DE102022004088A1 - Transmission device for a motor vehicle and motor vehicle, in particular motor vehicle - Google Patents

Abstract

The invention relates to a transmission device (10) for a motor vehicle, with a spur gear differential (12) which has a first sun gear (14) which is designed as a first output of the spur gear differential (12) and as a first spur gear and has a first pitch circle diameter. The spur gear differential (12) comprises a second sun gear (16) which is arranged coaxially to the first sun gear (14), which is designed as a second output of the spur gear differential (12) and as a second spur gear and has a second pitch circle diameter which is different from the first pitch circle diameter. The spur gear differential (12) comprises at least one planetary gear set (26) by means of which the sun gears (14, 16) are coupled to one another in such a way that the sun gears (14, 16) can rotate in opposite directions, the planetary gear set (26) having a planet carrier (28). The planetary gear set (26) comprises a first differential planetary gear (30) which engages with the first sun gear (14), has a third pitch circle diameter and is held on the planetary carrier (28) so as to be rotatable about a first planetary axis of rotation (32) relative to the planetary carrier (28).

Description

The invention relates to a transmission device for a motor vehicle according to the preamble of patent claim 1. Furthermore, the invention relates to a motor vehicle, in particular a motor vehicle, with such a transmission device.

The EN 10 2014 203 522 A1 a spur gear differential is known. Furthermore, the EN 10 2015 214 035 B4 an electronic drive unit for a motor vehicle. Furthermore, the EN 10 2018 128 836 B3 a transmission device for a motor vehicle is known.

The object of the present invention is to provide a transmission device for a motor vehicle and a motor vehicle with such a transmission device, so that a particularly compact and lightweight design and a particularly high torque density of the transmission device can be realized.

This object is achieved by a transmission device having the features of patent claim 1 and by a motor vehicle having the features of patent claim 15. Advantageous embodiments with expedient further developments of the invention are specified in the remaining claims.

A first aspect of the invention relates to a transmission device for a motor vehicle, also referred to simply as a vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car. This means that the motor vehicle in its fully manufactured state has the transmission device and can be driven via the transmission device, in particular by means of a drive motor of the motor vehicle. In particular, for example, vehicle wheels, also referred to simply as wheels, of the motor vehicle, in particular the same vehicle axle of the motor vehicle, also referred to simply as an axle, can be driven via the transmission device in order to drive the motor vehicle as a whole.

The transmission device has a spur gear differential, which is also referred to as a spur gear differential. The spur gear differential is thus a differential gear, also simply referred to as a differential, which is designed as a spur gear differential. For example, the vehicle wheels mentioned can be driven via the spur gear differential, in particular by a drive shaft of the motor vehicle. The spur gear differential, for example, has the function, which is well known from the prior art, of dividing and transmitting a drive torque provided or available by the drive shaft to the vehicle wheels, in particular to side shafts via which the vehicle wheels can be driven. Furthermore, the spur gear differential, for example, has the function of allowing different speeds of the vehicle wheels and thus the side shafts when the motor vehicle is cornering, such that the vehicle wheel on the outside of the curve can or does rotate at a higher speed than the vehicle wheel on the inside of the curve, in particular while the vehicle wheels can or are driven by the drive shaft via the spur gear differential. The side shafts mentioned can, for example, be part of the spur gear differential. A first of the vehicle wheels can be driven by a first of the side shafts, for example, and a second of the vehicle wheels can be driven by a second of the side shafts. In particular, the side shafts can be arranged coaxially to one another. In particular, the vehicle wheels are arranged on opposite sides of the vehicle in the transverse direction of the motor vehicle, also referred to simply as the vehicle.

The spur gear differential has a first sun gear, which is designed as a first output of the spur gear differential and as a first spur gear. The first sun gear has a first pitch circle diameter. In particular, the first sun gear has a first pitch circle diameter. For example, the first sun gear is connected, in particular permanently, in a rotationally fixed manner to the first side shaft, so that, for example, the first side shaft can be driven by the first sun gear and so that, for example, the first vehicle wheel can be driven by the first sun gear via the first side shaft. The spur gear differential also has a second sun gear, which is designed as a second output of the spur gear differential and as a second spur gear. For example, the second sun gear is connected, in particular permanently, in a rotationally fixed manner to the second side shaft, so that the second side shaft can be driven by the second sun gear. The second vehicle wheel can thus be driven by the second sun gear via the second side shaft. The sun gears are arranged coaxially to one another. In other words, for example, the second sun gear is arranged coaxially to an axis of rotation of the first sun gear. In other words: The first sun gear is rotatable, for example, in particular relative to a housing of the transmission device, about a first sun gear rotation axis. The first sun gear is arranged at least partially in the housing. The second sun gear is rotatable, for example, about a second sun gear rotation axis relative to the housing in which the second sun gear is arranged at least partially, for example, because the sun gears are arranged coaxially to one another, the sun gear rotation axes coincide. In particular, for example, the first side shaft is arranged coaxially to the first sun gear, and for example the second side shaft is arranged coaxially to the second sun gear.

In the context of the present disclosure, the feature that two components are connected to one another in a rotationally fixed manner can be understood to mean that the two components are formed in one piece, thus formed from a single piece and are thereby connected to one another in a rotationally fixed manner, so that the two components formed in one piece are formed as a monoblock, i.e. are formed by a monoblock. In other words, the components formed in one piece are formed by a one-piece and thus integrally manufactured, integral body. Furthermore, it is conceivable that the two components connected to one another in a rotationally fixed manner are formed separately from one another and are connected to one another in a rotationally fixed manner, in particular by a joining technique. The components connected to one another in a rotationally fixed manner are or will be rotatable or rotated about a component rotation axis common to the components, in particular relative to the housing, in particular when the components are driven, so that the components can rotate or rotate together or simultaneously at the same angular velocity about the component rotation axis, in particular relative to the housing. In addition, relative rotations between the components about the component rotation axis are prevented.

The second sun gear, designed as a second spur gear, has a second pitch circle diameter which is different from the first pitch circle diameter. Thus, for example, the first pitch circle diameter is larger than the second pitch circle diameter or vice versa. In particular, the second sun gear has a second pitch circle diameter which is different from the first pitch circle diameter, so that, for example, the first pitch circle diameter is larger than the second pitch circle diameter or vice versa.

The transmission device also has a planetary gear set, which is also referred to as a planetary arrangement or orbiting planetary arrangement. By means of the planetary gear set or via the planetary gear set, the sun gears are coupled to one another in such a way that the sun gears can rotate in opposite directions. This can be understood in particular as the following: The vehicle wheels mentioned are ground contact elements of the motor vehicle, also referred to as the vehicle, which can be or is supported on a ground such as a roadway via the ground contact elements in the vertical direction of the motor vehicle. If the vehicle wheels and thus the motor vehicle are driven so that the motor vehicle is driven along the ground while the motor vehicle is supported on the ground via the ground contact elements (vehicle wheels) in the vertical direction of the vehicle, the vehicle wheels roll, in particular directly, on the ground. If, for example, the motor vehicle is now at least partially raised in such a way that the vehicle wheels do not touch the ground and are, so to speak, floating in the air, and then, for example, the first vehicle wheel and thus the first side shaft and the first sun gear are rotated about the first sun gear axis of rotation in a first direction of rotation, the second sun gear and the second side shaft are thereby driven via the planetary gear set, as is well known from conventional differential gears, and the second vehicle wheel is driven via the second side shaft in such a way that the second sun gear and thus, for example, the second side shaft are rotated about the second sun gear axis of rotation and thus about the first sun gear axis of rotation in a second direction of rotation opposite to the first direction of rotation, thus in the opposite direction to the first sun gear.

The planetary gear set has a planet carrier, which is preferably arranged coaxially to the sun gears. The planet carrier is rotatable, for example, about a planet carrier axis of rotation relative to the housing, wherein the planet carrier can be arranged at least partially in the housing. In particular, it is conceivable that the planet carrier axis of rotation coincides with the sun gear axes of rotation, so that the planet carrier is preferably arranged coaxially to the sun gears. The planetary gear set also has at least one first differential planet gear, which engages in the first sun gear, thus meshes with the first sun gear or is in engagement with the first sun gear. The first differential planet gear has a third pitch circle diameter. In particular, the first differential planet gear has a third pitch circle diameter. For example, the planetary gear set has at least one further or several further first differential planet gears, wherein the previous and following statements on the at least one first differential planet gear can also be easily transferred to the respective, further first differential planet gear and vice versa. When the first differential planetary gear is mentioned above and below, this is to be understood as at least one first differential planetary gear, unless otherwise stated. The first differential planetary gear is connected by a first planet rotation axis is held rotatably on the planet carrier relative to the planet carrier. Preferably, the first planetary rotation axis runs parallel to the respective sun gear rotation axis and/or parallel to the planet carrier rotation axis, wherein preferably the first planetary rotation axis is spaced from the respective sun gear rotation axis and/or from the planet carrier rotation axis.

The planetary gear set also has at least one second differential planet gear. It is conceivable that the planetary gear set has at least one further second or several further second differential planet gears, wherein the previous and following statements on the at least one second differential planet gear can also be easily applied to the respective further second differential planet gear and vice versa. When the second differential planet gear is mentioned above and below, this is to be understood as the at least one second differential planet gear, unless otherwise stated. The second differential planet gear engages with the second sun gear. It is therefore provided that the second differential planet gear meshes with the second sun gear or is in engagement with the second sun gear. The second differential planet gear is held on the planet carrier so as to be rotatable about a second planetary axis of rotation running parallel to the first planetary axis of rotation and spaced apart from the first planetary axis of rotation. For example, the second planetary axis of rotation runs parallel to the respective sun gear axis of rotation and/or parallel to the planet carrier axis of rotation, wherein it is preferably provided that the second planetary axis of rotation is spaced from the respective sun gear axis of rotation and/or from the planet carrier axis of rotation.

The planetary gear set also has at least one coupling planetary gear arranged coaxially to the first differential planetary gear, connected in a rotationally fixed manner to the first differential planetary gear and engaging in the second differential planetary gear, thus engaging with the second differential planetary gear or meshing with the second differential planetary gear and thereby coupling the differential planetary gears to one another, which coupling planetary gear has a fourth pitch circle diameter that is different from the third pitch circle diameter. In particular, the coupling planetary gear has a fourth pitch circle diameter that is different from the third pitch circle diameter. The first differential planetary gear and the second differential planetary gear form, for example, a differential planetary gear group, it being conceivable that the spur differential has at least one further or several further differential planetary gear groups, the previous and following statements on the first differential planetary gear group being readily transferable to the respective further differential planetary gear group and vice versa.

The coupling planetary gear and the first differential planetary gear form a differential stage planetary gear which is held on the planetary carrier so as to be rotatable about the first planetary axis of rotation relative to the planetary carrier. The differential planetary gears and the coupling planetary gear are further spur gears of the spur gear differential. The first differential stage planetary gear has the first differential planetary gear as the first stage planet and the coupling planetary gear as the second stage planet. In other words, the first differential planetary gear is also referred to as the first stage planet and the coupling planetary gear is also referred to as the second stage planet. It is conceivable that the spur gear differential has at least one further or several further differential stage planetary gears, wherein the previous and following statements regarding the first differential stage planetary gear can also be easily transferred to the respective further differential stage planetary gear and vice versa.

The differential stage planetary gear and the second differential planetary gear are arranged on different axes. This means in particular that the first planetary axis of rotation and the second planetary axis of rotation run parallel to one another and are spaced apart from one another, in particular in the radial direction of the planetary gear set and/or in the circumferential direction of the planetary gear set running around the axial direction of the planetary gear set.

In order to be able to achieve a particularly compact, space-saving and particularly lightweight design and a particularly high torque density of the gear device, the invention provides that a first ratio between the first pitch circle diameter and the second pitch circle diameter and a second ratio between the third pitch circle diameter and the fourth pitch circle diameter are equal. For example, the first ratio is a first quotient which has the first pitch circle diameter in its first numerator and the second pitch circle diameter in its first denominator. It is very preferably provided that the second ratio is a second quotient which has the third pitch circle diameter in its second numerator and the fourth pitch circle diameter in its second denominator. The invention therefore provides that the quotients are equal. The previous and following statements on the pitch circle diameters can also be transferred to the pitch circle diameters and vice versa.

When the sun gears are mentioned above and below, this means the first sun gear and the second sun gear, unless otherwise stated. The first sun gear and the second sun gear are collectively referred to as outputs or output sun gears, with the first sun gear being a first of the output sun gears and the second sun gear being a second of the output sun gears.

The invention makes it possible to divide the aforementioned drive torque equally, i.e. half, between the output sun gears and thus to transmit it, thus realizing a so-called 50:50 torque distribution. For this purpose, the output sun gears are designed to be slightly different in terms of their pitch circle diameters, i.e. different sizes. However, this can avoid unfavorable, extreme profile shifts and the resulting adverse effects on the load-bearing behavior of the gear teeth of the spur gear differential. As a result, the transmission device can be designed to be particularly weight- and space-efficient, and a high torque density can be achieved.

In order to be able to realize a particularly compact design, one embodiment of the invention provides that the first differential planetary gear has a first toothing with a first number of teeth and a first toothing module, wherein the first toothing engages in the first sun gear. The first toothing has first teeth with a respective first tooth height, wherein the first tooth heights are preferably the same. The coupling planetary gear has a second toothing with a second number of teeth and a second toothing module, wherein the second toothing engages in the second differential planetary gear. The second toothing has second teeth with a respective second tooth height, wherein the second tooth heights are preferably the same.

Preferably, it is provided that the first differential planetary gear engages with the first sun gear, but preferably the first differential planetary gear does not engage with the coupling planetary gear, the second sun gear, or the second differential planetary gear. Furthermore, it is preferably provided that the coupling planetary gear engages with the second differential planetary gear, but preferably the coupling planetary gear does not engage with the first differential planetary gear or the first sun gear, and preferably the coupling planetary gear does not engage with the second sun gear. Furthermore, it is preferably provided that the second differential planetary gear engages with the second sun gear and the coupling planetary gear, wherein preferably the second differential planetary gear does not engage with the first sun gear or the first differential planetary gear.

A further embodiment of the invention is characterized in that the first number of teeth and the second number of teeth are the same, the first tooth module and the second tooth module differ from one another, and the respective first tooth height and the respective second tooth height differ from one another. This allows the installation space requirement to be kept particularly low.

In order to be able to realize a particularly compact design, it is provided in a further embodiment of the invention that the first toothing and the second toothing are oriented rotationally to one another, in particular when viewed around the first planetary axis of rotation, such that a respective gap, also referred to as a tooth gap, of the first toothing is aligned with a respective gap, also referred to as a tooth gap, of the second toothing of the coupling planet. In other words, it is preferably provided that the or all tooth gaps of the first toothing are aligned with the or all tooth gaps of the second toothing, in particular in the axial direction of the differential stage planetary gear and thus viewed along the first planetary axis of rotation.

In a further, particularly advantageous embodiment of the invention, it is provided that the first stepped planet and the second stepped planet are designed as one piece with one another, and are therefore made from a single piece. In other words, it is preferably provided that the first stepped planet and the second stepped planet are not designed as separate and interconnected components, but rather the first stepped planet and the second stepped planet are preferably designed as one piece with one another, so that the first stepped planet and the second stepped planet are designed as a monoblock or are formed by a monoblock. In other words, it is preferably provided that the first stepped planet and the second stepped planet are formed by a one-piece and thus integrally manufactured body, which is made from a single piece. This allows the installation space requirement, the weight and the costs to be kept to a particularly low level.

A further embodiment of the invention is characterized in that, viewed in the axial direction of the first stepped planet and the second stepped planet and thus along the first planetary axis of rotation, between the first stepped planet, which has a A transition region is provided, formed or arranged between the first stepped planet and the second stepped planet, which has a second width running in the axial direction of the second stepped planet and thus along the first planetary axis of rotation, also referred to as the coupling width, a transition region is provided, formed or arranged, the transition region having a third width, also referred to as the transition width. In principle, it is conceivable that the first width and the second width are the same. Furthermore, it is conceivable that the first width and the second width differ from one another. Furthermore, the first width and the third width can be the same, or the third width and the first width can differ from one another. Furthermore, it is conceivable that the second width and the third width are the same, or the third width and the second width differ from one another. In particular, it is conceivable that the transition region is free of teeth, or teeth, also referred to as transition teeth, are provided in the transition region, which can, for example, be formed integrally with the first teeth and/or integrally with the second teeth.

For example, in the transition region there is a tool outlet of a gear cutting tool for producing the first toothing of the first differential planetary gear and/or for producing the second toothing of the coupling planetary gear. Furthermore, it is preferably provided that a radial outer contour of the differential stage planetary gear, in particular a radial outer contour and thus an outer contour of the differential stage planetary gear pointing outwards in the radial direction of the differential stage planetary gear, does not fall below a first tip circle diameter of the second toothing of the coupling planetary gear in the transition region, but increases or grows from the first tip circle diameter of the second toothing of the coupling planetary gear, in particular continuously, to a second tip circle diameter of the first toothing of the first differential planetary gear. Thus, for example, the second tip circle diameter is larger than the first tip circle diameter. The respective previously mentioned width runs in the axial direction of the first stepped planet and the second stepped planet, thus in the axial direction of the differential stage planetary gear and thus along the first planetary axis of rotation. This ensures a particularly compact design, particularly in the axial direction of the differential stage planetary gear and thus of the transmission device as a whole.

In order to be able to realize a particularly compact design, particularly in the axial direction of the transmission device, it is provided in a further embodiment of the invention that the third width of the transition region is, in particular significantly, smaller than the first width of the first stepped planet, in particular of the first toothing, and, in particular significantly, smaller than the second width of the second stepped planet, in particular of the second toothing. Preferably, the first width is a first toothing width of the first toothing, and preferably the second width is a second toothing width of the second toothing. The feature that the third width is significantly smaller than the first width and significantly smaller than the second width is to be understood in particular that, for example, the third width is at most 90 percent, in particular at most 80 percent, most particularly at most 70 percent and most particularly at most 60 percent, of the first width and the second width if the first width and second width are the same, and that the third width is, for example, at most 90 percent, in particular at most 80 percent, most particularly at most 70 percent and most particularly at most 60 percent, of the smaller of the first width and the second width if the first width and the second width are different. In particular, for example, the third width is less than 50 percent, in particular less than 40 percent, most particularly less than 30 percent, of the first width and the second width or the smaller of the first width and the second width.

A further embodiment of the invention is characterized in that the first differential planetary gear and the coupling planetary gear are designed separately from one another and are connected to one another, in particular in a rotationally fixed manner, wherein the one of the first and second stepped planets whose pitch circle diameter or pitch circle diameter is smaller than the pitch circle diameter or pitch circle diameter of the other of the first and second stepped planets has a projection, for example designed as a pin, also referred to as an extension, on which the other of the first and second stepped planets is arranged and fastened. In other words, if the third pitch circle diameter is larger than the fourth pitch circle diameter, the first stepped planet is a large planet and the second stepped planet is a small planet. If the third pitch circle diameter is smaller than the fourth pitch circle diameter, the first stepped planet is a small planet and the second stepped planet is a large planet. It is provided that the small planet has the projection, for example designed as a pin, also referred to as an extension, on which the large planet is arranged and fastened. For example, the large planet has a hub in which, for example, at least a length region of the projection of the small planet is arranged, so that the The large planet is arranged via its hub on the length of the projection of the small planet. In particular, the large planet is attached to the projection via the hub in a rotationally fixed manner and is therefore connected to the small planet in a rotationally fixed manner. This allows a particularly space-saving and cost-effective design to be achieved.

In order to be able to keep the installation space requirement of the transmission device particularly low, in particular in the axial direction of the transmission device, it is provided in a further embodiment of the invention that the first stepped planet and the second stepped planet are immediately or directly adjacent to one another in the axial direction of the first stepped planet and the second stepped planet and thus viewed along the first planetary axis of rotation.

In a further embodiment of the invention, the first sun gear has a third toothing with a third number of teeth and a third toothing module, the third toothing engaging in the first differential planet gear, in particular in its first toothing. The third toothing has third teeth with a respective third tooth height, it is preferably provided that the third tooth heights are the same. The second sun gear has a fourth toothing with a fourth number of teeth and a fourth toothing module, the fourth toothing engaging in the second differential planet gear, in particular in its fifth toothing. The fourth toothing has fourth teeth with a respective fourth tooth height, the fourth tooth heights preferably being the same. In order to achieve a design that is particularly space- and weight-efficient, it has proven to be advantageous if the third number of teeth and the fourth number of teeth differ from one another, if the third toothing module and the fourth toothing module are the same, and if the respective third tooth height and the respective fourth tooth height are the same.

In the context of the present disclosure, ordinal numerals such as "first", "first", "second", "secondary" etc. are not necessarily used to indicate or imply a number or set of elements to which the ordinal numerals refer, but rather to be able to unambiguously refer to elements or concepts to which the ordinal numerals are assigned or to which the ordinal numerals refer.

In order to be able to keep the installation space requirement, costs and weight particularly low, it is provided in a further embodiment of the invention that all gears of the spur gear differential are straight-toothed, and are therefore designed or constructed with straight teeth.

In order to be able to achieve a particularly high torque density in a particularly space-saving manner, a further embodiment of the invention provides that the transmission device has a planetary gear, which is provided in particular in addition to the spur gear differential, which has at least one stepped planetary gear provided in addition to the differential step planetary gear and in particular also in addition to the second differential planetary gear and preferably also in addition to the sun gears and is held on the planet carrier so as to be rotatable, in particular about the second planetary axis of rotation relative to the planet carrier, which has a first planetary gear and a second planetary gear. The second planetary gear is also referred to as the third step planet, and the second planetary gear is also referred to as the fourth step planet. The third step planet and the fourth step planet are preferably spur gears. The third step planet and the fourth step planet are connected to one another in a rotationally fixed manner. It is conceivable that the third step planet and the fourth step planet are formed integrally with one another, thus made from a single piece, or the third step planet and the fourth step planet are formed separately from one another and connected to one another in a rotationally fixed manner.

The planetary gear also has a third sun gear, which is provided in addition to the first sun gear and in addition to the second sun gear and preferably also in addition to the differential stage planet gear and in addition to the second differential planet gear and also preferably in addition to the stepped planet gear, and which is a drive sun gear or is also referred to as a drive sun gear. The third sun gear is preferably a spur gear. One of the planet gears of the stepped planet gear of the planetary gear is in engagement, and therefore meshes with the drive sun gear. It is preferably provided that the first planet gear and the second planet gear, and therefore the third stepped planet and the fourth stepped planet, are of different sizes, in particular have different pitch circle diameters and/or different pitch circle diameters from one another, so that, for example, the first planet gear has a fifth pitch circle diameter and/or a fifth pitch circle diameter, and so that, for example, the second planet gear has a sixth pitch circle diameter and/or a sixth pitch circle diameter. It is conceivable that the fifth pitch circle diameter and the sixth pitch circle diameter differ from each other. In particular, it is conceivable that the fifth pitch circle diameter and the sixth pitch circle diameter circle diameters differ from one another. Thus, for example, the fifth pitch circle diameter or the fifth pitch circle diameter is larger than the sixth pitch circle diameter or the sixth pitch circle diameter. For example, one planetary gear has the fifth pitch circle diameter or the fifth pitch circle diameter, so that, for example, the other planetary gear of the stepped planetary gear of the planetary gear has the sixth pitch circle diameter or sixth pitch circle diameter. Thus, preferably one planetary gear is larger than the other planetary gear. In other words, preferably one planetary gear is the larger of the planetary gears, so that the other planetary gear is the smaller of the planetary gears. Most preferably, the first planetary gear is one planetary gear, most preferably the other planetary gear is the second planetary gear. Thus, it is preferably provided that the larger planetary gear of the stepped planetary gear of the planetary gear is in engagement with the drive sun gear.

The planetary gear also has a ring gear which is or can be connected to the aforementioned housing in a rotationally fixed manner. In particular, the ring gear can be permanently connected to the housing in a rotationally fixed manner. In particular, the ring gear is arranged at least partially in the housing. The other planet gear, in particular the smaller planet gear, is in engagement with the ring gear, thus engaging with the ring gear or meshing with the ring gear. In particular, it is conceivable that the stepped planet gear of the planetary gear is, in particular permanently, connected to the second differential planet gear in a rotationally fixed manner, or that the stepped planet gear of the planetary gear, in particular the second planetary axis of rotation, is rotatable relative to the second differential planet gear. In particular, the stepped planet gear of the planetary gear is arranged coaxially to the second differential planet gear. Preferably, the stepped planet gear is thus held on the planet carrier so as to be rotatable about the second planetary axis of rotation relative to the planet carrier.

In order to achieve a particularly compact and lightweight design, it has proven to be particularly advantageous if the second differential planetary gear is connected to the ring gear, to one planetary gear and to the other planetary gear of the planetary gear that engages the ring gear in a direction that runs in the axial direction of the second differential planetary gear and thus runs parallel to the second planetary axis of rotation or coincides with the second planetary axis of rotation, with the ring gear and the other planetary gear of the planetary gear connecting in the same direction to the one planetary gear of the planetary gear that engages the drive sun gear, whereby the ring gear and the other planetary gear of the planetary gear are arranged in the axial direction of the second differential planetary gear and thus viewed along the second planetary axis of rotation, between the second differential planetary gear of the spur gear differential and the one planetary gear of the planetary gear that engages the drive sun gear. This makes it possible to achieve a particularly compact design, particularly in the axial direction of the transmission device.

A further embodiment of the invention is characterized in that the first pitch circle diameter of the first sun gear is larger than the second pitch circle diameter of the second sun gear, which adjoins the first sun gear in an arrangement direction running in the axial direction of the sun gears, wherein the first sun gear adjoins the third sun gear in the same arrangement direction. As a result, the first sun gear is arranged between the second sun gear and the third sun gear in the axial direction of the sun gears and thus along the respective sun gear rotation axis, whereby the transmission device can have a particularly compact design, particularly in the axial direction.

In order to be able to keep the installation space requirement particularly low, it is provided in a further embodiment of the invention that planet carrier walls of the planet carrier, to whose planet carrier walls bolts are fastened, in particular in a rotationally fixed manner, on which the differential stage planetary gear of the spur gear differential, the second differential planetary gear of the spur gear differential and preferably the stepped planetary gear of the planetary gear are rotatably held, are located exclusively on the outside in the axial direction of the planetary gear and the spur gear differential and thus viewed along the respective sun gear rotation axis, thus adjoining on both sides the ring gear, the second differential planetary gear of the spur gear differential, the differential stage planetary gear of the spur gear differential and the sun gears of the spur gear differential and preferably the stepped planet gear of the planetary gear, so that the planet carrier walls, which are opposite one another in particular in the axial direction of the planet carrier, are arranged outside the planetary gear and outside the spur gear differential in the axial direction of the transmission device and thus viewed along the respective sun gear rotation axis.

It has also proven to be particularly advantageous if the first differential planetary gear is arranged in phase with the stepped planetary gear.

In order to be able to keep the axial installation space requirement particularly low, it is provided in a further embodiment of the invention that, viewed in the axial direction of the second differential planetary gear and thus along the second planetary axis of rotation, the smaller planetary gear of the planetary gear is arranged between the larger planetary gear of the planetary gear and the second differential planetary gear of the spur gear differential, or preferably, viewed in the axial direction of the second differential planetary gear of the spur gear differential and thus along the second planetary axis of rotation, the larger planetary gear of the planetary gear is arranged between the smaller planetary gear of the planetary gear and the second differential planetary gear of the spur gear differential.

A second aspect of the invention relates to a motor vehicle, also referred to simply as a vehicle, which is preferably designed as a motor vehicle, in particular as a passenger car. The motor vehicle according to the second aspect of the invention has a transmission device according to the first aspect of the invention. Advantages and advantageous embodiments of the first aspect of the invention are to be regarded as advantages and advantageous embodiments of the second aspect of the invention and vice versa.

Further advantages, features and details of the invention emerge from the following description of preferred embodiments and from the drawing. The features and combinations of features mentioned above in the description as well as the features and combinations of features mentioned below in the description of the figures and/or shown alone in the figures can be used not only in the combination specified in each case, but also in other combinations or on their own, without departing from the scope of the invention.

• 1 eine schematische Vorderansicht einer ersten Ausführungsform einer Getriebevorrichtung für ein Kraftfahrzeug;
• 2 eine schematische Seitenansicht der ersten Ausführungsform der Getriebevorrichtung;
• 3 eine schematische Seitenansicht einer zweiten Ausführungsform der Getriebevorrichtung;
• 4 eine schematische Vorderansicht einer ersten Ausführungsform eines Differentialstufenplanetenrads eines Stirnradifferentials der Getriebevorrichtung;
• 5 eine zweite Ausführungsform des Differentialstufenplanetenrads;
• 6 eine schematische Vorderansicht einer dritten Ausführungsform der Getriebevorrichtung;
• 7 eine schematische Seitenansicht der dritten Ausführungsform der Getriebevorrichtung;
• 8 eine schematische Vorderansicht einer vierten Ausführungsform der Getriebevorrichtung;
• 9 eine schematische Seitenansicht der vierten Ausführungsform der Getriebevorrichtung;
• 10 ausschnittsweise eine schematische Längsschnittansicht einer dritten Ausführungsform des Differentialstufenplanetenrads;
• 11 ausschnittsweise eine schematische Längsschnittansicht einer vierten Ausführungsform des Differentialstufenplanetenrads; und
• 12 ausschnittsweise eine schematische Längsschnittansicht einer fünften Ausführungsform des Differentialstufenplanetenrads.

The drawing shows in:

• 1 a schematic front view of a first embodiment of a transmission device for a motor vehicle;
• 2 a schematic side view of the first embodiment of the transmission device;
• 3 a schematic side view of a second embodiment of the transmission device;
• 4 a schematic front view of a first embodiment of a differential stage planetary gear of a spur gear differential of the transmission device;
• 5 a second embodiment of the differential stage planetary gear;
• 6 a schematic front view of a third embodiment of the transmission device;
• 7 a schematic side view of the third embodiment of the transmission device;
• 8th a schematic front view of a fourth embodiment of the transmission device;
• 9 a schematic side view of the fourth embodiment of the transmission device;
• 10 a partial schematic longitudinal sectional view of a third embodiment of the differential stage planetary gear;
• 11 a partial schematic longitudinal sectional view of a fourth embodiment of the differential stage planetary gear; and
• 12 a schematic longitudinal sectional view of a fifth embodiment of the differential stage planetary gear.

In the figures, identical or functionally identical elements are provided with identical reference symbols.

1 and 2 show in a schematic front view or in a schematic and sectional side view a first embodiment of a transmission device 10 for a motor vehicle preferably designed as a motor vehicle, in particular as a passenger car, and also simply referred to as a vehicle. In its fully manufactured state, the motor vehicle has, for example, at least or exactly two vehicle axles arranged one behind the other in the longitudinal direction of the vehicle, also simply referred to as axles. The respective vehicle axle has at least or exactly two vehicle wheels, which are also simply referred to as wheels. The respective vehicle wheels of the respective vehicle axle are arranged on opposite sides in the transverse direction of the motor vehicle. The vehicle wheels are ground contact elements by means of which the motor vehicle can be or is supported downwards on a ground in the vertical direction of the motor vehicle. For example, the motor vehicle has at least one drive motor by means of which the vehicle wheels of at least or exactly one of the vehicle axles can be driven via the transmission device 10, whereby the motor vehicle as a whole can be driven. In particular, the drive motor can be an internal combustion engine or an electric machine, so that the motor vehicle is designed, for example, as a hybrid vehicle or as an electric vehicle, in particular as a battery-electric vehicle (BEV). The vehicle wheels that can be driven by the transmission device 10 are also referred to as drive wheels. When reference is made below to the wheels or the vehicle wheels, this refers to the drive wheels of the motor vehicle, unless otherwise stated.

The transmission device 10 has a spur differential 12, which is also referred to as a spur differential gear. The spur differential 12 is a differential gear, also simply referred to as a differential, which is designed as a spur differential gear. In particular, the spur differential 12 is designed as a planetary differential. The spur differential 12 has a first sun gear 14, which is also referred to as a first sun. The first sun gear 14 is designed as a first output of the spur differential 12. In addition, the first sun gear 14 is designed as a first spur gear. In other words, the sun gear 14 is a first gear which is designed as a spur gear. The first sun gear 14 has a first pitch circle diameter. The spur differential 12 also has a second sun gear 16, which is designed as a second output of the spur differential 12. The second sun gear 16 is designed as a second spur gear. In other words, the second sun gear 16 is a second gear which is designed as a spur gear. Particularly well 1 and 2 It can be seen that the sun gears 14 and 16 are arranged coaxially to each other. The gear device 10 has a 1 particularly schematically illustrated housing 18, wherein the spur gear differential 12 is at least partially arranged in the housing 18. The sun gears 14 and 16 are rotatable relative to the housing 18 about a sun gear axis of rotation common to the sun gears 14 and 16. The sun gear axis of rotation 20 is also simply referred to as the axis of rotation, wherein the axis of rotation runs in the axial direction of the transmission device 10 and thus of the spur gear differential 12, in particular coincides with the axial direction of the transmission device 10 and thus of the spur gear differential 12. In particular, the axial direction of the transmission device 10 coincides with the axial direction of the spur gear differential 12, the radial direction of which coincides with the radial direction of the transmission device 10. The second sun gear 16 is designed as a second output of the spur gear differential 12. The spur gear differential 12 can provide output torques via its outputs, i.e. via the sun gears 4 and 16, by means of which the drive wheels can be driven. In particular, the respective output torque provided or available by the respective sun gear 14, 16 results from a drive torque that can be introduced or is introduced into the spur gear differential 12. For example, the drive torque can be provided by the drive motor or the drive torque results from another torque that can be provided by the drive motor. In particular, the drive torque can be divided and distributed between the vehicle wheels, in particular in half, by means of the spur gear differential 12. From 2 it can be seen that a first shaft designed as a first side shaft 22 can be driven by the first sun gear 14 and a second shaft designed as a second side shaft 24 can be driven by the sun gear 16, with a first of the drive wheels being driven by the side shaft 22 and a second of the drive wheels being driven by the side shaft 24. In particular, it is provided here that the first sun gear 14 is provided, in particular permanently, in a rotationally fixed manner with the first side shaft 22, and alternatively or additionally the second sun gear 16 is connected, in particular permanently, in a rotationally fixed manner with the second side shaft 24. The second sun gear 16 has a second pitch circle diameter that is different from the first pitch circle diameter, with the second pitch circle diameter being smaller than the first pitch circle diameter in this case. The second sun gear 16 is also referred to as the second sun, small sun or smaller sun, with the sun gear 14 also being referred to as the first sun, larger sun or large sun.

The spur gear differential 12 further comprises a planetary gear set 26, by means of which the sun gears 14 and 16 are coupled to one another in such a way that the sun gears 14 and 26 can rotate in opposite directions, in particular about the axis of rotation relative to the housing 18. The planetary gear set 26 comprises a planet carrier 28, which is also referred to as a web and is arranged coaxially to the sun gears 14 and 16 in the present case. The planet carrier 28 can be rotated about the axis of rotation (sun gear axis of rotation 20) relative to the housing 18. The planetary gear set 26 further comprises a first differential planet gear 30. In particular, the planetary gear set 26 comprises at least one further or several further first differential planet gears, wherein the following and previous statements on the first differential planet gear 30 can also be readily applied to the respective further first differential planet gear and vice versa. The first differential planetary gear 30 engages the first sun gear 14, thus meshing with the first sun gear 14 or engaging with the first sun gear 14. In addition, the first differential planetary gear 30 is held on the planetary carrier 28 so as to be rotatable about a first planetary rotation axis 32 relative to the planet carrier 28. In addition, the first differential planetary gear 30 has a third pitch circle diameter. In the first embodiment, the first differential planetary gear 30 is assigned a first bolt 34, which is also referred to as the first planet bolt. In particular, the first differential planetary gear 30 is rotated about the first planetary axis of rotation 32 is arranged, in particular mounted, on the bolt 34 so as to be rotatable relative to the bolt 34 and relative to the planet carrier 28, wherein, for example, the bolt 34 is in turn fastened, in particular in a rotationally fixed manner, to the planet carrier 28.

The planetary gear set 26 also has at least one second differential planet gear 36. In particular, it is conceivable that the planetary gear set 26 has at least one further or several further second differential planet gears, wherein the previous and following statements on the second differential planet gear 36 can also be easily transferred to the further second differential planet gear and vice versa. The second differential planet gear 36 engages in the second sun gear 16, which in 2 is shown by a dashed arrow 38. In other words, the second differential planetary gear 36 meshes with the sun gear 16 or the second differential planetary gear 36 is in engagement with the second sun gear 16. Thus, the dashed arrow 38 means "meshes with". The second differential planetary gear 36 is held on the planetary carrier 28 so as to be rotatable about a second planetary axis of rotation 40 relative to the planetary carrier 28. From 2 it can be seen that the second planetary axis of rotation 40 runs parallel to the first planetary axis of rotation 32 and is spaced from the planetary axis of rotation 32. In addition, the planetary axes of rotation 32 and 40 run parallel to the axis of rotation (sun gear axis of rotation 20), and the planetary axes of rotation 32 and 40 are each spaced from the axis of rotation. In the first embodiment, the second differential planetary gear 36 is assigned a second bolt 42, which is also referred to as a second planetary bolt. The second differential planetary gear 36 is arranged, in particular mounted, on the second bolt 42 so as to be rotatable about the second planetary axis of rotation 40 relative to the bolt 42 and relative to the planet carrier 28, wherein, for example, the second bolt 42 is in turn fastened, in particular in a rotationally fixed manner, to the planet carrier 28.

The planetary gear set 26 also has at least one coupling planetary gear 44. In particular, the planetary gear set 26, in particular for each first differential planetary gear, has a respective coupling planetary gear such as the coupling planetary gear 44. The first differential planetary gear 30, the second differential planetary gear 36 and the coupling planetary gear 44 are designed as spur gears, thus as gears which are designed as spur gears. The coupling planetary gear 44 is arranged coaxially to the first differential planetary gear 30 and is, in particular permanently, connected in a rotationally fixed manner to the first differential planetary gear 30. The coupling planetary gear 44 engages in the second differential planetary gear 36, whereby the differential planetary gears 30 and 36 are coupled to one another via the coupling planetary gear 44, in particular in a torque-transmitting manner. The coupling planetary gear 44 has a fourth pitch circle diameter that is different from the third pitch circle diameter of the first differential planetary gear 30. Furthermore, the first differential planetary gear 30 and the coupling planetary gear 44 assigned to it form a differential stage planetary gear 46, which is also referred to as a differential stage planet. The planetary gear set 26 thus has the differential stage planetary gear 46. In particular, for example, the planetary gear set 26 has at least one further or several further differential stage planetary gears, wherein the previous and following statements regarding the differential stage planetary gear 46 can also be easily transferred to the respective further differential stage planetary gear and vice versa. The differential stage planetary gear 46 is held on the planet carrier 28 so as to be rotatable about the first planetary axis of rotation 32 relative to the planet carrier 28. In the present case, this is achieved in that the differential stage planetary gear 46 is arranged, in particular mounted, on the bolt 34 so as to be rotatable about the first planetary axis of rotation 32 relative to the bolt 34 and relative to the planet carrier 28, so that the coupling planetary gear 44 is also arranged, in particular mounted, on the bolt 34 so as to be rotatable about the first planetary axis of rotation 32 relative to the bolt 34 and relative to the planet carrier 28. The first differential planetary gear 30 is a first stage planet of the differential stage planetary gear 46 or is also referred to as the first stage planet of the differential stage planetary gear 46. Accordingly, the coupling planetary gear 44 is a second stage planet of the differential stage planetary gear 46, or the coupling planetary gear 44 is also referred to as the second stage planet of the differential stage planetary gear 46. In the first embodiment, the fourth pitch circle diameter of the coupling planetary gear 44 is smaller than the third pitch circle diameter of the first differential stage planetary gear 46, so that the coupling planetary gear 44 is also referred to as a small stage planet or smaller stage planet or small planet, and so that the first differential planetary gear 30 is also referred to as a large stage planet or larger stage planet or large planet.

In order to be able to realize a particularly compact and lightweight design of the transmission device 10 as well as a particularly high torque density, it is provided that a first ratio between the first pitch circle diameter and the second pitch circle diameter and a second ratio between the third pitch circle diameter and the fourth pitch circle diameter are equal. For example, the first differential planetary gear 30 has a first number of teeth and a first toothing module. transmitting, first toothing, which engages in the first sun gear 14 and has first teeth with a respective first tooth height. The coupling planetary gear 44 has, for example, a second number of teeth and a second toothing module, second toothing, which engages in the second differential planetary gear 36 and has second teeth with a respective second tooth height. It is further preferably provided that the first number of teeth and the second number of teeth are the same, and that the first toothing module and the second toothing module differ from one another, so that the respective first relationship and the respective second relationship differ from one another.

4 shows a schematic front view of a first embodiment of the differential stage planetary gear 46. In 4 the first toothing of the first differential planetary gear 30 is designated 48, the first teeth of which are designated 50. The second toothing of the coupling planetary gear 44 is in 4 designated with 52, the second teeth of which are designated with 54. It can be seen that the first toothing 48 also has first gaps 56, which are also referred to as first tooth gaps. In the circumferential direction of the toothing 48 and thus of the differential planet gear 30, which runs around the planetary axis of rotation 32, a respective one of the gaps 56 is arranged between two directly adjacent teeth 50. The toothing 52 has second gaps 58, which are also referred to as second tooth gaps. In the circumferential direction of the coupling planet gear 44 and the toothing 52, which runs around the planetary axis of rotation 32, between two directly adjacent teeth 54, one of the second gaps 58 is arranged. The respective gap 56 is also referred to as the first tooth gap, and the respective gap 58 is also referred to as the second tooth gap. In the 4 In the first embodiment of the differential stage planetary gear 46 shown, the toothings 48 and 52 are rotationally oriented relative to one another when viewed around the planetary axis of rotation 32 in such a way that the respective first gaps 56 are aligned with the respective second gaps 58 in the axial direction of the differential stage planetary gear 46 and thus when viewed along the first planetary axis of rotation 32.

At the 1 and 2 In the first embodiment of the transmission device 10 shown, the first differential planetary gear 30 and the coupling planetary gear 44 are formed separately from one another and connected to one another. In this case, the first differential planetary gear 30 and the coupling planetary gear 44 directly adjoin, in particular abut, one another in the axial direction of the differential stage planetary gear 46 and thus viewed along the first planetary axis of rotation 32, i.e. immediately adjacent to one another, so that, for example, the first differential planetary gear 30 and the coupling planetary gear 44 directly touch one another in the axial direction of the differential stage planetary gear 46. 3 shows a second embodiment of the transmission device 10 in a schematic and sectional side view. In the second embodiment, for example, the first differential planetary gear 30 and the associated coupling planetary gear 44 are also formed separately from one another and, in particular permanently, connected to one another in a rotationally fixed manner.

In contrast to the first embodiment, however, in the axial direction of the differential stage planetary gear 46 and thus viewed along the first planetary axis of rotation 32, an intermediate region 60 is arranged between the first differential planetary gear 30 and the associated coupling planetary gear 44, which intermediate region 60 can also be referred to as a transition region or can be designed as a transition region. For example, the first differential planetary gear 30, in particular its toothing 48, has a first width running in the axial direction of the differential stage planetary gear 46, over which, for example, the toothing 48 engages in the sun gear 14. For example, the coupling planetary gear 44, in particular its toothing 52, has a second width running in the axial direction of the differential stage planetary gear 46, in particular a second toothing width, over which, for example, the toothing 52 engages in the differential planetary gear 36. The first width is also referred to, for example, as b1, and the second width is also referred to, for example, as b2. Furthermore, it is conceivable that the intermediate region 60 has a third width running in the axial direction of the differential stage planetary gear 46, which is also designated b3.

5 shows a schematic front view of a second embodiment of the differential stage planetary gear 46. In the second embodiment, the toothings 48 and 52 are oriented rotationally relative to one another in the circumferential direction of the differential stage planetary gear 46 running around the first planetary axis of rotation 32 in such a way that the first gaps 56 of the first toothing 48 of the first differential planetary gear 30, viewed in the axial direction of the differential stage planetary gear 46, are aligned with the second teeth 54 of the second toothing 52 of the coupling planetary gear 44, and that the first teeth 50 of the first toothing 48 of the first differential planetary gear 30, viewed in the axial direction of the differential stage planetary gear 46, are aligned with the second gaps 58 of the second toothing 52 of the coupling planetary gear 44. Alternatively, it is conceivable that, while in the 4 shown, first embodiment of the differential planetary gear 46, the teeth 48 and 52 are exactly aligned in the axial direction of the differential planetary gear 46, thus the teeth 50 with the teeth 54 and the gaps 56 with the gaps 58 in the axial direction of the differential stage planetary gear 46 are exactly aligned, in the 5 In the second embodiment of the differential stage planetary gear 46 shown, the toothings 48 and 52 are not aligned, but are offset or rotated relative to one another by an offset angle V in the circumferential direction of the differential stage planetary gear 46 running around the first planetary axis of rotation 32, so that, for example, at least respective partial areas of the teeth 50 and the gaps 58 and at least respective partial areas of the gaps 56 and the teeth 54 are arranged at the same height or in the same rotational position when viewed around the circumferential direction of the differential stage planetary gear 46.

Preferably, it is in 3 In the second embodiment of the transmission device 10 shown, it is provided that the third width b3 of the intermediate region 60 is smaller than the first width b1 of the first stepped planet and smaller than the second width b2 of the second stepped planet. It is conceivable that the first width and the second width are the same or the first width and the second width can differ from one another.

It is preferably provided that the first sun gear 14 has a third number of teeth and a third toothing module, has third teeth which engage in the first differential planet gear 30, in particular in its first toothing 48, and has third teeth with a respective third tooth height. The second sun gear 16 has, for example, a fourth toothing having a fourth number of teeth and a fourth toothing module, which engages in the second differential planet gear 36, in particular in its fifth toothing, and has fourth teeth with a respective fourth tooth height. It is preferably provided that the third number of teeth and the fourth number of teeth differ from one another, wherein preferably the third toothing module and the fourth toothing module are the same, so that preferably the respective third tooth height and the respective fourth tooth height are the same. It is therefore preferably provided that all the teeth of the spur gear differential 12 have straight teeth.

6 and 7 show a third embodiment of the transmission device 10 in a schematic front view and in a schematic and sectional side view. In the third embodiment, the transmission device 10 has a planetary gear 62 provided in addition to the spur gear differential 12, which is explained in more detail below. The planetary gear 62 has at least one stepped planetary gear 64 provided in addition to the differential stage planetary gear 46 or in addition to the differential stage planetary gears 46, which is held on the planet carrier 28 so as to be rotatable about the second planetary axis of rotation 40 relative to the planetary carrier 28. In the third embodiment, the stepped planetary gear 64 is arranged, in particular mounted, on the second bolt 42 so as to be rotatable about the planetary axis of rotation 40 relative to the bolt 42 and relative to the planetary carrier 28. In the third embodiment, the stepped planetary gear 64 is thus arranged coaxially to the second differential planetary gear 36. In particular, the second differential planetary gear 36 and the stepped planetary gear 64 are rotatable relative to one another about the second planetary axis of rotation 40. For example, the planetary gear 62 can have at least one further or several further stepped planetary gears, wherein the previous and following statements regarding the stepped planetary gear 64 can be easily transferred to the respective further stepped planetary gear and vice versa. In particular, a respective stepped planetary gear 64 is provided for each second differential planetary gear 36.

The stepped planetary gear 64 has a first planetary gear 66 and a second planetary gear 68, wherein the planetary gears 66 and 68 are connected to one another in a rotationally fixed manner, in particular permanently. The planetary gears 66 and 68 are spur gears. Thus, the planetary gears 66 and 68 are gears which are designed as spur gears. Preferably, the planetary gears 66 and 68 are also straight-toothed. The planetary gear 66 is also referred to as the third stepped planet, and the planetary gear 68 is also referred to as the fourth stepped planet. It can be seen that the planetary gears 66 and 68 are different sizes, thus have different pitch circle diameters and/or different pitch circle diameters, in this case such that the planetary gear 66 has a fifth pitch circle diameter and the planetary gear 68 has a sixth pitch circle diameter which is smaller than the fifth pitch circle diameter. Therefore, the planetary gear 66 is also called the large planetary gear or larger planetary gear, and the planetary gear 68 is also called the small planetary gear or smaller planetary gear.

The planetary gear 62 also has a third sun gear 70, which is also referred to as a drive sun gear or drive sun, in addition to the first sun gear 14 and in addition to the second sun gear 16. The third sun gear 70 is preferably also a spur gear and preferably has straight teeth. It can be seen that the large planet gear, in this case the planet gear 66, engages with the third sun gear 70. In other words, the large planet gear is in engagement with the third sun gear 70. The planetary gear 62 also has a ring gear 72, which in the third embodiment form, in particular permanently, is connected to the housing 18 in a rotationally fixed manner. In an alternative embodiment, it would be conceivable for a switching element to be provided which can be switched between a coupled state and an uncoupled state. In the coupled state, for example, the ring gear 72 is connected to the housing 18 in a rotationally fixed manner by means of the switching element. In the uncoupled state, for example, the switching element releases the ring gear 72 for rotations about the axis of rotation (sun gear rotation axis 20) relative to the housing 18, so that the ring gear 72 can rotate about the axis of rotation relative to the housing 18 in the uncoupled state. In the third embodiment, the planetary gear 62 is thus arranged coaxially to the spur gear differential 12. The sun gear 70 is arranged coaxially to the sun gears 14 and 16 and can therefore rotate about the sun gear rotation axis 20 relative to the housing 18. It can also be seen that the planet carrier 28 is a planet carrier common to the spur gear differential 12 and the planetary gear 62, on which the stepped planet gear 64 is also held so as to be rotatable about the second planetary axis of rotation 40. It can be seen that the small planet gear, in this case the planet gear 68, is in engagement with the ring gear 72.

For example, the sun gear 70 can be driven by the drive motor, so that the aforementioned drive torque can be provided, for example, via the planetary gear 62 and can be introduced into the spur gear differential 12 via the planetary gear 62 in order to thereby drive the planet carrier 28 and thus the spur gear differential 12. Thus, the planet carrier 28 is preferably designed as a drive of the spur gear differential 12, via whose drive the aforementioned drive torque of the spur gear differential 12 can be introduced.

In 3 a dashed arrow 74 means “meshes with”, so that the dashed arrow 74 illustrates that the sun gear 70 meshes with the large planet gear (planet gear 66), and is therefore in engagement with the large planet gear.

In order to be able to realize a particularly compact design, in particular in the axial direction of the transmission device 10 and thus viewed along the sun gear rotation axis 20, it is provided in the third embodiment that the second differential planetary gear 36 extends in a direction extending in the axial direction of the second differential planetary gear 36 and thus parallel to the second planetary rotation axis 40 or coinciding with the second planetary rotation axis 40, in 7 by an arrow 76, adjoins the ring gear 72 and the planetary gear 68 meshing with the ring gear 72, wherein the ring gear 72 and the planetary gear 68 meshing therewith adjoin the planetary gear 66 in the direction illustrated by the arrow 76, whereby the ring gear 72 and the planetary gear 68 are arranged between the second differential planetary gear 36 and the planetary gear 66 in the axial direction of the second differential planetary gear 36 and in this case also in the axial direction of the stepped planetary gear 64 and thus viewed along the second planetary axis of rotation 40.

As in the first embodiment and the second embodiment of the transmission device 10, in the third embodiment of the transmission device 10 the first pitch circle diameter of the first sun gear 14 is larger than the second pitch circle diameter of the second sun gear 16. In the second embodiment the second sun gear 16 closes in a direction in the axial direction of the sun gears 14 and 16 and thus parallel to the sun gear rotation axis 20 or coinciding with the sun gear rotation axis 20, in 3 by an arrow 78 illustrated arrangement direction to the sun gear 14, wherein in the present case the arrangement direction illustrated by the arrow 78 corresponds to the direction illustrated by the arrow 76. The first sun gear 14 adjoins the third sun gear 70 in the arrangement direction (arrow 78), whereby the first sun gear 14 is arranged in the axial direction of the sun gears 14, 16 and 70 and thus along the sun gear rotation axis 20 between the second sun gear 16 and the third sun gear 70.

Furthermore, it is provided that planet carrier walls 80 and 82 of the planet carrier 28, to whose planet carrier walls 80 and 82 the bolts 34 and 42 are fastened, in particular in a rotationally fixed manner, are located exclusively on the outside in the axial direction of the planetary gear 62 and the spur gear differential 12 and thus along the sun gear rotation axis 20, thus adjoining on both sides the ring gear 72, the stepped planet gear 64, the second differential planet gear 36, the differential stepped planet gear 46 and the sun gears 14, 16 and 70 and are thus arranged outside both the planetary gear 62 and the spur gear differential 12.

8th and 9 show a fourth embodiment of the transmission device 10 in a schematic front view and in a schematic and sectional side view, respectively. As in the third embodiment, the small planetary gear (planetary gear 68) engages in the ring gear 72, and the large planetary gear (planetary gear 66) engages in the third sun gear 70. In the fourth embodiment, however, it is provided that, viewed in the axial direction of the second differential planetary gear 36 and the stepped planetary gear 64, the large planetary gear tenrad (planetary gear 66) is arranged between the second differential planetary gear 36 and the small planetary gear (planetary gear 68), so that the planetary gear 66 is arranged between the second differential planetary gear 36 and the ring gear 72 when viewed in the axial direction of the stepped planetary gear 64 and the second differential planetary gear 36.

3 shows a third embodiment of the differential stage planetary gear 46. In the third embodiment, the differential planetary gear 30 and the associated coupling planetary gear 44 are formed separately from one another and are connected to one another in a rotationally fixed manner. The coupling planetary gear 44 has a projection 84, which in the present case is formed as a collar of the coupling planetary gear 44 or by a collar of the coupling planetary gear 44. The differential planetary gear 30 is arranged on the projection 84 and, in particular permanently, is connected to the projection 84 in a rotationally fixed manner, as a result of which the differential planetary gear 30 is, in particular permanently, connected to the coupling planetary gear 44 in a rotationally fixed manner. In the present case, the differential planetary gear 30 has a hub 36 in which the projection 84 is arranged. The differential planetary gear 30 is thus connected via its hub 86, in particular permanently, to the projection 84 and thus to the coupling planetary gear 44 in a rotationally fixed manner.

11 shows a fourth embodiment of the differential stage planetary gear 46. In the fourth embodiment of the differential stage planetary gear 46, the first differential planetary gear 30 and the associated coupling planetary gear 44 are formed integrally with one another and are thereby connected to one another in a rotationally fixed manner, in particular permanently. In 11 is an area labeled B. As can be seen from 11 As can be seen, a radial outer contour 88 of the differential stage planetary gear 46 in the transition region (intermediate region 60) does not fall below a first tip circle diameter k1 of the second toothing 52, but rather increases from the first tip circle diameter k1 to a second tip circle diameter k2 of the first toothing 48, in particular at least substantially continuously. In particular, for example, in the region B, machining, in particular production, of the toothing 52 and/or the toothing 48 takes place, in particular by means of a toothing tool, so that the region B is, for example, a tool run-out region.

12 shows a fifth embodiment of the differential stage planetary gear 46. 12 It can be seen that in the fifth embodiment the intermediate region 60 (transition region) is free of teeth.

It can be seen that the spur gear differential 12 comprises the planet carrier 28, which is driven or drivable in any way, and the two sun gears 14 and 16 of different sizes, which simultaneously represent the two outputs, also referred to as outputs, of the spur gear differential 12. The spur gear differential 12 also comprises the differential stage planet gear 46 or preferably a group of identical differential stage planet gears 46, wherein the group comprises at least or more than two identical differential stage planet gears 46. Preferably, the differential stage planetary gears 46 are arranged evenly distributed in the circumferential direction of the spur gear differential 12 running around the sun gear rotation axis 20, in particular over a respective circumference of the respective sun gear 14, 16. Furthermore, the spur gear differential 12 comprises the second differential planetary gear 36 or preferably a group of identical differential planetary gears 36, wherein preferably the plurality of differential planetary gears 36 are arranged evenly distributed in the circumferential direction of the spur gear differential 12 running around the sun gear rotation axis 20. In particular, a respective second differential planetary gear 36 is provided for each differential stage planetary gear 46. The differential stage planetary gears 46 and the second differential planetary gears 36 are rotatably mounted on, in particular on, their respective associated bolts 34 and 42. For example, rolling and/or sliding bearings can be used for this. The bolts 34 and 42 are fastened to, in particular in, the planet carrier 28, in particular in a rotationally fixed manner. The planet carrier 28 can be made in one or more parts, i.e. in one piece or in several parts. The planet carrier 28 is mounted, for example, directly or indirectly, in particular rotatably, relative to the one or more part housing 18, which is designed, for example, as a gear housing or as a drive housing. For example, a direct mounting between the planet carrier 28 and the housing takes place via at least or exactly two bearings, designed, for example, as plain bearings or roller bearings, in particular such that the planet carrier 28 is mounted rotatably on the housing 18 via the bearings mentioned, in particular such that the planet carrier 28 can rotate about the axis of rotation relative to the housing 18. The second differential planet gear 36 meshes with the second, smaller sun gear 16 and with the coupling planet gear 44, which is smaller than the first differential planet gear 30, in particular directly in each case, and preferably otherwise with no other, further gear. The first differential planetary gear 30, for example, meshes exclusively with the first, larger sun gear 14. In order to ensure that identical torques are applied to the two sun gears 14 and 16, and thus so that the drive torque can be or is divided equally between the sun gears 14 and 26 and thus the side shafts 22, 24, the ratios between the pitch circle diameters diameters of the sun gears 14 and 16 and those of the stepped planets (differential planet gear 30 and coupling planet gear 44) of the differential stage planet gear 46 are identical, so that: $$\text{WS1/WS2}=\text{WSP1/WSP2}$$

Here, WS1 designates the first pitch circle diameter of the first sun gear 14, WS2 the second pitch circle diameter of the second sun gear 16, WSP1 the third pitch circle diameter of the first differential planetary gear 30 and WSP2 the fourth pitch circle diameter of the coupling planetary gear 44. As previously described, the first pitch circle diameter is larger than the second pitch circle diameter, and the third pitch circle diameter is larger than the fourth pitch circle diameter.

All gear teeth of the spur gears can be straight or helical. Straight teeth are preferred. As stated in 4 is shown, the gears 48 and 52 are oriented rotationally to one another in such a way that the teeth 50 are exactly aligned with the teeth 54, so that gap 56 is exactly on gap 58 and tooth 50 is exactly on tooth 54, a tool outlet for a gear cutting tool for producing the smaller gear 52 can, for example, protrude into the gaps of the larger gear 48 to a certain extent, without removing material in the area of the larger gear 48. 90 designates a collar by means of which a particularly wide bearing base of the stepped planetary gear 64 can be represented.

In this way, the unusable intermediate region 60 between the gears 48 and 50 in the axial direction of the differential stage planetary gear 46 can be kept small or short. The smaller the difference between the third pitch circle diameter and the fourth pitch circle diameter, the smaller or shorter the intermediate region 60 that cannot be used for gearing advantageously becomes.

If the differential planetary gear 30 and the associated coupling planetary gear 44 are designed separately from one another and are connected to one another in a rotationally fixed manner, the rotationally fixed connection between the differential planetary gear 30 and the associated coupling planetary gear 44 can be implemented via a press fit, via a spline, a weld seam, a combination of these connections or in another way. One advantage here is that the differential planetary gear 30 and the associated coupling planetary gear 44 can be designed axially directly adjacent, i.e. without the intermediate region 60, which makes it possible to have a particularly short axial design.

• - Das Differentialstufenplanetenrad 46 kann einteilig beziehungsweise einstückig ausgeführt werden, wodurch die Kosten besonders geringgehalten werden können.
• - Durch das Eintauchen des Verzahnungswerkzeugs zum Herstellen der Verzahnung 52 in die Verzahnung 48 kann die Breite b3, die einen in axialer Richtung des Differentialstufenplanetenrads 46 verlaufenden Abstand zwischen dem Differentialplanetenrad 30 und dem Koppelplanetenrad 44 darstellt, kleingehalten werden.
• - Zahnfußfestigkeit höher als bei abgesetzten Zähnen.

Preferably, however, the intermediate region 60 with the width B3 is provided between the differential planetary gear 30 and the coupling planetary gear 44, and thus between the gear teeth 48 and 52. In the intermediate region 60, for example, there is the tool outlet of the gear cutting tool for producing the gear teeth 52 of the coupling planetary gear 44. The gear cutting tool, also referred to simply as a tool, even runs into the area of the gear teeth 48 of the differential planetary gear 30, for example, but only into the gaps 56 of the gear teeth 48, so that the gear teeth 48 are not damaged, machined or otherwise impaired by the gear cutting tool used to produce the gear teeth 52. In the intermediate region 60, the teeth 54 of the gear teeth 52 grow, so to speak, from the second pitch circle diameter or from the tip circle diameter k1 to the first pitch circle diameter or to the tip circle diameter k2. The radial outer contour 88 of the differential planetary gear 46 therefore does not fall below the tip diameter k1 of the coupling planetary gear 44, which is smaller than the first differential planetary gear 30, in the intermediate region 60. Preferably, the difference between the first pitch circle diameter of the differential planetary gear 30 and the second pitch circle diameter of the coupling planetary gear 44 is chosen to be as small as possible, since the width b3 of the intermediate region 60 can be kept small as a result. The advantages of this design are in particular:

• - The differential stage planetary gear 46 can be designed as a single piece or in one piece, which means that costs can be kept particularly low.
• - By plunging the gear cutting tool for producing the gearing 52 into the gearing 48, the width b3, which represents a distance between the differential planetary gear 30 and the coupling planetary gear 44 in the axial direction of the differential stage planetary gear 46, can be kept small.
• - Tooth root strength higher than with offset teeth.

• - einteilige beziehungsweise einstückige Ausführung
• - einfacher Herstellungsprozess

After all, as it is in 12 As shown, in the fifth embodiment it is conceivable that between the two toothings 48 and 52 or between the differential planetary gear 30 and the associated coupling planetary gear 44, viewed in the axial direction of the differential stage planetary gear 46, the intermediate region 60 with the width b3 exists, whereby in the 12 shown fifth embodiment, within the intermediate region 60, the outer diameter of the differential stage planetary gear 46 is significantly smaller than the smaller head compared to the tip diameter k2 of the teeth 50 or the toothing 48. circle diameter k1 of the teeth 54 or the gearing 52. The outside diameter is in 12 designated with a. The outer diameter a in this intermediate area 60 can even be the same size or smaller than a root diameter of the gearing 52. It is conceivable that, for example, the gear cutting tool for producing the gearing 52 does not penetrate into the area or into the gaps 56 of the gearing 48. In precisely this case, it is advantageous not to let the teeth 50 and 54 of the gearings 48 and 52 be axially aligned, but rather, as in 5 shown, the gears 48 and 52 are rotated relative to one another around the planetary axis of rotation 32. This rotational alignment or rotation of the gears 48 and 52 can at least be freely selected, but should be the same size for all differential stage planetary gears 46 so that the spur gear differential 12 can be advantageously mounted. In this specific embodiment, the gears 52 and 48 should therefore not necessarily have the same number of teeth. The disadvantage of this can be a large width b3 between the gears 48 and 52, which can, however, be classified as acceptable. The resulting advantages can be:

• - one-piece or one-piece design
• - simple manufacturing process

It is conceivable that the number of teeth in gears 48 and 52 are identical, whereby, for example, as is the case with the 4 shown first embodiment, the teeth 50 and 54 of the two gears 48 and 52 are aligned in the axial direction of the differential stage planetary gear 46. Alternatively, it is conceivable that, as shown in 5 As shown, the gear teeth 48 and 52, viewed in the circumferential direction of the differential stage planetary gear 46, are arranged rotated relative to one another in contrast to the mutually aligned alignment.

• - Bei klassischen Kegelraddifferentialen entstehen bei der Drehmomentübertragung hohe axiale Spreizkräfte zwischen den Kegelrädern, die über massive Gehäuse, häufig in Grauguss ausgeführt, aufgefangen werden müssen. Bei der Getriebevorrichtung 10 entstehen im Gehäuse 18 vorteilhafterweise keine signifikanten axialen Kräfte, wobei der Bauraumbedarf in axialer Richtung besonders geringgehalten werden kann, und der Planetenträger 28 kann deutlich leichter als ein Graugussgehäuse eines Kegeldifferentials ausgeführt werden.
• - Bei herkömmlichen Lösungen kann ein Nachteil darin bestehen, dass zwischen den beiden Sonnenrädern 14 und 26 ein signifikanter axialer Zwischenraum bestehen muss, in welchen die beiden breiten Planetenräder miteinander kämmen, ohne in diesem Bereich im Verzahnungseingriff mit einer der beiden Sonnen zu stehen. Im Gegensatz dazu kann bei der Getriebevorrichtung 10 der axiale Bauraumbedarf besonders geringgehalten werden, und das Gewicht und die Materialkosten können besonders geringgehalten werden.
• - Das zuvor beschriebene Problem kann beispielsweise dadurch gelöst werden, dass zumindest zum Teil Verzahnungen mit extremen Profilverschiebungen verwendet werden, was jedoch nachteilig für die Betriebsfestigkeit und die spezifische Belastbarkeit der betroffenen profilverschobenen Zahnräder sein kann und über eine deutliche Verbreiterung der profilverschobenen Verzahnungen kompensiert werden muss. Ferner wirkt sich die extreme Profilverschiebung nachteilig auf das Abwälzverhalten und damit auf die Geräuschabstrahlung der profilverschobenen Verzahnungen aus. Diese Nachteile und Probleme können bei der Getriebevorrichtung 10 vermieden werden. Es kann somit ein geringerer axialer Bauraumbedarf, ein geringeres Gewicht und geringere Materialkosten realisiert werden. Außerdem kann eine geringere mechanische Anregung (Geräuschabstrahlung) innerhalb der Verzahnung bei einer Relativdrehzahl dargestellt werden.

In particular, the following advantages can be realized by the transmission device 10:

• - In classic bevel gear differentials, high axial spreading forces arise between the bevel gears during torque transmission, which must be absorbed by massive housings, often made of gray cast iron. In the case of the gear device 10, no significant axial forces arise in the housing 18, whereby the installation space requirement in the axial direction can be kept particularly low, and the planet carrier 28 can be made significantly lighter than a gray cast iron housing of a bevel differential.
• - In conventional solutions, a disadvantage can be that there must be a significant axial gap between the two sun gears 14 and 26, in which the two wide planet gears mesh with each other without being in meshing engagement with either of the two suns in this area. In contrast, with the gear device 10, the axial installation space requirement can be kept particularly low, and the weight and material costs can be kept particularly low.
• - The problem described above can be solved, for example, by using at least some gears with extreme profile shifts, which can, however, be detrimental to the operational strength and the specific load-bearing capacity of the affected profile-shifted gears and must be compensated for by significantly widening the profile-shifted gears. Furthermore, the extreme profile shift has a detrimental effect on the rolling behavior and thus on the noise emission of the profile-shifted gears. These disadvantages and problems can be avoided with the gear device 10. This means that less axial installation space is required, less weight and lower material costs can be achieved. In addition, less mechanical excitation (noise emission) within the gears can be achieved at a relative speed.

List of reference symbols

10

Gearbox device

12

Spur gear differential

14

first sun gear

16

second sun gear

18

Housing

20

Sun gear rotation axis

22

first side wave

24

second side shaft

26

Planetary gear set

28

Planet carrier

30

first differential planetary gear

32

first planetary axis of rotation

34

bolt

36

second differential planetary gear

38

dashed arrow

40

second planetary axis of rotation

42

bolt

44

Coupling planetary gear

46

Differential stage planetary gear

48

first gearing

50

first tooth

52

second gearing

54

second tooth

56

first gap

58

second gap

60

Intermediate area

62

Planetary gear

64

Stepped planetary gear

66

first planetary gear

68

second planetary gear

70

third sun gear

72

Ring gear

74

dashed arrow

76

Arrow

78

Arrow

80

Planet carrier wall

82

Planet carrier wall

84

head Start

86

hub

88

Outer contour

90

collar

b1

first width

b2

second width

b3

third width

B

Area

V

Offset angle

a

outer diameter

k1

first tip diameter

k2

second tip diameter

QUOTES INCLUDED IN THE DESCRIPTION

This list of documents listed by the applicant was generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions.

Cited patent literature

• DE 102014203522 A1 [0002]
• DE 102015214035 B4 [0002]
• DE 102018128836 B3 [0002]

Claims (14)

Transmission device (10) for a motor vehicle, with a spur gear differential (12), which has: - a first sun gear (14), which is designed as a first output of the spur gear differential (12) and as a first spur gear and has a first pitch circle diameter; - a second sun gear (16) arranged coaxially to the first sun gear (14), which is designed as a second output of the spur gear differential (12) and as a second spur gear and has a second pitch circle diameter that is different from the first pitch circle diameter; and - at least one planetary gear set (26), by means of which the sun gears (14, 16) are coupled to one another in such a way that the sun gears (14, 16) can rotate in opposite directions, the planetary gear set (26) having: ◯ a planet carrier (28); ◯ at least one first differential planetary gear (30) which engages with the first sun gear (14), has a third pitch circle diameter and is held on the planet carrier (28) so as to be rotatable about a first planetary axis of rotation (32) relative to the planet carrier (28); ◯ at least one second differential planetary gear (36) which engages with the second sun gear (16) and is held on the planet carrier (28) so as to be rotatable about a second planetary axis of rotation (40) running parallel to the first planetary axis of rotation (32) and spaced from the first planetary axis of rotation (32); and ◯ at least one coupling planetary gear (44) arranged coaxially to the first differential planetary gear (30), connected in a rotationally fixed manner to the first differential planetary gear (30) and engaging in the second differential planetary gear (36) and thereby coupling the differential planetary gears (30, 36) to one another, which has a fourth pitch circle diameter that is different from the third pitch circle diameter and forms a differential stage planetary gear (46) with the first differential planetary gear (30) which is held on the planetary carrier (28) so as to be rotatable about the first planetary axis of rotation (32) relative to the planetary carrier (28) and has the first differential planetary gear (30) as the first stage planet and the coupling planetary gear (44) as the second stage planet; characterized in that a first ratio between the first pitch circle diameter and the second pitch circle diameter and a second ratio between the third pitch circle diameter and the fourth pitch circle diameter are the same. Gear device (10) according to Claim 1 , characterized in that: - the first differential planetary gear (30) has a first toothing (48) having a first number of teeth and a first toothing module, which engages in the first sun gear (14) and has first teeth (50) with a respective first tooth height; and - the coupling planetary gear (44) has a second toothing (52) having a second number of teeth and a second toothing module, which engages in the second differential planetary gear (36) and has second teeth (54) with a respective second tooth height. Gear device (10) according to Claim 2 , characterized in that: - the first number of teeth and the second number of teeth are the same; - the first tooth module and the second tooth module differ from one another; and - the respective first tooth height and the respective second tooth height differ from one another. Gear device (10) according to Claim 2 or 3 , characterized in that the first toothing (48) and the second toothing (52) are rotationally oriented to one another such that a respective gap (56) of the first toothing (48) of the first differential planetary gear (30) is aligned with a respective gap (58) of the second toothing (52) of the coupling planet (44). Transmission device (10) according to one of the preceding claims, characterized in that the stepped planets are formed integrally with one another. Gear device (10) according to Claim 5 and one of the Claims 2 until 4 , characterized in that a transition region (60) with a third width (b3) is provided in the axial direction of the respective stepped planet between the first stepped planet with a first width (b1) and the second stepped planet with a second width (B2), wherein a radial outer contour (88) of the differential stage planetary gear (46) in the transition region (60) does not fall below a first tip circle diameter (k1) of the second toothing (52), but increases from the first tip circle diameter (k1) to a second tip circle diameter (k2) of the first toothing (48). Gear device (10) according to Claim 6 , characterized in that the third width (b3) of the transition region (60) is smaller than the first width (b1) of the first stepped planet and smaller than the second width (b2) of the second stepped planet. Transmission device (10) according to one of the Claims 1 until 4 , characterized in that the first differential planetary gear (30) and the Coupling planetary gear (44) are formed separately from one another and connected to one another, wherein the one of the first and second stepped planets whose pitch circle diameter is smaller than the pitch circle diameter of the other of the first and second stepped planets has a projection (84) on which the other stepped planet is fastened. Gear device (10) according to Claim 8 , characterized in that the stepped planets are directly adjacent to one another in the axial direction of the respective stepped planet. Gear device (10) according to one of the preceding claims, characterized in that: - the first sun gear (14) has a third toothing having a third number of teeth and a third toothing module, which engages in the first differential planet gear (30) and has third teeth with a respective third tooth height; - the second sun gear (16) has a fourth toothing having a fourth number of teeth and a fourth toothing module, which engages in the second differential planet gear (36) and has fourth teeth with a respective fourth tooth height; - the third number of teeth and the fourth number of teeth differ from one another; - the third toothing module and the fourth toothing module are the same; and - the respective third tooth height and the respective fourth tooth height are the same. Transmission device (10) according to one of the preceding claims, characterized in that all teeth of the spur gear differential (12) are straight-toothed. Gear device (10) according to one of the preceding claims, characterized in that: - the gear device (10) has a planetary gear (62) which has: ◯ at least one stepped planetary gear (64) provided in addition to the differential stage planetary gear (46) and rotatably held on the planet carrier (28), which has a first planetary gear (66) as the third stage planet and a second planetary gear (68) as the fourth stage planet, which is connected in a rotationally fixed manner to the third stage planet, ◯ a third sun gear (70) provided in addition to the first sun gear (14) and in addition to the second sun gear (16) as the drive sun gear, with which one of the planetary gears (66, 68) is in engagement; and ◯ a ring gear (72) which is or can be connected in a rotationally fixed manner to a housing (18) of the gear device (10), with which the other planetary gear (68, 66) of the stepped planetary gear (64) is in engagement. Gear device (10) according to Claim 12 , characterized in that the second differential planetary gear (36) is connected to the ring gear (72), to the one planetary gear (66) and to the other planetary gear (68) of the planetary gear (62) in a direction (76) running in the axial direction of the second differential planetary gear (36), the ring gear (72) and the other planetary gear (68) of which are connected to the one planetary gear (66) of the planetary gear (62) in the direction (76), as a result of which the ring gear (72) and the other planetary gear (68) are arranged between the second differential planetary gear (36) of the spur gear differential (12) and the one planetary gear (66) of the planetary gear (62) when viewed in the axial direction of the second differential planetary gear (36). Gear device (10) according to Claim 12 or 13 , characterized in that the first pitch circle diameter of the first sun gear (14) is larger than the second pitch circle diameter of the second sun gear (16), which adjoins the first sun gear (14) in an arrangement direction (78) running in the axial direction of the first sun gear (14) and the second sun gear (16), which adjoins the third sun gear (70) in the arrangement direction (78), whereby the first sun gear (14) is arranged between the second sun gear (16) and the third sun gear (70) when viewed in the axial direction of the first sun gear (14) and the second sun gear (16).

Images