Abstract:
A flexible drive concept for a vehicle is provided. As a result, the claimed drive device includes a shifting device which can shift a transmission gear and an intermediate gear into different shifting states such that a second motor can be selectively used in two gears as a drive motor or alternatively as a torque vectoring motor.

Description:
[0001]    The present invention relates to a drive device for a vehicle. 
         [0002]    Drives for vehicles including two engines are frequently used as hybrid drives, optionally one of the engines or both engines of the drive being used together to drive the vehicle as a function of the operating state of the drive. 
       BACKGROUND 
       [0003]    The publication DE 10 2006 031 089 A1, which is arguably the most proximate prior art, provides a drive device for a motor vehicle. The drive device is characterized in that it includes an internal combustion engine and an electric motor, in a first operating mode, the drive device operating as a hybrid drive in the case of which an identical power flow takes place on both wheels of the motor vehicle via the main engine, and in another operating mode, a power and torque distribution on the wheels being alternatingly variable via an additional main engine as a function of the predefined parameters. 
       SUMMARY OF THE INVENTION 
       [0004]    It is an object of the present invention to provide a more flexible drive concept. 
         [0005]    The present invention provides a drive device is provided which is suitable and/or designed for a vehicle. The vehicle is, in particular, implemented as a passenger car, a truck, a bus or the like. In particular, the drive device is used to generate and output a drive torque for an axle of the vehicle. 
         [0006]    For this purpose, the drive device includes a first and a second output shaft, each of the output shafts being assigned and/or assignable to a wheel of the vehicle. The output shafts are used to transfer the drive torque from the drive device via the output shafts to the wheels. 
         [0007]    The drive device includes a first interface for coupling a first engine. The first engine may, for example, be coupled to the first interface via a shaft, in particular via a pinion shaft. 
         [0008]    Furthermore, the drive device includes a differential device which is designed for distributing the drive torque from the first interface to the two output shafts. In particular, the drive torque of the first engine is distributed 50:50 to the output shafts without further influences and/or is designed as a transverse differential. The differential device includes an input and two outputs. The input of the differential device is, in particular, drivably coupled to the first interface. In particular, the input of the differential device forms the first interface. The first interface is, for example, implemented as a ring gear which meshes with the pinion shaft. The two outputs of the differential device are, in particular, drivably coupled or rotatably fixedly connected to the first and the second output shafts. In the most general specific embodiment of the present invention, the differential device may be designed as a bevel gear wheel differential device, for example. Preferred specific embodiments of the present invention will be explained in the following. 
         [0009]    Furthermore, the drive device includes a second interface for coupling a second engine. In particular, the first engine differs from the second engine with respect to the engine type. 
         [0010]    The drive device includes a transmission which is designed for transmitting the drive torque of the second engine. The transmission is preferably designed in such a way that it converts a high rotational speed of the second interface to a lower rotational speed. The transmission includes an input and two outputs. The input of the transmission is coupled to the second interface or forms same. The two outputs are, in particular, assigned to different transmission stages so that different rotational speeds are present at the two outputs of the transmission in the case of the same input rotational speed at the input of the transmission. 
         [0011]    Furthermore, the drive device includes an intermediate gear, the intermediate gear being situated in the torque flow, in particular, between the transmission and the differential device. In particular, the drive torque is guided from the second interface to the differential device via the intermediate gear in at least one shifting state of the shifting device. 
         [0012]    In addition, the drive device includes a shifting device, the shifting device being operable electromechanically, electrohydrostatically, hydraulically, or electromagnetically, for example. The shifting device is designed to couple the transmission and the intermediate gear to one another in at least two different shifting states. The shifting device may also be referred to as a coupling device or a coupling system. 
         [0013]    It is provided within the scope of the present invention that the intermediate gear includes a first and a second input. 
         [0014]    With the aid of this constructive design, different shifting states of the shifting device and thus of the drive device are possible: 
         [0015]    First Gear: 
         [0016]    In a first shifting state of the shifting device, the first output of the transmission is rotatably fixedly connected to the first input of the intermediate gear. In particular, the first output of the transmission is that output which has in comparison to the second output of the transmission a lower rotational speed, while having the same input rotational speed. The intermediate gear is designed in such a way that the drive torque is distributed to the two output shafts from the second interface via the intermediate gear and via the differential device. In this first shifting state, the drive device may thus optionally be powered exclusively by the second engine or in a hybrid state together by the first and the second engines. 
         [0017]    Second Gear: 
         [0018]    In a second shifting state of the shifting device, the second output of the transmission is rotatably fixedly connected to the first input of the intermediate gear. In this shifting state, the drive torque is also distributed to the output shafts from the second interface, i.e., from the second engine, via the differential device in order to optionally allow for an exclusive drive by the second engine or a hybrid drive with the aid of the two engines. 
         [0019]    TV Mode (Torque Vectoring Mode): 
         [0020]    In the third shifting state of the shifting device, the first or the second output, preferably the first output of the transmission, is rotatably fixedly connected to the second input of the intermediate gear so that the drive torque of the second interface is usable for a drive torque distribution. In this TV mode, the power and/or the torque distribution to the output shafts may be influenced via the second engine. 
         [0021]    The advantage of the present invention is thus to be seen in that the drive device may make available two hybrid gears and one torque distribution gear despite the simple design. At the same time, the constructive design is enlarged only to a minor degree as compared to the prior art. It is to be stressed, in particular, that the second engine is used for the drive as well as for the torque distribution. 
         [0022]    In one preferred refinement of the present invention, the shifting device is designed to assume a TV intermediate shifting state which is between the second and the third shifting state. In this intermediate shifting state, the first and the second outputs of the transmission are freewheeling. In particular, the intermediate shifting state is assumed at the transition from the second to the third shifting state. The advantage of the TV intermediate shifting state is that at that point in time when the first and the second outputs of the transmission are freewheeling, the rotational speed of the second interface or of the second engine may be adapted to the changed function. While in the first and in the second gears a concurrent movement of the second interface or of the second engine at a rotational speed which matches the rotational speed of the output shafts is necessary, in the third shifting state, a standstill of the second interface or of the second engine is necessary at least when the vehicle is driving straight ahead. In this way, the TV intermediate shifting state has the advantage that the second interface or the second engine may be decelerated during the change from the second to the third shifting state and/or accelerated during the transition from the third shifting state to the second shifting state and may be synchronized with the required rotational speed. 
         [0023]    In addition, the shifting device is optionally designed to assume a drive intermediate shifting state between the first shifting state and the second shifting state, the first and the second outputs of the transmission also being freewheeling in the drive intermediate shifting state so that the rotational speed of the second interface or of the second engine may be adapted to the changing transmission. 
         [0024]    In one preferred constructive embodiment of the present invention, the intermediate gear includes a drive gear section and a distribution gear section. 
         [0025]    In one possible constructive embodiment of the present invention, the drive gear section includes a first input of the intermediate gear and a first output of the intermediate gear to the differential device. The distribution gear section includes the second input of the intermediate gear, a second output of the intermediate gear to one of the output shafts, and a coupling output, the coupling output being, in particular, rotatably fixedly coupled to the first input of the intermediate gear. In this embodiment, the functions of the intermediate gear may be implemented via the drive gear section in the first and in the second shifting states and the function of the intermediate gear may be implemented via the distribution gear section in the third shifting state. 
         [0026]    With regard to the construction, it is preferred that the drive gear section is designed as a drive planetary gear set, in particular as a spur planetary gear set including gear wheels which are circumferentially teethed at the front sides. The drive planetary gear set includes a sun gear, a planetary carrier, an annulus gear as well as a set of planet wheels which are rotatably situated on the planetary carrier and which mesh with the sun gear and the annulus gear. The first input of the intermediate gear is, in particular, rotatably fixedly coupled to the sun gear. A or the first output of the intermediate gear is, in particular, rotatably fixedly coupled to the planetary carrier. The annulus gear is, in particular, rotatably fixedly coupled to a stationary surrounding structure, e.g., a housing or the like. Due to this design, the drive gear section may be implemented to be very narrow and in addition lightweight, in particular in the axial extension. 
         [0027]    It is also preferred that the distribution gear section is designed as a distribution planetary gear set. The distribution planetary gear set includes a sun gear, a planetary carrier, an annulus gear as well as a set of planet wheels which are rotatably mounted on the planetary carrier and which mesh with the annulus gear and the sun gear. The second input of the intermediate gear is, in particular, rotatably fixedly coupled to the annulus gear. A or the second output of the intermediate gear to one of the output shafts is, in particular, rotatably fixedly coupled to the planetary carrier. A or the coupling output of the distribution planetary gear set which is, in particular, rotatably fixedly coupled to the first input of the intermediate gear is, in particular, rotatably fixedly coupled to the sun gear. 
         [0028]    In particular, in the case that the drive gear section as well as the distribution gear section is designed as a planetary gear set, the intermediate gear may be constructed to be very narrow and in addition lightweight in the axial extension. 
         [0029]    In one preferred refinement of the present invention, the differential device is designed as a differential planetary gear set. In one preferred embodiment, the differential planetary gear set includes an annulus gear, a planetary carrier and a sun gear, two sets of planet wheels being situated on the planetary carrier which mesh in pairs with one another and a set of planet wheels meshing with the annulus gear and the other set of planet wheels meshing with the sun gear. The annulus gear is rotatably fixedly connected to the first interface and in addition to the first output of the intermediate gear. The sun gear is, in particular, rotatably fixedly coupled to one of the output shafts; the planetary carrier is, in particular, rotatably fixedly coupled to the other output shaft. 
         [0030]    Particularly preferably, the first and the second outputs of the transmission as well as the first and the second inputs of the intermediate gear are designed as output or input gears which are circumferential and/or toothed on the front side, these wheels having the same diameter, in particular. The shifting device may include a shifting member having coupling areas which are spaced apart from one another in the axial direction; the coupling areas are situated in such a way that in the case of an axial displacement of the shifting member in one direction, the first shifting state, the first drive intermediate shifting state, the second shifting state, the TV intermediate shifting state, and the third shifting state are consecutively selected or set. 
         [0031]    In one possible specific embodiment of the present invention, the transmission is designed as a one-stage transmission planetary gear set. The one-stage transmission gear set includes a sun gear, a planetary carrier as well as an annulus gear. The annulus gear is, in particular, rotatably fixedly connected to a surrounding structure and is thus stationary. The planetary carrier is, in particular, rotatably fixedly coupled to the first output; the sun gear is rotatably fixedly coupled to the second output. At the same time, the sun gear forms the input to the one-stage intermediate gear or is, in particular, rotatably fixedly coupled thereto. 
         [0032]    Alternatively, the transmission may be designed as a two-stage transmission planetary gear set which has a first and a second planet set. Each of the planet sets includes a sun gear, a planetary carrier as well as a set of planet wheels. An annulus gear of the first and the second planet sets is designed as a joint annulus gear. The input of the transmission planetary gear set is coupled, in particular rotatably fixedly connected, to the sun gear of the first planet set. The first output is rotatably fixedly connected to the planetary carrier of the second planet set; the second output is coupled, in particular rotatably fixedly connected, to the sun gear of the second planet set. The joint annulus gear is situated stationary in a surrounding structure, in particular a housing. The planetary carrier of the first planet set is rotatably fixedly coupled to the sun gear of the second planet set. In this embodiment, the transmission ratio may be implemented to be higher. 
         [0033]    In one particularly preferred embodiment of the present invention, the drive planetary gear set, the distribution planetary gear set, and the transmission planetary gear set, in particular the one- or two-stage transmission planetary gear set, are situated coaxially to a joint main axis of rotation. In addition, the differential planetary gear set may optionally also be situated coaxially to this joint main axis of rotation. Due to this construction, a great compactness of the drive device may be achieved on the one hand, and the design of the shifting unit is considerably simplified on the other hand. 
         [0034]    In one possible refinement of the present invention, the drive device includes the first and the second engines, the first engine being designed as an internal combustion engine and the second engine being designed as an electric motor. This embodiment has the advantage that the electric motor may be rotated in any arbitrary direction for the purpose of generating a drive torque for the second interface so that the torque distribution may be easily implemented. 
         [0035]    A rotor axis of the electric motor is particularly preferably situated coaxially to the joint main axis of rotation. Alternatively, the rotor axis of the electric motor is offset in parallel to the joint main axis of rotation. 
         [0036]    Another object relates to a vehicle including the drive device, the two output shafts being optionally assigned to the front axle or to the rear axle of the vehicle. 
     
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
         [0037]    Other features, advantages, and effects of the present invention are derived from the following description of preferred exemplary embodiments of the present invention as well as from the accompanying figures. 
           [0038]      FIG. 1  shows a schematic representation of a drive device as a first exemplary embodiment of the present invention; 
           [0039]      FIGS. 2 through 6  show the drive device from  FIG. 1  in different shifting states; 
           [0040]      FIG. 7  shows a first variant of the drive device from the preceding figures; and 
           [0041]      FIG. 8  shows a second variant of the drive device from the preceding figures. 
       
    
    
     DETAILED DESCRIPTION 
       [0042]      FIG. 1  illustrates in a schematic representation a drive device  1  for a vehicle  2  as one exemplary embodiment of the present invention. Drive device  1  includes two output shafts  3   a, b  which are drivably coupled to the wheels of vehicle  2 . It is possible in this case that output shafts  3   a, b  are rotatably fixedly connected to the wheels or via a further gear. Output shafts  3   a, b  define a joint output axle  4 . In addition, the output shafts define a main axis of rotation  5 . 
         [0043]    Vehicle  2  includes a first engine  6 , which is designed as an internal combustion engine, as well as a second engine  7 , which is designed as an electric motor, for the purpose of generating a drive torque for output shafts  3   a, b . First engine  6  is connected to drive device  1  via a first interface  8 ; second engine  7  is coupled to drive device  1  via a second interface  9 . The drive torque of engines  6 ,  7  is guided into drive device  1  via interfaces  8 ,  9 . 
         [0044]    From a schematic point of view, drive device  1  includes a differential planetary gear set  10  as a differential device, an intermediate gear  11 , a transmission planetary gear set  12  as a transmission as well as a shifting device  13  which is able to couple transmission  12  and intermediate gear  11  to one another in different shifting states. 
         [0045]    Differential Planetary Gear Set  10 : 
         [0046]    Differential planetary gear set  10  includes a sun gear  14 , a planetary carrier  15 , an annulus gear  16  as well as two sets of planet wheels  17 ,  18 . The two sets of planet wheels  17 ,  18  are rotatably situated on planetary carrier  15 . The two sets of planet wheels  17 ,  18  mesh in pairs with one another so that a planet wheel of set  17  meshes with a planet wheel of set  18  in each case. In addition, the planet wheel of set  17  meshes with sun gear  14  and the planet wheel of set  18  meshes with annulus gear  16 . 
         [0047]    Planetary carrier  15  forms a first output of differential planetary gear set  10  and is rotatably fixedly connected to output shaft  3   a.  Sun gear  14  forms a second output of differential planetary gear set  10  and is rotatably fixedly connected to output shaft  3   b . Annulus gear  16  includes a ring gear T which meshes with a pinion shaft R, ring gear T forming first interface  8 . Sun gear  14 , planetary carrier  15 , and annulus gear  16  are situated coaxially to main axis of rotation  5 . 
         [0048]    Differential planetary gear set  10  has the function of evenly distributing the drive torque of first engine  6  to output shafts  3   a, b.    
         [0049]    Transmission Planetary Gear Set  12 : 
         [0050]    Transmission planetary gear set  12  includes a first planet set  19   a  and a second planet set  19   b.  Both planet sets  19   a, b  have a joint annulus gear  20 . First planet set  19   a  includes a sun gear  21 , a planetary carrier  22  as well as a set of planet gears  23 . Sun gear  21  forms second interface  9  and is rotatably fixedly coupled to a rotor shaft  24  of second engine  7  in this exemplary embodiment. The set of planet gears  23  meshes, on the one hand, with joint annulus gear  20  and on the other hand, with sun gear  21 . Sun gear  21  thus forms an input to transmission planetary gear set  12 . 
         [0051]    Second planet set  19   b  includes a sun gear  25 , a planetary carrier  26 , and a set of planet gears  27 , planet gears  27  meshing with sun gear  25  and joint annulus gear  20 . Sun gear  25  of second planet set  19   b  is rotatably fixedly connected to planetary carrier  22  of first planet set  19   a  so that planetary carrier  22  forms an intermediate output. 
         [0052]    Planetary carrier  26  forms a first output of transmission planetary gear set  12 . Sun gear  25  forms a second output of transmission planetary gear set  12 . 
         [0053]    Planetary carrier  26  is rotatably fixedly coupled to a first output gear  28 ; sun gear  25  is rotatably fixedly coupled to a second output gear  29 . First and second output gears  28 ,  29  are situated coaxially to main axis of rotation  5 . 
         [0054]    Intermediate Gear  11 : 
         [0055]    Intermediate gear  11  includes a drive planetary gear set  30  as the drive gear section and a distribution planetary gear set  31  as the distribution gear section. Drive planetary gear set  30  includes a sun gear  32 , a planetary carrier  33 , and an annulus gear  34 , annulus gear  34  being situated in a surrounding structure U just as is joint annulus gear  20 . Sun gear  32  is rotatably fixedly coupled to a first input gear  36 . A set of planet wheels  37  meshes with sun gear  32  and annulus gear  34 . Sun gear  32  forms the input to drive planetary gear set  30 . Planetary carrier  33  forms the first output of drive planetary gear set  30  or of intermediate gear  11  and is rotatably fixedly connected to annulus gear  16  of differential planetary gear set  10 . 
         [0056]    Distribution planetary gear set  31  includes a sun gear  38 , a planetary carrier  39 , an annulus gear  40  as well as a set of planet gears  41 , set of planet gears  41  meshing with sun gear  38  and annulus gear  40 . Annulus gear  40  simultaneously forms a second input gear  42 . Planetary carrier  39  is rotatably fixedly coupled to output shaft  3   b.  Sun gear  38  is rotatably fixedly coupled to first input gear  36  and at the same time to sun gear  32  of drive planetary gear set  30 . 
         [0057]    First input gear  36 , second input gear  41 - 42  as well as planetary carriers  33 ,  39  are situated coaxially to main axis of rotation  5 . 
         [0058]    Shifting Device  13 : 
         [0059]    Shifting device  13  is used to set the different shifting states so that intermediate gear  11  and transmission planetary gear set  12  may assume different operating states. For this purpose, output gears  28 ,  29  are differently rotatably fixedly connected to input gears  36 ,  42 . The wheels are situated in series in the sequence of first output gear  28 , second output gear  29 , second input gear  42 , and first input gear  36 . Gears  28 ,  29 ,  36 ,  42  each have the same outer diameter. 
         [0060]    Shifting device  13  includes a shifting member  43  which is situated displaceably in the axial direction and which includes three coupling areas  44   a, b, c , free areas being situated between coupling areas  44   a, b, c . Coupling areas  44   a, b, c  are designed to engage in a rotatably fixed coupling with gears  28 ,  29 ,  36 ,  42  in the case of an overlap in the axial direction. If one of gears  28 ,  29 ,  36 ,  42  is situated in one of the free areas, shifting member  43  and the wheel in the free area are not coupled in the circumferential direction. Shifting member  43  may, for example, be designed in the form of a sleeve having internal toothing or as a shift collar. The activation of shifting member  43  may be carried out electromechanically, electrohydrostatically, hydraulically, or electromagnetically. 
         [0061]    The different shifting states of shifting device  13  are described in conjunction with the following figures: 
         [0062]      FIG. 2  shows first shifting state I, first output gear  28  being rotatably fixedly coupled to first input gear  36  via shifting member  43 . For this purpose, coupling area  44   a  engages in an operative connection with first input gear  36  and coupling area  44   b  engages in an operative connection with first output gear  28 . In this shifting state, the drive torque for output shafts  3   a, b  may be optionally generated via second engine  7  or as a hybrid drive jointly via first engine  6  and second engine  7 . The torque flow from second engine  7  is illustrated in  FIG. 2  as a dashed line and runs from rotor shaft  24  via the two planet sets  19   a, b  and output gear  28 , shifting member  43 , first input gear  36 , and drive planetary gear set  30  to differential planetary gear set  10 . The drive torque flow of first engine  6  is not illustrated, but it runs from first interface  8  via differential planetary gear set  10  to output shafts  3   a, b.    
         [0063]    As illustrated in  FIG. 3 , a drive intermediate shifting state N (neutral) may be achieved with the aid of an axial offset of shifting member  43 , first coupling area  44   a  still being in operative connection with first input gear  36 , second coupling area  44   b,  however, being situated between first and second output gears  28 ,  29  so that these two are freewheeling. In this drive intermediate shifting state N, second engine  7  is in a neutral position so that it may set—decoupled from output shafts  3   a, b —its rotational speed in any arbitrary way. If during operation of vehicle  2  it is shifted from first shifting state Ito second shifting state II, second engine  7  must be adapted with respect to its rotational speed during the transition. This may take place in drive intermediate shifting state N. 
         [0064]    In  FIG. 4 , second shifting state II is illustrated, first coupling area  44   a  being in operative connection with, i.e., being rotatably fixedly coupled to, first input gear  36 , second coupling area  44   b  now, however, being in operative connection with second output gear  29 . The plotted torque flow from second engine  7  to output shafts  3   a, b  now runs via second output gear  29 . The speed-transformation is reduced in second shifting state II so that, for the same input rotational speed at second interface  9 , a higher output rotational speed is applied at the used output of transmission planetary gear set  12  in comparison to first shifting state I. The torque flow is again illustrated using a dashed line, the difference from  FIG. 2  being that the transition from transmission planetary gear set  12  to intermediate gear  11  takes place via second output gear  29 . 
         [0065]    In  FIG. 5 , a TV intermediate shifting state NTV is shown, first coupling area  44   a  still being engaged with first input gear  36 , and second coupling area  44   b  and third coupling area  44   c  being free. In this second TV intermediate shifting state, second input gear  42  and first and second output gears  28 ,  29  may rotate freely. As far as the shifting sequence is concerned, it is shifted from a hybrid transmission to a transmission having an active torque distribution. During the transition from the function of the hybrid transmission to the function of the torque distribution, first or second output gears  28 ,  29  and thus second engine  7  must be decelerated. In order to achieve this, the TV intermediate shifting state is used. 
         [0066]    By further offsetting shifting member  43  in the axial direction, first coupling area  44   a  is decoupled from first input gear  36 . In contrast, second coupling area  44   b  is in operative connection with second input gear  42  and third coupling area  44   c  is in operative connection with first output gear  28 . As is apparent from the illustrated torque flow, it is now possible to bring about an active torque distribution through the activation of second engine  7  by actively rotating second input gear  42  clockwise or counterclockwise. 
         [0067]      FIG. 7  shows a first variant of drive device  1  from the preceding figures, transmission planetary gear set  12  being designed as a simply reducing planet gear set which now only includes second planet set  19   b.  Annulus gear  20  is assigned exclusively to planet set  19   b.  Rotor shaft  24  or second interface  9  is rotatably fixedly connected to sun gear  25  which forms the input to transmission  12 . The functionality of shifting device  13  corresponds to the functionality described in the preceding figures. 
         [0068]      FIG. 8  illustrates a second variant of drive device  1  from the preceding figures, second engine  7  being designed as an electric motor and being offset in parallel to main axis of rotation  5  with its rotor shaft  24 . The drive torque from second engine  7  is supplied via an additional gear  45  which, on the one hand, compensates for a parallel offset between the rotor shaft and main axis of rotation  5  and, on the other hand, forms a first transmission stage. 
         [0069]    It must be stressed that shifting states  1 , first intermediate shifting state NTV, and second intermediate shifting state TV may be assumed through a serial displacement of the shifting member in a single axial direction. In order to achieve this, it is particularly advantageous that first input gear  36 , second input gear  42 , first output gear  28 , and second output gear  29  have the same outer diameter. Shifting member  43  may, for example, be designed in the form of a sleeve having internal toothing with/without an undercut analogously to a sliding collar. The activation of shifting member  43  is preferably electromechanical, furthermore electrohydrostatic, hydraulic, or electromagnetic. 
         [0070]    With the aid of shown drive device  1  it is achieved that the shifting takes place in a defined sequence so that at any point in time or shifting point only one function (drive, neutral, TV) is implemented in order to avoid a maloperation (e.g., simultaneous activation of TV and drive). The sequence may reach the different shifting states without reversal of the direction of shifting member  43 , thus resulting in a rapid as well as reliable shifting. 
       LIST OF REFERENCE NUMERALS 
       [0000]    
       
           1  drive device 
           2  vehicle 
           3   a, b  output shafts 
           4  output axle 
           5  main axis of rotation 
           6  first engine 
           7  second engine 
           8  first interface 
           9  second interface 
           10  differential planetary gear set 
           11  intermediate gear 
           12  transmission planetary gear set 
           13  shifting device 
           14  sun gear 
           15  planetary carrier 
           16  annulus gear 
           17  planet wheels 
           18  planet wheels 
         T ring gear 
         R pinion shaft 
           19   a, b  planet sets 
           20  annulus gear 
           21  sun gear 
           22  planetary carrier 
           23  planet gears 
           24  rotor shaft 
           25  sun gear 
           26  planetary carrier 
           27  planet gears 
           28  first output gear 
           29  second output gear 
           30  drive planetary gear set 
           31  distribution planetary gear set 
           32  sun gear 
           33  planetary carrier 
           34  annulus gear 
           35  surrounding structure 
           36  first input gear 
           37  planet wheels 
           38  sun gear 
           39  planetary carrier 
           40  annulus gear 
           41  planet gears 
           42  second input gear 
           43  shifting member 
           44   a, b, c  coupling areas 
           45  additional gear