicle can be stabilized travel according to road conditions. 
         [0094]    Although the embodiments of the present invention has been disclosed above, but it is not limited to the use of the specification and embodiments listed, it can be applied to various fields suitable for the invention, for a person skilled in the art, it can be easily additional modifications to achieve, and therefore without departing from the general concept of the scope of the claims and the equivalents as defined in the present invention is not limited to the specific details and illustrations herein illustrated and described herein.