Abstract:
A drive train of a motor vehicle between a drive unit and a first wheel axle and a second wheel axle is disclosed, the second wheel axle consisting at least of a first sub-axle and a second sub-axle, and the first and the second sub-axle being connected to a differential for torque distribution. The differential is an individual differential which is operatively connected to the drive unit via a drive shaft and which can optionally be operatively connected to the first wheel axle for torque distribution.

Description:
CROSS-REFERENCES TO RELATED APPLICATIONS 
     This application is the U.S. National Stage of International Application No. PCT/EP2014/001943, filed Jul. 16, 2014, which designated the United States and has been published as International Publication No. WO 2015/014449 and which claims the priority of German Patent Application, Serial No. 10 2013 012 947.8, filed Aug. 2, 2013, pursuant to 35 U.S.C. 119(a)-(d). 
     BACKGROUND OF THE INVENTION 
     The invention relates to a drive train of a motor vehicle between a drive aggregate and a first wheel axle and a second wheel axle, wherein the second wheel axle consists of at least one first sub-axle and a second sub-axle, which are connected with a differential for distribution of a torque. 
     Such a drive train was proposed in the not yet published German patent application 10 2012 021 531.4 of the applicant. In order to reduce the space required by an axle differential on the second wheel axle and thus enable a compact configuration of the second wheel axle this drive train includes instead of an axle differential on the second wheel axle a dual differential arranged at a greater distance to the second wheel axle consisting of two operably connected planetary differentials. A first one of the two differentials serves as middle differential, which is operatively connected with a drive shaft originating from the and can be operatively connected with an output shaft leading to the first wheel axle, while the second differential serves as axle differential for the second wheel axle and is operatively connected with a first connecting shaft, which leads to the first sub-axle and with a second connecting shaft which leads to the second sub-axle. 
     The drive train serves for transmitting a torque between the drive aggregate of the motor vehicle and the at least two wheel axles. Thus the first wheel axle and also the second wheel axle are connected to the drive aggregate by the drive train. Both wheel axles are thus driven wheel axles and hence the motor vehicle is for example an all wheel drive motor vehicle. The first wheel axle is hereby for example a front axle of the motor vehicle while the second wheel axles is the rear axle of the motor vehicle. However, the opposite configuration is also possible. The two connecting shafts serve for transmitting the torque to the second wheel axle and distribute the torque to the two sub-axles. The connecting shafts are in particular configured as cardanic shafts. 
     SUMMARY OF THE INVENTION 
     In light of the foregoing the invention is based on the object to improve a drive train of the above-mentioned type to enable a more compact configuration of a drive train. 
     According to a first variant of the invention this is achieved with a drive train characterized by the features of the independent claim. Accordingly the differential is a single differential, which is operatively connected with the drive aggregate via a drive shaft and which can optionally be operatively connected for torque distribution with the first wheel axle. In other words instead of a dual differential only a single differential is used, which firstly is directly operatively connected with the drive shaft, secondly is connected with the first and the second sub-axle of the second wheel axle for torque distribution and which thirdly can optionally also be operatively connected with the first wheel axle for torque distribution. 
     A preferred embodiment of the invention provides that the first and the second sub-axles are connected for torque distribution with the differential by a first and a second connecting shaft and that the differential can optionally be connected with the first wheel axle for torque distribution via one or both connecting shafts and an output shaft. 
     This configuration of the invention is based on the rationale to connect the first wheel axle to the two connecting shafts which lead from the differential to the sub-axles of the second wheel axle or to connect them to the output of the differential so thus obviating the requirement for a dual differential and thus reducing the installation space required for the differential. Preferably the first wheel axle is not fixedly connected to the two connecting shafts so that an all wheel drive can be implemented when needed, wherein after the connection of the first wheel axle to the two connecting shafts the torque provided by the drive aggregate can be distributed differently to the wheels of the motor vehicle. 
     As a result of the feature combination of the first variant of the invention the drive aggregate is thus not only operatively connected via the drive shaft, the single differential and the first and second connecting shaft with the two sub-axles of the second wheel axle, but can also be operatively connected with the first wheel axle for torque distribution. 
     As in the drive shaft of the above-mentioned German patent application 10 2012 021 513.4 the torque distribution from the differential in the direction of the second wheel axle is preferably accomplished by means of two connecting shafts, which are advantageously constructed as cardanic shafts. The first connecting shaft is or can be hereby coupled with the first sub-axle of the second wheel axle. The second connecting shaft on the other hand can be or is coupled with the second sub-axle of the second wheel axle. Because the torque distribution to the two sub-axles occurs separate from each other via the connecting shafts, the differential can be relocated from the region of the second wheel axle, which enables reducing the required space. 
     The invention also relates to a motor vehicle with a drive train, which is preferably constructed as described above in the above. The motor vehicle has the first wheel axle and the second wheel axle wherein the second wheel axle consists of at least the first sub-axle and the second sub-axle. 
     In the preferred embodiment of the invention the motor vehicle is characterized by a first connecting shaft operatively connected with the first sub-axle, by a second connecting shaft operatively connected with the second sub-axle and by a single differential operatively connected with both connecting shafts, which differential is operatively connected with the drive aggregate or a transmission of the motor vehicle assigned to the drive aggregate via a drive shaft, and can be selectively operatively connected if needed with the first wheel axle via one or both connecting shafts and an output shaft for torque distribution. The single differential thus connects the drive shaft for torque distribution with the first and the second connecting shaft and can also connect the drive shaft with the output shaft via the first and/or second connecting shaft for torque distribution. 
     This means that for example equal amounts of a portion of the torque provided via the drive shaft are provided at the first and at the second connecting shaft and with this at the first or second sub-axle of the second wheel axle, when only the second wheel axle is to be driven. When also the first wheel axle is to be driven the respective torques provided at each of the two connecting shafts can partially be transmitted by the output shaft to the first wheel axle, selectively either each respective torque individually or both torques together. When the torque provided at both connecting shafts is transmitted to the first wheel axle, all wheels of the two wheel axles are driven with approximately equal torques, when the torque of the drive shaft is distributed in the differential in equal parts to the first and the second connecting shaft or to the two sub-axles of the second wheel axle. 
     In a preferred embodiment of the invention, the differential is a planetary gear differential with a sun gear, a ring gear and a planet carrier and with at least one planet gear meshing with the sun gear and the ring gear. The single differential thus has the known construction of a planetary gear train with a sun gear, a ring gear and advantageously multiple planet gears rotatably supported on the planet carrier, which mesh with the sun gear and with the ring gear. 
     Preferably the ring gear is directly connected with the drive aggregate via the drive shaft, while the sun gear is directly operatively connected with one of the two connecting shafts and the planet carrier is directly operatively connected with the other one of the two connecting shafts. The term direct operative connection means that the mentioned shafts are respectively directly connected with the respective element of the planetary gear differential. 
     In order to enable a selective connection of the drive shaft to one or both connecting shaft, the output shaft is connected to the two connecting shafts or corresponding outputs of the differential by two separate and independently activatable or shiftalbe clutches, wherein each of the two clutches directly operatively connects the drive shaft with one of the two connecting shafts or with the element of the planetary gear differential that is directly operatively connected with the respective connecting shaft, i.e., with the sun gear in the case of the one of the connecting shafts and with the planet gear in the case of the other one of the connecting shafts. 
     Advantageously one of the two clutches includes a clutch disc operatively connected with the one connecting shaft or the sun gear of the planetary differential, wherein at least two clutch rings that are operatively connected with the output shaft and are coaxial with the output shaft can be brought into coupling engagement against the outer circumference of the clutch disc from opposite sides. The other one of the two clutches on the other hand advantageously includes a clutch disc operatively connected with the other connecting shaft or with the planet carrier of the planetary differential, wherein also at least two clutch rings, which are connected with the output shaft in fixed rotative relationship with the output shaft, and are coaxial with the output shaft, can be brought in coupling engagement against the outer circumference of the other clutch from opposite sides. 
     The two clutches are open when only the second wheel axle is to be driven. When the first wheel axle is also to be driven with a relatively small torque, one of the two clutches is closed, whereby the torque provided at one of the wheels of the second wheel axle is partially transmitted to the first wheel axle via the closed clutch. When the first wheel axle is to be driven with a greater torque, both clutches are closed, whereby the torques provided at the two wheels of the second wheel axle are transmitted respectively partially to the first wheel axle via the closed clutches. By corresponding actuation of the clutches a torque can thus be shifted from the first and/or second sub-axle of the second wheel axle to the first wheel axle in a targeted manner. Actuation of both clutches blocks the differential. The clutches are advantageously constructed as friction clutches, which can also be closed at greater rotational speed differences. When such a friction clutch is controlled so that the clutches are not completely closed and a slip is present between the clutch elements, only a small torque is transmitted to the first wheel axle, which results in further possible variations of the torque vectoring or torque splitting. 
     As an alternative to the embodiments described above the separate or separately shiftable clutches can also be arranged between either of the two sub-axles and the first wheel axle so that selectively one or both sub-axles can be operatively connected with the first wheel axle. In this case advantageously one of the two clutches is arranged between an output shaft, which leads to the first wheel axle, and the first sub-axle and an element of the differential, which is operatively connected with the first sub-axle in fixed rotative relationship with the first sub-axle, while the other one of the two clutches is arranged between the output shaft and the second sub-axle and another element of the differential which is operatively connected with the second sub-axle. 
     An advantageous refinement of the invention provides that the planetary gear differential includes a dual planetary transmission in which the planet carrier has at least one radially outer outer-planet gear and at least one radially inner inner-planet gear, wherein the outer-planet gear meshes with the second ring gear and the inner-planet gear, while the inner-planet gear meshes with the outer-planet gear and the sun gear. The outer-planet gear and also the inner-planet gear are rotatably supported on the planet carrier. The outer-planet gear and the inner planet gear can be arranged in different angular positions relative to a rotary axis of the planet carrier. 
     Even though it is generally possible to arrange the two connecting shafts between the differential and the second wheel axel at lest in sections parallel adjacent each other it is advantageous when the first and the second connecting shaft acre arranged coaxial to each other, wherein one of the two connecting shafts is configured as a hollow shaft though which the other connecting shaft, which is configured as central shaft, extends. This enables on one hand to accommodate the two connecting shafts particularly space-efficiently and on the other hand avoids reducing the efficiency which would result in case of a parallel arrangement of the two connecting shafts due to the requirement of an additional spur gear or chain drive for connecting the connecting shaft, which is offset relative to the rotary axis of the sun gear and ring gear of the planetary gear differential. 
     In the case of a coaxial arrangement of the two connecting shafts according to another preferred embodiment of the invention, two oppositely acting axial bearings are arranged between the two coaxial connecting shafts so that the connecting shaft that is configured as central shaft, is indirectly supported in the connecting shaft that is configured as hollow shaft. This preferred configuration of the invention is not only advantageous in the above-described drive trains but also generally in wheel axles with two sub-axles that are driven by two coaxial connecting or cardanic shafts via a respective bevel gear transmission, and also in wheel axles with conventional transmissions in which two sub-axles are driven via bevel gear transmissions and two short coaxial connecting shafts are driven by an axle differential that is configured as planetary gear differential, so that this preferred configuration of the invention is at the same time also a second variant of the invention. 
     In this second variant of the invention the indirect support of the inner connecting or cradanic shaft, which is configured as central shaft, in the outer connecting or cardanic shaft, which is configured as hollow shaft, makes it possible that the axial forces mostly compensate each other. 
     A configuration of the first and the second variant of the invention provides that the crown wheel connected with the first sub-axle has an offset to one of the two bevel gear transmissions and the crown wheel connected with the second sub-axle has an offset to the other one of the two bevel gear transmissions in axial direction. In this case the crown wheels of the two bevel gear transmissions can have the same diameter, which allows increasing the number of parts that are the same. 
     Another configuration of the second variant of the invention on the other hand provides that the first and second sub-axle are each connected with the first and the second connecting shaft respectively via bevel gear transmissions with differently sized crown wheel diameters. In this case the first and second sub-axle can have aligned rotary axes in axial direction of the two connecting shafts. This has the advantage that one of the sub-axles can be extended by a support axle on which the crown wheel, which is connected the other sub-axle, can be supported via two axial bearings. This has the advantage that the axial meshing forces between the crown wheel and the pinion of each bevel gear transmission compensate each other and thus reduce load-dependent bearing losses. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWING 
       In the following the invention is explained in more detail by way of five embodiments shown in the drawing and several variants, without limiting the invention. It is shown in: 
         FIG. 1  a schematic representation of a first embodiment of a drive train according to the first variant of the invention; 
         FIG. 2  a schematic representation of a second embodiment of a drive train according to the first variant of the invention 
         FIG. 3  a schematic representation of a third embodiment of a drive train according to the first variant of the invention; 
         FIG. 4  a schematic representation of parts of a fourth embodiment of a drive train according to the first and second variant of the invention; 
         FIG. 5  a schematic representation according to  FIG. 4 , however of one variant; 
         FIG. 6  a schematic representation of parts of an embodiment of a drive train according to the second variant of the invention; 
         FIG. 7  a schematic representation corresponding to  FIG. 6  however of one variant; 
         FIG. 8  a schematic representation of a fifth embodiment of a drive train according to the first variant of the invention. 
     
    
    
     DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS 
       FIG. 1  shows a first embodiment of a drive train  1  of a motor vehicle, which is here not further shown. The motor vehicle has a drive train  2 , a transmission  3 , a first wheel axle  4  configured as front axle and a second wheel axle  5  configured as rear axle, which are here only indicated schematically, wherein the second wheel axle  5  consists of at least one first sub-axle  6  and a second sub-axle  7 . The drive train  1  has a planetary gear differential  8 , which is operatively connected with the transmission  3  via a drive shaft  9 . Between the differential  8  and the first wheel axle  4  an output shaft  10  is arranged, which is operatively connected with the first wheel axle  4  via a gearwheel stage  11 . Between the differential  8  and the second wheel axle  5  a first and a second connecting shaft  12 ,  13  are arranged, with the first connecting shaft  12  being operatively connected with the first sub-axle  6  via a first bevel gear transmission  14 , and the second connecting shaft  13  being operatively connected with the second sub-axle  7  via a second bevel gear transmission  15 . 
     The planetary gear differential  8 , which is configured as dual planetary transmission, consists of a sun gear  16 , a ring gear  17  and a planet carrier  18 , on which multiple radially outer outer-planet gears  19  and multiple radially inner inner-planet gears  290  are rotatably supported. The outer-planet gears  19  mesh with the ring gear  17  and with the inner-planet gears  20 . The inner-planet gears  20  mesh with the outer-planet gears  19  and with the sun gear  16 . With this the planet carrier  18  and also the sun gear  16  are rotatively driven by a rotation of the ring gear  17 . 
     The ring gear  17  of the planetary gear differential  8  is connected with the drive shaft  9  and via the drive shaft with the transmission  3  and the drive aggregate  2 . The planet carrier  18  is connected to the first connecting shaft  12  in fixed rotative relationship with the first connecting shaft. The sun gear  16  is operatively connected with the connecting shaft  13  via an output shaft  21 , which is configured as a hollow shaft, and a gearwheel stage  22  with spur gear teeth. The first connecting shaft  12  is coaxial with the output shaft  21  and extends through the output shaft. 
     Between the output shaft  21  and the output shaft  10  a first clutch  23  is arranged by which the second connecting shaft  13  can be operatively connected with the output sahft  10  via the gearwheel stage  2  and the output shaft  21 . Between the planet carrier  18  and the output shaft  10  a second clutch  24  is arranged by which the first connecting shaft  12  can be operatively connected with the output shaft  10  via the planet carrier  18 . The two clutches  23  and  24  are friction clutches and are open when only the wheels of the second wheel axle  5  are to be driven. The two clutches  23  and  24  are arranged on the side of the differential  8  neighboring the wheel axle  5 . 
     The clutch  23  includes a clutch disc  25 , which is connected with the transmission output shaft  21  in fixed rotative relationship with the transmission output shaft, and against which two clutch rings  26  can be pressed from opposite sides when closing the clutch  23 . The clutch  24  includes a clutch disc  27 , which is connected with the planet carrier  18  in fixed rotative relationship with the planet carrier, and against which two clutch rings  28  can be pressed from opposite sides when closing the clutch  24 . The clutch rings  26  and  28  are in fixed rortative relationship with each other and with the output shaft  10 . 
     When the first wheel axle  4  is also to be driven with a relatively small torque, only the clutch  23  or only the clutch  24  is closed. When only the clutch  23  is closed the torque provided to the first sub-axle  7  is partially redirected or transmitted via the clutch  23  to the first wheel axle  4 . When only the clutch  24  is closed the torque delivered from the drive aggregate to the second sub-axle  6  is partially transmitted or redirected to the first wheel axle  4  via the clutch  24 . When the first wheel axle  4  is to be driven with a greater torque, both clutches  23  and  24  are closed. In this case the torque delivered by the drive aggregate  2  to the two sub-axles  6  and  7  is respectively partially transmitted or redirected to the first wheel axle  4  via the two clutches  23  and  24 . In this case the differential  8  is blocked. Closing the clutches  23 ,  24  thus enables a torque splitting between the first wheel axle  4  and the second wheel axle  5 . 
     While in the first embodiment shown in  FIG. 1  the output shaft  10  is configured as a hollow shaft though which the drive shaft  9  passes as central shaft, the output shaft  10  in the second embodiment shown in  FIG. 2  extends as central shaft through the drive shaft  9 , which is configured as a hollow shaft and which in this case is operatively connected with the output shaft  30  of the transmission  3  via an additional transmission stage  29  with spur gear teeth. 
     In the second embodiment the two clutches  23  and  24  are additionally arranged on the side of the differential  8  neighboring the wheel axle  4 . The first clutch  23  is arranged between the output shaft  10  and a further output shaft  31  of the differential  8 , which output shaft  31  is connected with the planet carrier  18  in fixed rotative relationship with the planet carrier, and is operatively connected with the connecting shaft  13  via the planet carrier  18 , the inner-planet gears  20 , the output shaft  21  and the gearwheel stage  22 . The second clutch  24  is arranged between the output shaft  10  and the first connecting shaft  12 , which extends through the differential  8  and is connected with the sun gear  16  in fixed rotative relationship with the sun gear. The remaining features of the second embodiment essentially correspond to those of the first embodiment. 
     When in the second embodiment the clutch  23  is closed, the torque provided from the drive aggregate  2  to the second sub-axle  7  is partially redirected to the first wheel axle  4  via the clutch  23 . When the clutch  24  is closed the torque provided by the drive aggregate  2  to the first sub-axle  6  is partially redirected to the first wheel axle  4  via the clutch  24 . 
     The embodiment shown in  FIG. 3  corresponds to the embodiment of  FIG. 2  with the exception of the part of the drive train  1  arranged between the differential  8  and the two sub-axles  6  and  7 . In order to reduce the required space of the drive train  1  between the differential  8  and the sub-axles and to increase the efficiency, in the embodiment of  FIG. 3  the two connecting shafts  12 ,  13  are configured coaxial relative to each other wherein the shaft  13  is configured as hollow shaft though which the shaft  12  extends. In addition in this embodiment the crown wheels  32 ,  33  of both bevel gear transmissions  14 ,  15 , which are connected with the two sub-axles  6  and  7  in fixed rotative relationship with the sub-axles  6  and  7 , have bevel gears which are slanted in the same direction, in contrast to the embodiments described above where the direction of the slant of the bevel gears of the crown wheels  32 ,  33  is different. 
       FIGS. 4 and 5  show two variants of the third embodiment, which may not only be used in the afore-described drive train  1  but generally in drive trains  1  with two coaxial cardanic or connecting shafts  12 ,  13 . 
     As shown in  FIGS. 4 and 5 , two axial bearings  34   35  are arranged between the connecting shaft  13 , which is configured as hollow shaft, and the connecting shaft  12 , which is configured as central shaft, in which axial bearings the connecting shaft  12  is supported in the connecting shaft  13 . The connecting shaft  13  in turn is supported in at least one bearing  38  in relation to a surrounding housing  39  so that the connecting shaft  12  is indirectly supported in the housing  39 . Hereby the connecting shaft  12  is supported in the two axial bearings  34 ,  35  in opposite directions, whereby the occurring axial forces compensate each other to the most degree. 
     While in the variant in  FIG. 4  the crown wheels  32 ,  33  of the bevel gear transmissions  14 ,  15 , which are connected with the sub-axles  6  or  7  of the second heel axle  5  in fixed rotative relationship with the sub-axles  6  or  7 , have an axial offset in axial direction of the two connecting shafts  12 ,  13  but same diameters, in the variant in  FIG. 5  the crown wheels  32 ,  33  and with this also the pinions  36 ,  37  of the two bevel gear transmissions  14 ,  15 , which are connected with the connecting shafts  12 ,  13  in fixed rotative relationship with the connecting shafts  12 ,  13 , have different diameters while the crown wheels  32 ,  33  of the sub-axles  6  and  7  of the second wheel axle  5  are aligned with each other. In the variant of  FIG. 5  an additional support shaft  40 , which is connected in fixed rotative relationship with the sub-axle  6  and with the crown wheel  32 , is provided, extends past the crown wheel  32  up to the crown wheel  33  where the latter is supported in two opposite axial bearings  41 ,  42  on the support shaft  40 . This also enables a compensation of the axial forces of the crown wheels so that only the resulting axial forces are introduced into the bearings  38  fixedly connected to the housing. In order to make it possible to guide the support shaft  40  past the connecting shaft  12 , the bevel gear transmissions  14 ,  15  in the variant in  FIG. 5  have a hypoid offset in the direction of the vertical axis of the motor vehicle of at least 25 to 30 mm. 
       FIGS. 6 and 7  show two variants of a conventional second wheel axle  5  or rear axle with two sub-axles  6 ,  7  and a differential  8 , which is configured as planetary gear differential, and which is operatively connected with the pinions  36 ,  37  of two bevel gear transmissions  14 ,  15  via two short coaxial connecting shafts  12 ,  13 , with the crown wheels of  32 ,  33  of the two bevel gear transmissions  14 ,  15  being connected with the two sub-axles  6 ,  7 . 
     As in  FIG. 4 , in the variant in  FIG. 6  the two crown wheels  32 ,  33  again have an offset V in axial direction of the connecting shafts  12 ,  13  and have same diameters. In the variant in  FIG. 7  the crown wheels  32 ,  33 , as in  FIG. 5 , have different-sized diameters, while the crown wheels  32 ,  33  of the sub-axles  6  and  7  are aligned with each other. Also in this case an additional support axle  40  is provided between the sub-axle  6  and the crown wheel  33 , on which the crown wheel  3  is supported in two axial bearings  41 ,  42  in order to compensate the axial forces of the crown wheel. Also in this case the bevel gear transmissions  14 ,  15  have a hypoid offset in the direction of the vertical axis of the motor vehicle of at least 25 to 30 mm. 
       FIG. 8  shows a fifth embodiment of the drive train  1 , which is provided for a motor vehicle with a transversely mounted drive aggregate  2  and a DQ or MQ transmission  3 , wherein a further clutch  43  is provided between the drive aggregate  2  and the transmission  3 . In contrast to the embodiments in  FIGS. 1 to 3 , the drive train  1  in  FIG. 5  has a first wheel axle  4  configured as rear axle and a second wheel axle  5  configured as front axle. The first wheel axle  4  can be activated or deactivated if needed, while the second wheel axle  5  consists of at least one first sub-axle  6  and a second sub-axle  7 . In contrast to the embodiment in  FIGS. 6 and 7 , the differential  8  is not a rear axle differential but a front axle differential arranged in the region of the second wheel axle  5 , which is operatively connected with the transmission  3  by a drive shaft  9  and a gearwheel stage  11  as in the differentials  8  described above. 
     Between the differential  8  and the first wheel axle  4 , an output shaft  10  is arranged, which can selectively be coupled or operatively connected with the first sub-axle  6  or with the second sub-axle  7  by means of two clutches  23 ,  24 , in order to partially transmit the torque provided by the drive aggregate at the first sub-axle  6  and/or the second sub-axle  7  to the first sub-axle  4 . As above, the two clutches  23  or  24  are friction clutches each including a clutch disc  25  or  27  and two clutch rings  26  or  28 , which when closing the clutch  23  or  24  are pressed from opposite sides against the associated clutch disc  25  or  27 . The clutch rings  26 ,  28  of the two clutches  23 ,  24  are connected to each other in fixed rotative relationship. The two clutches  23   24  have a common output shaft  44 , which is connected with the clutch rings  26 ,  28 , via which a bevel gear transmission  45  is connected with the output shaft  10 , which extends in longitudinal direction of the motor vehicle. The output shaft  10  can be configured as cradanic shaft. 
     As described above, the differential  8  is configured as dual planet gear transmission and consists of a sun gear  16 , a ring gear  17  and a planet carrier  18 , on which multiple radially outer outer-planet gears  19  and multiple radially inner inner-planet gears  20  are rotatably supported. The outer-planet gears  19  mesh with the ring gear  17  and with the inner-planet gears  20 . The inner-planet gears  20  mesh with the outer-planet gears  19  and the sun gear  16 . 
     The ring gear  17  is driven by the drive shaft  9  via the gearwheel stage  11 . The sun gear  16  is connected with the first sub-axle  6  and with the clutch disc  25  of the first clutch  23  in fixed rotative relationship. The planet carrier  18  is connected with the other sub-axle  7  and with the clutch disc  27  of the second clutch  24  in fixed rotative relationship. 
     When in the fifth embodiment the clutch  23  is closed, the torque delivered by the drive aggregate  2  to the first sub-axle  6  is partially redirected to the first wheel axle  4  via the clutch  23 , the output shaft  44 , the bevel gear transmission  45  and the drive shaft  10 . When the clutch  24  is closed the torque delivered by the drive aggregate  2  to the second sub-axle  7  is partially redirected to the first wheel axle  4  via the clutch  24 . When the first wheel axle  4  is also to be driven with a greater torque, both clutches  23  and  24  are closed. In this case the torque delivered by the drive aggregate  2  to both sub-axles  6  and  7  is partially transmitted or redirected to the first wheel axle  4 . In this case again the differential is blocked. Closing the clutches  23 ,  24  thus also enables in this case a torque splitting between the first wheel axle  4  and the second wheel axle  5 .