DE102008063107A1 - Differential gear for use as intermediate axle differential in drive train of motor vehicle to distribute torque, has planetary gear wheel with conical toothing section that combs with one or both of secondary gear wheels - Google Patents

Abstract

The gear has a planetary gear wheel (32) that is rotatably supported at an outer side of a primary shaft (12). The gear wheel has a rotational axis (DA) that points transverse to a central axis (ZA), and a secondary gear wheel (18) that is rotatably supported on the shaft. Another secondary gear wheel (20) is supported rotatably on the shaft. The planetary gear wheel has a conical toothing section (40) that tapers radially outward with respect to the central axis. The toothing section combs with one or both of the secondary gear wheels.

Description

The The present invention relates to a differential with a Primary wave, which is relative to a central axis the differential gear is rotatable, at least two planetary gears, rotatable on the outside of the primary shaft are mounted and each one transverse to the central axis facing axis of rotation comprising a first secondary gear rotatably on the primary shaft is supported, and a second secondary gear, which is rotatably mounted on the primary shaft.

such Differential gears can be used in a powertrain of a Motor vehicle be provided as a central differential (also inter-axle differential called) acting in the longitudinal direction to a drive torque distribute between the axles of the motor vehicle. The named Central axis can in this case in particular in the longitudinal direction or aligned in the transverse direction of the associated motor vehicle be. For example, the primary shaft is a drive shaft educated. Alternatively, the drive can also over one of the secondary gears done. through through the secondary gears and the planetary gears formed planetary gear is a torque split between accomplished two output elements. Differential gear of the mentioned type can in a drive train of a motor vehicle also be provided as Achsedifferenziale, in the transverse direction are effective to drive torque on the two axle shafts of the same Distribute vehicle axle.

Zentraldifferiale, in which the planetary gears are not stored in a differential cage, but on the outside of the primary shaft are, for example, from US 5,304,103 known.

at These known differential gears are the planetary gears formed as bevel gears and stored such that the Cone tip to the central axis out points, the toothed area the planetary gears so tapers radially inward. The during operation of the differential gear on the planet gears exerted axial forces (i.e., in radial direction with respect to said central axis) Direction forces) thus point from the central axis away and have to go outside at the planet carrier be supported. Such support can elaborate safety devices on the bearing components make the planet gears necessary, such. B. retaining washers or locking pins. Besides, it can be difficult Differential gear of the type mentioned as possible clearance adjust.

Of the Invention is therefore based on the object, a generic To provide differential gear, the above Disadvantages avoids.

The This object is achieved by the features of the claim 1 and in particular in that each of the planetary gears at least one radially outward with respect to the central axis having tapered bevel gear portion, which with the first secondary gear and / or the second secondary gear combs.

Across from the known differential gears is the gear alignment the planet gears and the secondary axial gears So at least partially inverted. In other words, it shows relevant bevel gear portion of the respective planetary gear essentially radially outward while the Hereby meshing secondary gear a Verzahnungsabschnitt having, with respect to the genann th central axis substantially directed radially inward. Through this gearing inversion is achieved that due to a torque transmission and the mutual rolling of the respective tooth flanks the planetary gears acting axial forces in Reference to the central axis at least partially radially inward are directed. This allows the planetary gears easily and reliably supported on the primary shaft be so on the planet carrier appropriate support measures outwardly dispensable or significantly weaker or can be made lighter than conventional Differential gears.

One Another advantage results from the fact that during the Operation due to outward centrifugal forces an automatic clearance compensation between the planetary gears and the secondary gears becomes. In differential gears with conventionally aligned Bevel gears as planetary gears, the centrifugal forces act a clearance compensation straight contrary.

From Another advantage is that the two secondary gears are rotatably mounted on the primary shaft, as a result also with regard to the secondary gears a simple and reliable radial centering relative is reached to the primary wave. Because of the usual low rotational speeds of the primary shaft, the first Secondary gear and the second secondary gear relative to each other can be explained for the coaxial bearing these three elements relative to each other simple Needle roller bearings are used.

In the context of the invention, the planet gears may have a plurality of different bevel gear sections, for example, with different cone angles and / or with one to additional Kegelver zahnungsabschnitt which is tapered radially inwardly in a conventional manner. In the latter case, a partial compensation of forces can be achieved. If the axis of rotation of the respective planetary gear is not exactly perpendicular and not aligned parallel to the central axis of the differential gear but obliquely thereto, there is a radially outwardly tapered bevel gear portion according to the invention then, when the bevel gear portion along the direction away from the central axis direction of Rotary axis of the planetary gear is tapered.

further developments of the invention can be attached to the attached claims, the description and the drawing are taken.

According to one advantageous embodiment of the invention is each of Planetary gears as a bevel gear with a single in Regarding the central axis tapered radially outward Tapered portion formed with the first secondary gear and the second secondary gear meshes. This particularly simple construction corresponds to one opposite the above conventional bevel gear variant completely inverted configuration. This embodiment is suitable Especially good, with respect to the two secondary gears as output elements an equally high torque distribution (50:50) represent, especially in an axle differential. Indeed is an asymmetric torque distribution possible, for example, if the respective axis of rotation of the planetary gears with respect to a purely rectangular orientation to the Central axis of the differential gear is inclined.

According to one Another embodiment of the invention, each of the planetary gears further, a radially inwardly tapered with respect to the central axis Bevel gear section, which is connected to the first secondary gear or the second secondary gear meshes. To this Way can also be a distribution of different torques on the two output elements (eg the two secondary gears) can be achieved, wherein by the radially outwardly tapered bevel gear portion radially inwardly directed force components are effected, which the support of the planetary gears on the primary shaft facilitate. The radially inwardly tapered bevel gear portion and the radially outwardly tapered bevel gear portion can rotatably connected to each other (in particular integrally formed) be to a double-cone shape of the respective planetary gear form.

Of the radially inwardly tapered bevel gear portion of a Each planetary gear can in particular mesh with the first secondary gear and the radially outwardly tapered bevel gear portion of each planetary gear can with the second secondary gear combing (or vice versa), so that the two secondary gears in each case a different toothing section is assigned.

Preferably is the gear ratio (according to the Number of teeth ratio) between the radially inward tapered bevel gear portion and the first secondary gear from the gear ratio (or the number of teeth) between the radially outwardly tapered bevel gear portion and the second secondary gear different to simple Way a distribution of different torques to the to reach both secondary gears.

Of the radially tapered outward tapered section and the radially inwardly tapered bevel gear portion each Plane tenzahnrads can each other at the respective cone base adjoin. This results in an easy to manufacture in this case and particularly stable "O" or "diamond" shape the planetary gears. Alternatively, the mentioned Adjacent bevel gear sections at the respective apex of the cone, to form an "X" shape. In both cases can the two bevel gear sections under training border one another or continuously merge into one another.

According to another embodiment of the invention, each of the planetary gears further includes a further radially outwardly tapered bevel gear portion concentric with the radially outwardly tapered bevel gear portion, which meshes with the first secondary gear or the second secondary gear. So there are two different, but rotatably interconnected radially outwardly tapered bevel gear sections. In particular, the two bevel gear portions are offset with respect to the axis of rotation of the respective planetary gear in the axial direction to each other. Preferably, one of the radially outwardly tapered bevel gear portions of each planetary gear meshes with the first secondary gear and the other of the radially outwardly tapered bevel gear portions of each planetary gear meshes with the second secondary gear. The two conically tapered tapered radially outward portions may, for example, adjacent to each other with the formation of a step or continuously merge into each other (with or without kink of the generatrices). With regard to the two bevel gear sections, different cone angles and / or different axis crossing points can be used be provided.

Prefers is the gear ratio (according to the Teeth ratio) between the one of the radial outwardly tapered bevel gear sections and the first secondary gear from the gear ratio between the other of the radially outwardly tapered Bevel gear sections and the second secondary gear different, so that again a distribution of different Torques to the first and the second secondary gear results.

The respective rotational axis of the planetary gears pointing transversely to the central axis can be exactly perpendicular with respect to the central axis of the differential gear be aligned. In this variant, the planet carrier very simple. Alternatively, the respective axis of rotation of the Planetary gears also in a different from 90 ° Inclination angle with respect to the central axis of the differential gear be aligned. Such inclined planetary gears describe with their Verzahnungsbereich example on the the first secondary gear side facing a circulation circuit with larger diameter than on the second Secondary gear facing side, so the possibility results in the respective secondary gears different torques transferred to. With such a designed differential gear So, for example, to the front axle and to the Rear axle of a motor vehicle different proportions of the introduced Drive torque can be distributed.

According to one advantageous embodiment of the invention are exactly two each other opposite planetary gears with one common axis of rotation on the outside of the primary shaft stored. Two opposite planet gears correspond a particularly simple and material-saving construction, the one mutual compensation of forces allows. Especially can the planetary gears on one in the Be mounted primary shaft sitting bolt. Such a Bolt can be formed one or more parts. In such a Training are for storage of the planetary gears only a few simple to produce components required. alternative can also have three, four or more planetary gears in even or uneven Division provided along the circumference of the primary shaft be. For this purpose, for example, a planet carrier be provided with star-shaped protruding bearing pin, wherein the planet carrier rotatably connected to the primary shaft is. The required number of planetary gears are aimed according to the respective performance specifications for the differential gear.

Around a distribution of different torques on the two To achieve secondary gears can the first secondary gear and the second secondary gear a different number of teeth and / or a different effective diameter exhibit. In this way, the desired different transmission ratio achieved.

The first secondary gear or the second secondary gear can be rotatably connected to a secondary shaft whose one end is formed as a hollow shaft and surrounds one end of the primary shaft. In particular, the relevant secondary gear can also be formed integrally with the secondary shaft. On the secondary shaft, a mounting flange can be provided be. The axis of rotation of the primary shaft, the axis of rotation of the Secondary shaft and the central axis of the differential gear coincide with this configuration.

According to one Another embodiment is the first secondary gear or the second secondary gear with a connecting wheel rotatably connected (in particular integrally formed). The connecting wheel is one with respect to the primary shaft offset or transversely (i.e., at right angles or in one from 90 ° different inclination angle) aligned secondary shaft drive-connected. The connec tion wheel can be used as a gear, Sprocket or pulley be formed and, for example directly or via a drive chain, a belt or an intermediate gear with a gear of a secondary shaft drive-effectively coupled to form an offset drive. The said compound wheel may also be part of a transmission form, for example, an angle drive or a translation stage. This transmission can be used, for example, as a helical gear, bevel gear, Schraubradgetriebe or Beveloidradgetriebe be formed.

The first secondary gear and / or the second secondary gear is preferably as a bevel gear with a bevel gear portion formed, which is complementary to the associated bevel gear portion the planet gears is aligned. This gives a simple construction of the secondary gears, where these can be connected to other drive components.

The invention also relates to a drive train of a motor vehicle having a drive unit, a first axle, a second axle and a differential gear of the type described above, which distributes a drive torque generated by the drive unit to the first axle and the second axle. In other words, the invention also relates to a drive train with a central differential. Furthermore, the invention relates to a drive train of a motor vehicle zeugs with a first axle of a vehicle axle, a second axle of the same vehicle axle and a differential gear of the type described above, which distributes a drive torque to the first axle and the second axle. In other words, the invention also relates to a drive train having a transversely effective axle differential.

The Differential gear according to the invention can therefore in different forms for torque distribution be inserted between two output elements. The invention in the following is merely an example in connection with a Central differential in a drive train of a motor vehicle described.

1a and 1b show a differential gear according to the invention according to a first embodiment in a longitudinal section and in a perspective view.

2a and 2 B show a differential gear according to the invention according to a second embodiment in a longitudinal section and in a perspective view.

3a and 3b show a differential gear according to the invention according to a third embodiment in a longitudinal section and in a perspective view.

4a and 4b show a differential gear according to the invention according to a fourth embodiment in a longitudinal section and in a perspective view.

5a and 5b show a differential gear according to the invention according to a fifth embodiment in a longitudinal section and in a perspective view.

This in 1a shown in section and in 1b Differential shown in perspective for a drive train of a motor vehicle comprises a housing 10 , a primary wave 12 (For example, forms an input element of the differential gear), a secondary shaft 14 and a connection gear 16 (For example, form two output elements of the differential gear). The primary wave 12 is by means of a ball bearing serving as a fixed bearing 13 with respect to a central axis ZA of the differential gear in the housing 10 rotatably mounted. The secondary shaft 14 is by means of a likewise serving as a fixed bearing ball bearing 15 with respect to the central axis ZA in the housing 10 rotatably mounted. The secondary shaft 14 includes a mounting flange 17 with a hollow shaft section 19 who in the 1a and 1b right end of the primary shaft 12 surrounds. The connecting gear 16 is designed as a helical spur gear. A first secondary gear 18 is with the connecting gear 16 integrally formed and is by means of a radial bearing 22 and a thrust bearing 24 rotatable on the primary shaft 12 stored. In the same way is a second secondary gear 20 by means of a radial bearing 26 and a thrust bearing 28 rotatable on the primary shaft 12 stored. The second secondary gear 20 is non-rotatable with the hollow shaft section 19 the secondary shaft 14 connected.

Between the first secondary gear 18 and the second secondary gear 20 is seated at a right angle to the central axis ZA aligned bolt 30 in the primary wave 12 , which two opposing planetary gears 32 wearing. The planetary gears 32 are by means of radial bearings 34 rotatable on the bolt 30 stored and mesh with the first secondary gear 18 and the second secondary gear 20 , In the direction of the central axis ZA (ie radially inward) are the planetary gears 32 directly on the outside of the primary shaft 12 supported. In the opposite direction, ie radially outward, are the planetary gears 32 by security elements 36 held.

The arrangement of a bolt 30 with the two planetary gears 32 and the first secondary gear 18 and the second secondary tooth wheel 20 forms a planetary gear, which is the primary shaft 12 drive effective with the secondary shaft 14 and the connecting gear 16 coupled.

The planetary gears 32 are as bevel gears with a respective bevel gear portion 40 formed, with the cone base facing towards the central axis ZA, the bevel gear portion 40 that is, tapered radially outward. Due to this design of the planetary gears 32 results in transmission of torque, a support on the primary shaft 12 , which supports the axial forces occurring during operation of the differential gear (with respect to the axis of rotation DA). The security elements 36 can therefore be designed accordingly easy, and it is also no special axial fixation of the bolt 30 required. With a rotation of the primary shaft 12 and thus the bolt 30 The centrifugal forces print the planetary gears 32 radially outward, thereby reducing the backlash of the planetary gear.

The illustrated differential gear serves to distribute a drive torque from an input element to two output elements of the differential gear. The primary wave 12 , the secondary wave 14 or the connecting gear 16 forms the input element, while the respective two other mentioned parts form the two output elements.

When used as a central differential, the input member is drivably coupled to a drive unit of the motor vehicle, and the two output members are drivably coupled to a respective vehicle axle. In particular, a via the primary wave 12 initiated drive torque to equal proportions on the secondary shaft 14 on the one hand and via the connecting gear 16 and an offset drive or angle drive on another secondary shaft (not illustrated sets) on the other hand be distributed. For example, in a front engine arrangement, the secondary shaft 14 be drivingly coupled to a rear axle of the motor vehicle, and the connecting gear 16 via an offset drive with a front axle. Alternatively, for example, in a mid-engine or rear engine assembly, the secondary shaft 14 (over the mounting flange 17 ) are drivingly coupled to the front axle, and the connecting gear 16 Furthermore, it is also possible that the two secondary gears 18 and 20 are coupled via a respective offset drive or angle drive with an associated secondary shaft.

Alternatively, for example, the secondary shaft 14 act as an input element and a torque on the primary shaft 12 and transmit the said further secondary shaft. According to a further alternative, the connecting gear 16 form the input element to a drive torque on the primary shaft 12 and the secondary shaft 14 distribute, with the primary wave 12 or the secondary shaft 14 is coupled for example with an angle drive.

As a general rule The differential gear shown can also be considered a in the transverse direction effective axle differential reach the application.

With reference to the 2 to 5 Now further embodiments of the invention will be described. Components that function in the components of 1 are denoted by the same reference numerals.

At the in 2 shown differential gear have the planetary gears 42 in addition to the radially outwardly tapered bevel gear portion 44 a radially inwardly tapered Kegelverzah voltage section 46 on. The radially inwardly tapered bevel gear portion 46 closes immediately to the radially outwardly tapered bevel gear portion 44 on, so the planetary gears 42 overall have a compact double cone shape. The radially outwardly tapered bevel gear portion 44 meshes with the second secondary gear on the right side of the picture 20 during the radially inwardly tapered bevel gear portion 46 on the left in the picture with the first secondary gear 18 combs. The second secondary gear 20 has a larger diameter and - with the same pitch - a larger number of teeth than the first secondary gear 18 , Thus, the gear ratio between the radially outwardly tapered bevel gear portion 44 and the second secondary gear 20 from the gear ratio between the radially inwardly tapered bevel gear portion 46 and the first secondary gear 18 different. In this way it is achieved that by the primary shaft 12 mediated drive torque in uneven distribution to the secondary shaft 14 and the connection gear 16 is transmitted.

In the embodiments according to 3 and 4 have the planetary gears 52 a first outwardly tapered bevel gear portion 54 and a second outwardly tapered bevel gear portion 56 on, which are rotatably connected to each other and in particular on a one-piece planetary gear 52 are formed. According to 3 may be between the first bevel gear portion 54 and the second bevel gear portion 56 an approach or a stage be formed. 4 shows a variant in which between the first outwardly tapered bevel gear portion 54 and the second outwardly tapered bevel gear portion 56 no stage is formed. In this embodiment, therefore, go the two bevel gear sections 54 . 56 continuously into each other, without kink of the generatrices, ie the two bevel gear sections 54 . 56 have the same cone angle. As can be seen from the figures, the first outwardly tapered bevel gear section meshes in both variants 54 on the right side with the second secondary gear 20 , and the second outwardly tapered bevel gear portion 56 meshes with the first secondary gear 18 , Due to the different effective diameters of the first secondary gear 18 and second secondary gear 20 in turn results in an uneven torque distribution between the first and second output element.

At the in 5 shown differential gear are as in the first embodiment according to 1 Planet gears 32 with only one bevel gear portion tapered radially outward 40 intended. The axes of rotation DA of the planetary gears 32 are inclined relative to the central axis ZA of the differential gear by a deviating from 90 ° angle. Instead of a single bolt rotates with the primary shaft 12 connected ring element 60 with several bearing bolts attached to it 61 for storage of the planet gears 32 on the primary wave 12 used. Due to the inclination of the axes of rotation DA is the radially outwardly tapered bevel gear portion 40 at the location of the second secondary gear 20 radially outward than at the location of the first secondary gear 18 , This in turn allows secondary gears 18 . 20 be used with unequal effective diameter.

In this embodiment, a planet carrier ring 62 instead of the individual security elements 36 intended. The planet carrier ring 62 is at the bearing pin 61 attached and secures them radially outward. Optionally, the planet carrier ring 62 also at the primary wave 12 be solidified. Such a planet carrier ring 62 may also be provided in the other embodiments explained above.

The principles explained above of the inclination of the planetary rotary axes DA according to 5 and the combination of different bevel gear sections 44 . 46 . 54 . 56 according to 2 . 3 and 4 can be combined in many ways depending on the particular application.

While in the figures by way of example two planetary gears 32 . 42 . 52 are shown, a different number of planetary gears is possible (for example, three, four or five).

10

casing

12

primary shaft

13

ball-bearing

14

secondary shaft

15

ball-bearing

16

connecting gear

17

mounting flange

18

first Secondary gear

19

Hollow shaft section

20

second Secondary gear

22

radial bearings

24

thrust

26

radial bearings

28

thrust

30

bolt

32

planetary gear

34

radial bearings

36

fuse element

40

radial outwardly tapered bevel gear section

42

planetary gear

44

radial outwardly tapered bevel gear section

46

radial inwardly tapered bevel gear section

52

planetary gear

54

radial outwardly tapered bevel gear section

56

radial outwardly tapered bevel gear section

60

ring element

61

bearing bolt

62

Planet carrier ring

ZA

central axis

THERE

Planetary axis of rotation

QUOTES INCLUDE IN THE DESCRIPTION

This list The documents listed by the applicant have been automated generated and is solely for better information recorded by the reader. The list is not part of the German Patent or utility model application. The DPMA takes over no liability for any errors or omissions.

Cited patent literature

• US 5304103 [0003]

Claims (18)

Differential gear with a primary shaft ( 12 ) which is rotatable relative to a central axis (ZA) of the differential gear, at least two planetary gears ( 32 . 42 . 52 ) located on the outside of the primary shaft ( 12 ) are rotatably mounted and each have a transverse to the central axis (ZA) facing axis of rotation (DA), a first secondary gear ( 18 ) rotatable on the primary shaft ( 12 ) is mounted, and a second secondary gear ( 20 ) rotatable on the primary shaft ( 12 ), characterized in that each of the planetary gears ( 32 . 42 . 52 ) at least one with respect to the central axis (ZA) radially outwardly tapered bevel gear portion ( 40 . 44 . 54 ), which is connected to the first secondary gear ( 18 ) and / or the second secondary gear ( 20 ) combs. Differential gearing according to claim 1, wherein each of the planetary gears ( 32 ) as a bevel gear with a single bevel gear section tapered radially outward with respect to the central axis (ZA) ( 40 ) formed with the first secondary gear ( 18 ) and the second secondary gear ( 20 ) combs. Differential gearing according to claim 1, wherein each of the planetary gears ( 42 ) further with respect to the central axis (ZA) radially inwardly tapered bevel gear portion ( 46 ), which is connected to the first secondary gear ( 18 ) or the second secondary gear ( 20 ) combs. Differential gearing according to claim 3, wherein the radially inwardly tapered bevel gear portion (FIG. 46 ) of each planetary gear ( 42 ) with the first secondary gear ( 18 ) and the radially outwardly tapered bevel gear portion (FIG. 44 ) of each planetary gear ( 42 ) with the second secondary gear ( 20 ) combs. Differential gear according to claim 4, wherein the gear ratio between the radially inwardly tapered bevel gear portion ( 46 ) and the first secondary gear ( 18 ) of the transmission ratio between the radially outwardly tapered bevel gear portion ( 44 ) and the second secondary gear ( 20 ) is different. Differential gear according to at least one of claims 3 to 5, wherein the radially outwardly tapered bevel gear portion ( 44 ) and the radially inwardly tapered bevel gear portion (FIG. 46 ) of each planetary gear ( 42 ) adjoin one another at the respective cone base. Differential gearing according to claim 1, wherein each of the planetary gears ( 52 Further, a tapered to the radially outwardly tapered portion ( 54 ) concentric further radially outwardly tapered Kegelverzahnungsab section ( 56 ), which is connected to the first secondary gear ( 18 ) or the second secondary gear ( 20 ) combs. Differential gearing according to claim 7, wherein one of the radially outwardly tapered bevel gear sections (11). 54 . 56 ) of each planetary gear ( 52 ) with the first secondary gear ( 18 ) and the other of the radially outwardly tapered bevel gear sections (FIG. 54 . 56 ) of each planetary gear ( 52 ) with the second secondary gear ( 20 ) combs. A differential gear according to claim 8, wherein the gear ratio between the one of the radially outwardly tapered bevel gear portions ( 54 . 56 ) and the first secondary gear ( 18 ) of the gear ratio between the other of the radially outwardly tapered bevel gear portions (FIG. 54 . 56 ) and the second secondary gear ( 20 ) is different. Differential gear according to at least one of the preceding claims, wherein the respective axis of rotation (DA) of the planet gears ( 32 . 42 . 52 ) is oriented at right angles with respect to the central axis (ZA) of the differential gear. Differential gear according to at least one of claims 1 to 9, wherein the respective axis of rotation (DA) of the planet gears ( 32 . 42 . 52 ) is oriented at a different angle of inclination from 90 ° with respect to the central axis (ZA) of the differential gear. Differential gear according to at least one of the preceding claims, wherein exactly two opposing planetary gears ( 32 . 42 . 52 ) with a common axis of rotation (DA) on the outside of the primary shaft ( 12 ) are stored. A differential gear according to claim 12, wherein the planetary gears ( 32 . 42 . 52 ) on one in the primary wave ( 12 ) sitting bolts ( 30 ) are stored. Differential gear according to at least one of the preceding claims, wherein the first secondary gear ( 18 ) and the second secondary gear ( 20 ) have a different number of teeth and / or a different effective diameter. Differential gear according to at least one of the preceding claims, wherein the first secondary gear ( 18 ) and / or the second secondary gear ( 20 ) with a respective secondary shaft ( 14 ) is rotatably connected, one end of which is formed as a hollow shaft and one end of the primary shaft ( 12 ), the secondary wave ( 14 ) preferably a mounting flange ( 17 ) having. Differential gear according to at least one of the preceding claims, wherein the first secondary gear ( 18 ) and / or the second secondary gear ( 20 ) with a connecting wheel ( 16 ) connected in a rotationally fixed manner with respect to the primary shaft ( 12 ) offset arranged or transversely oriented secondary shaft is drivingly coupled or forms part of a transmission. Differential gear according to at least one of the preceding Claims, wherein the differential gear for torque distribution formed along a longitudinal axis of a motor vehicle is. Powertrain of a motor vehicle, with a first Axis, a second axis and a differential gear after at least one of the preceding claims to a drive torque to distribute on the first axis and the second axis.