WO2023233010A1

WO2023233010A1 - Differential planetary gear system comprising ring gears, and drive device for motor vehicles

Info

Publication number: WO2023233010A1
Application number: PCT/EP2023/064852
Authority: WO
Inventors: Bernd-Robert HÖHN
Original assignee: Höhn Gmbh
Priority date: 2022-06-03
Filing date: 2023-06-02
Publication date: 2023-12-07
Also published as: DE102022114146A1

Abstract

The invention relates to a differential planetary gear system (10) comprising an input gear (12), a planet carrier (14; 14a; 14b) which is connected to the input gear (12) for co-rotation about the rotational axis (Y1), a first planet (16; 16a) which is mounted on the planet carrier (14; 14a; 14b), a second planet (18; 18a; 18b) which is mounted on the planet carrier (14; 14a; 14b), a first ring gear (20) which is provided on one side of the planet carrier (14; 14a; 14b) in the direction of the rotational axis (Y1) and which is in engagement with the first planet (16; 16a), and a second ring gear (24) which is provided on the planet carrier (14; 14a; 14b) side lying opposite the first ring gear (20) in the direction of the rotational axis (Y1) and which is in engagement with the second planet (18; 18a; 18b), wherein the second planet (18; 18a; 18b) is in engagement with the first planet (16; 16a) radially within the inner toothing (26) of the first ring gear (20) with respect to the rotational axis (Y1), the engagement points lie between the first planet (16; 16a) and the second planet (18; 18a; 18b) and between the first planet (16; 16a) and the first ring gear (20) on a common engagement plane, and a mounting supports a gear rim region (60) of the input gear (12) from a radial inner face.

Description

Planetary differential gear with ring gears and drive device for motor vehicles

The present disclosure relates to a planetary differential gear with ring gears and a drive device for motor vehicles with such a planetary differential gear.

Planetary differential gears with ring gears are known, for example, from DE 103 15 181 Al. A planet carrier is provided in this planetary differential gear. On one side of the planet carrier, several first planets are mounted, which mesh with a first ring gear. On the other side of the planet carrier, several second planets are mounted, which mesh with a second ring gear. Furthermore, openings are provided in the planet carrier, through which one of the first planets meshes in pairs with one of the second planets. The construction is such that each planet meshes with a first axial section of the toothing with the respective ring gear and with a second axial section of the toothing with the other assigned planet.

The object of the present disclosure is to provide an improved planetary differential gear and an improved drive device for motor vehicles. In particular, the improvement should lie in a more compact design, in particular a shorter design in the axial direction, and an increased or improved power transmission with a compact design.

This object is achieved with a planetary differential gear according to claim 1 or 21 or 26 and a drive device for motor vehicles according to claim 27. Further developments are specified in the dependent claims.

The planetary differential gear preferably has an input gear, which is preferably designed as a spur gear or bevel gear with straight or helical teeth. The input wheel is preferably mounted on or in a housing and is preferably driven by a drive machine, such as an electric motor or an internal combustion engine.

The planetary differential gear preferably has a planet carrier. The planet carrier is preferably designed as part of the input gear. The planet carrier is preferably the part lying radially with respect to the axis of rotation within the teeth of the input wheel of the input wheel. However, the planet carrier can also be provided as a separate component, which is mounted and provided in such a way that it rotates around the axis of rotation together with the input wheel. Torque is introduced into the differential gear via the input gear and transferred to the planet carrier.

The planetary differential gear has at least a first and a second planet. A pair of first planet and second planet is always preferred. Each planet is preferably designed as a spur gear with spur or helical teeth, for example. The planetary differential gear preferably has a plurality of first planets and a plurality of second planets, which are preferably rotatably mounted on the planet carrier about a respective planetary axis of rotation that is parallel to the axis of rotation of the input wheel, distributed evenly over the circumference. Storage is preferably carried out using rolling bearings (for example ball or roller bearings) or plain bearings. Depending on the requirements, the first and/or second planets are preferably each mounted on the planet carrier by means of a bearing pin (first planet bearing pin, second planet bearing pin). Alternatively, the planets, in particular the second planet, are stored directly on the planet carrier.

Such a planetary differential gear can be referred to as a spur gear differential gear.

Depending on the requirements, the bearing pin is, for example, integrally formed with the planet carrier. Alternatively (preferably), the bearing pin can be provided separately and attached to the planet carrier. Depending on the requirements, each first planet is preferably rotatably mounted about the planetary axis of rotation via a bearing on the respective bearing pin. Alternatively, the planet can have no bearing pin or can be formed integrally with the bearing pin or can be rigidly attached to it and, in this case, the bearing pin can be mounted together with the planet on the planet carrier so that it can rotate about the axis of rotation.

When the planet carrier rotates around the axis of rotation of the input wheel, the planetary axes of rotation rotate around the axis of rotation of the input wheel.

The planetary differential gear preferably has a first ring gear, which is rotatable about the axis of rotation of the input gear. The first ring gear and the first planets or the first planet are preferably arranged and designed such that an internal toothing of the first ring gear meshes or engages with the teeth of the first planet stands. As far as the terms meshing or meshing are used here and below with respect to two gears (planet, ring gear, input gear), this is to be understood as the gear meshing in the respective gear pair to form a gear transmission.

The first planet is therefore preferably designed to drive the first ring gear. The toothings are preferably coordinated with one another, so the first ring gear has the same type of toothing as the first planet (for example spur or helical toothing). Preferably, a toothing width of the first planet parallel to the axis of rotation (i.e. in the axial direction) is essentially equal to or greater than the toothing width of the first ring gear. The first ring gear is preferably designed as a cup-shaped ring gear, and therefore preferably has a base. The bottom is provided on the side of the first ring gear opposite the planet carrier.

The planetary differential gear preferably has a second ring gear, which is rotatable about the axis of rotation of the input gear. The second ring gear is preferably arranged on the axial side of the planet carrier that is opposite to the first ring gear. The second ring gear and the second planet (or the second planet) are preferably arranged and designed such that an internal toothing of the second ring gear meshes or is in engagement with the toothing of the second planet. The second planet is therefore preferably designed to drive the second ring gear. The toothings are preferably coordinated with one another, so the second ring gear has straight or helical toothings. The second ring gear is preferably designed as a cup-shaped ring gear, so it has a base. The floor is preferably provided on the side opposite to the planet carrier.

A (total) toothing width of the second planet parallel to the axis of rotation (i.e. in the axial direction) is preferably larger than that of the second ring gear. The second planet is preferably designed and arranged in such a way that it meshes with the second ring gear and the first planet. Preferably, the second planet meshes with the second ring gear in an axial region that differs from the axial region in which the second planet meshes with the first planet. The second planet preferably meshes with the first planet. dial within the first ring gear without being in engagement with the first ring gear. Preferably, the second planet meshes with the second ring gear radially within the second ring gear.

The second planet preferably has at least one externally toothed area (toothing area) along the second planetary axis of rotation, which is designed to come into engagement with the first planet. This externally toothed region preferably overlaps, as seen from the axis of rotation in a radial direction of the axis of rotation, with the internal toothing of the first ring gear.

As far as the term toothing area is used here and below, it preferably means an axial (partial) area of a gear in which a toothing is present.

The second planet is in engagement with the first planet and preferably the engagement of the second planet with the first planet and the engagement of the first planet with the first ring gear are both in a common engagement plane that is perpendicular to the axis of rotation. A second engagement plane perpendicular to the axis of rotation results from the engagement of the second planet with the second ring gear. Overall, only two levels of intervention are preferably provided. The engagement planes are preferably perpendicular to the axis of rotation.

The preferred arrangement and design of the second planet and the location of engagement of the second planet with the first planet result in a planetary differential gear that is compact in the axial direction. In particular, this is achieved in that the engagement between the second planet and the first planet and the engagement between the first planet and the first ring gear take place in a common first engagement plane perpendicular to the axis of rotation.

Due to the arrangement of the components, the specified planetary differential gear preferably enables an optimized power flow, especially for vehicles with a transversely installed engine. Due to the design optimized for the flow of force, it can preferably be designed to be light and compact. The first planet and the second planet preferably have the same tooth geometry. Here and below, the same gear geometry should preferably be understood to mean that at least the number of teeth and the tip circle of the different gears (the first planet and the second planet) are the same. The widths of the gears can be different (even with the same gear geometry). Alternatively or additionally, the base circle and the head circle of both planets are preferably the same. Alternatively or additionally, the gearing of the second planet is obtained by applying a profile shift to the gearing of the first planet.

The planets preferably differ in their axial length (parallel to the axis of rotation). The second planet is preferably longer than the first planet. In this way it can preferably be achieved that the second planet can come into engagement with the second ring gear at a first axial position (a first axial end) and can come into engagement with the first planet at a second axial position (preferably radially within the first ring gear). The second planet therefore preferably extends from radially within the first ring gear to radially within the second ring gear.

The ring gears preferably have tip circle diameters that differ from one another. The tip circle diameter defines the minimum inside diameter of the gearing. The tip circle diameter of the first ring gear is preferably larger than the tip circle diameter of the second ring gear. The tip circle diameter of the first ring gear is preferably larger such that the second planet, which is in engagement with the second ring gear, does not come into engagement with the first ring gear. The toothing area of the second planet, which is in engagement with the first planet, advantageously has the same toothing geometry as the toothing area which is in engagement with the second ring gear. The planets preferably have the same toothing geometries (with the exception of the width if necessary), in particular the same tip circle diameter.

In a projection onto a plane perpendicular to the axis of rotation, the tip circle of a toothing region of the second planet, which is in engagement with the first planet, therefore preferably does not intersect the tip circle of the first ring gear or is preferably located radially within the tip circle of the first ring gear. In a projection onto a plane perpendicular to the axis of rotation, the tip circle of a gear area of the second planet intersects with the second ring gear is engaged, preferably the tip circle of the second ring gear ^engagement).

In a possible embodiment, the root circle of the second ring gear can be larger than the tip circle of the first ring gear.

Furthermore, the ring gears preferably have the same number of teeth despite unequal tip circles. This is preferably achieved by a corresponding profile shift. In this way, with, for example, the same toothing geometry of the planets or the same tip circle diameter of the planets and/or the same number of teeth on the planets, it is preferably achieved that the translation resulting from the engagement between the first planet and the first ring gear is equal to that resulting from the engagement between the second planet and the second ring gear resulting translation is. This leads to an even distribution of torque across the ring gears.

The tip circle of the first planet, on the other hand, can be designed such that it intersects the tip circle of the first ring gear and the tip circle of the second ring gear in a projection onto a plane perpendicular to the axis of rotation.

The radial distance of the first planetary axis of rotation of the first planet from the axis of rotation of the planet carrier is therefore preferably greater than the radial distance of the second planetary axis of rotation of the second planet from the axis of rotation of the planet carrier.

The second planet preferably has a continuous toothing, with one area of the continuous toothing meshing with the first planet and an axially different area of the toothing meshing with the second ring gear. This allows for easy production. In this case, the second planet is preferably mounted on the planet carrier via the second planet bearing pin. Here, a first end side of the second planet bearing pin is preferably mounted on the planet carrier. For example, a plain or rolling bearing is used as a bearing, which is provided between the planet and the second planet bearing pin. Alternatively, the second planet bearing pin can also be rotatably mounted on the planet carrier. In this case, the toothing is, for example, rigidly provided on the bearing pin. In the case of a second planet with continuous teeth, both bearing pins (for the first planet and for the second planet) are preferably arranged on the (same) side of the first ring gear with respect to the planet carrier. Preferably, the end sides of both bearing pins, which face the second ring gear, are attached to, mounted on, or formed integrally with the planet carrier. A bearing disk is also preferably provided, in which the ends of the bearing pins facing the first ring gear are mounted/supported.

In such a configuration, the planet carrier preferably has a second planet receiving area, which is designed as a cup-shaped recess in the planet carrier, which deepens in the direction of the second ring gear. The radially outwardly directed part of the pot side wall is preferably opened and the fastening of the second planetary bearing bolt is preferably provided in the form of a through hole in the bottom area of the recess. In the assembled state of the second planet bearing pin with second planet, a first toothing area of the second planet, which meshes with the first ring gear, can mesh with the second ring gear through the open pot side wall area. The depth of the cup-shaped depression in the axial direction preferably corresponds essentially to the toothing width of the first toothing region.

By storing the bearing pins using the bearing disk and the planet carrier, the bearing pins are supported from both end sides. This preferably enables the planets to be supported in a torsion-resistant manner.

In another preferred embodiment, the second planet has at least a first toothing region (axial region in which a toothing is provided) for engagement with the second ring gear and a second toothing region for engagement with the first planet. A storage area, which is preferably not toothed, is preferably provided between the toothed areas. The storage area is preferably mounted on the planet carrier so that it can rotate about the planetary axis of rotation. For example, a sliding or rolling bearing is preferably used. The toothed areas are preferably connected to one another in a torsionally rigid manner via the bearing area, so that a torque can be transmitted. Preferably, the first toothing region is formed integrally with a second planetary bearing pin or is fastened in a torsionally rigid manner on a second planetary bearing pin. Alternatively, the second toothing area is preferably formed integrally with the second planetary bearing pin or torsionally rigid on a bearing pin. The storage area is preferably cylindrical.

If a bearing area is provided in the second planet (between the toothing areas), this is preferably attached/mounted on the planet carrier by means of a bearing component which can be mounted on the planet carrier. The planet carrier, together with the mounted bearing component, forms a bearing holder in which the bearing area of the second planet is stored.

A possible advantage of such a design is, for example, the central mounting of the second planet on the planet carrier and the easy assembly of the second planet while simultaneously making the second planet simple and cost-effective.

In a further embodiment, the bearing area of the second planet is preferably held in a through hole in the planet carrier. In this case, the first or second toothing region of the second planet is preferably fastened in a rotationally rigid manner to the second planet bearing pin after the bearing region has been inserted into the through hole. All known shaft-hub connections can be used here, for example a feather key or a press fit.

A possible advantage of such a design is the simple design of the planet carrier with central storage of the second planet on the planet carrier.

In both of the last-mentioned embodiments, a bearing disk can preferably be provided in which the end of the first planetary bearing pin and the second planetary bearing pin facing the first ring gear are mounted/fastened.

With regard to all configurations, the toothing widths of the first toothing area of the second planet and the second ring gear are preferably coordinated with one another, as are the toothing widths of the first planet and the first ring gear, as well as the toothing widths of the second toothing area of the second planet and the first planet. In this way, a compact design with maximum torque transmission can preferably be achieved. In particular, it follows from the pairwise coordination of the tooth widths of the first ring gear with the first planet that preferably no or only small tilting moments act on the first planet. The long second planet in turn is preferably also advantageously supported via its axial length and support on the second ring gear, the first planet and the bearing on the planet carrier.

In a further alternative embodiment, the first toothing area of the second planet and the second toothing area of the second planet can have different toothing geometries and/or numbers of teeth and/or tip circle diameters. In this case, the ring gears can also have different numbers of teeth and/or the same or different tip circles, depending on the requirements. Such a configuration is only limited by the fact that the second planet and the first planet mesh with one another radially within the first ring gear, the second planet does not mesh with the first ring gear, the first planet meshes with the first ring gear and the second planet meshes with the second hollow - wheel combs and the planets are mounted on a common planet carrier. It is also preferred here that the translations of the first planet to the first ring gear are the same as the second planet to the second ring gear.

In an advantageous embodiment, which relates to all of the above embodiments, the input wheel is preferably supported in an O-arrangement by means of two bearings (sliding or rolling bearings). Preferably, a gear rim area on which the teeth are provided on the outside is supported from the radial inside by the bearings provided on both sides of the planet carrier. The bearings can be provided separately or integrally as sliding surfaces of the housing. A force is introduced into a housing preferably via (bearing) support flanges provided radially on the inside of the gear ring area. Such a bearing arrangement preferably enables a compact design while supporting high forces through the bearings, in particular due to the geometrically advantageous arrangement and advantageous size of the bearings. This preferably results in a high, advantageous torsional rigidity because the calculated bearing width is larger than the real bearing distance of the rolling bearings (for more information, see the Schaeffler rolling bearing catalog).

In the preferred drive device for motor vehicles, the axle shafts (joint shafts) are preferably attached directly to the ring gears via appropriate screw connections, which means an advantageous simple and compact design. On the use otherwise The use of quick-release axles can thus preferably be dispensed with because the conventional interface, ie the previously used axle shaft flange, can be adopted from the series.

Overall, a light and compact drive device is specified.

The ring gears are preferably sealed, guided and/or mounted on the bearing support flanges (preferably from a radial inside). This preferably creates an encapsulated design in which the differential can be at least partially filled with grease.

The toothing area of the first planet is preferably wider than the first toothing area of the second planet. The difference in width or the width can preferably be calculated taking into account an alternating load factor, which results from the two interventions present in the first planet in the same toothing (on the leading and trailing flanks of the toothing of the first planet) with, on the one hand, the first ring gear and, on the other hand, the second planet results.

The number of teeth, widths and diameters are calculated as usual from given parameters such as loads and required gear ratios. The number of teeth on the planets preferably results from a minimum number of teeth required for the overlap of 8 _a > 1 (for the tooth engagement between the first and second planets 16, 18).

The disclosure also includes in particular the following aspects:

1. Planetary differential gear (10), with an input wheel (12), which is rotatable about an axis of rotation (R), a planetary carrier (14; 14a; 14b), which is designed as part of the input wheel (12) or is rotationally rigid the axis of rotation (Yl) is connected to the input wheel (12), a first planet (16; 16a), which is mounted on the planet carrier (14; 14a; 14b) in such a way that it can be rotated about a first planetary axis of rotation (PI), which runs parallel to the axis of rotation (R) and rotates around the axis of rotation (Yl) with the rotation of the input wheel (12), a second planet (18; 18a; 18b), which is mounted on the planet carrier (14; 14a; 14b) in such a way that it can be rotated about a second planetary axis of rotation (P2), which runs parallel to the axis of rotation (Yl) and with which Rotation of the input gear (12) revolves around the axis of rotation (Yl), a first ring gear (20) with internal teeth (22) which runs in the direction of the axis of rotation (Yl) on one side of the planet carrier (14; 14a; 14b) and around the axis of rotation (Yl) is rotatably provided and is in engagement with the first planet (16; 16a) by means of its internal teeth (22), and a second ring gear (24) with internal teeth (26) which is in the direction of the axis of rotation (Yl ) is provided on the side of the planet carrier (14; 14a; 14b) opposite the first ring gear (20) and rotatable about the axis of rotation (Yl) and by means of its internal teeth (26) with the second planet (18; 18a; 18b). Engagement is in which the second planet (18; 18a; 18b) is radially within the internal toothing (26) of the first ring gear (20) with the first planet (16; 16a) is engaged and the engagements between the first planet (16; 16a) and the second planet (18; 18a; 18b) and between the first planet (16; 16a) and the first ring gear (20) lie in a common engagement plane .

2. Planetary differential gear according to aspect 1, in which the tip circle diameter of the first ring gear (20) is larger than the tip circle diameter of the second ring gear (24), and / or the number of teeth of the first ring gear (20) is equal to the number of teeth of the second ring gear (24 ), and/or the toothing geometry of the second ring gear (24) is obtained by profile shifting the toothing geometry of the first ring gear (20).

3. Planetary differential gear according to aspect 1 or 2, in which the second planet (18; 18b) has a first toothing region (28; 28b) which is designed to engage in the internal toothing (26) of the second ring gear (24), and has a second toothing area (30; 30b) which is designed to engage in the first planet (16).

4. Planetary differential gear according to aspect 3, in which the first toothing area (28; 28b) of the second planet (18) and the second toothing area (30; 30b) of the second planet (18) have the same toothing geometry.

5. Planetary differential gear according to aspect 3 or 4, in which the first toothing region (28; 28b) of the second planet (18; 18b) has a toothing width which corresponds to a toothing width of the internal toothing (26) of the second ring gear (24), and / or the second toothing area (30; 30b) of the second planet (18; 18b) has a toothing width that corresponds to a toothing width of the first planet (16), and / or the first planet (16; 16a) has a toothing area (32; 32a ) with a toothing width that corresponds to the toothing width of the internal toothing (22) of the first ring gear (20) and / or the toothing area (32a) of the first planet (16a) preferably over its entire width with the toothing of the first ring gear (20). intervention is.

6. Planetary differential gear according to one of aspects 3 to 5, in which the second planet (18; 18b) has a bearing area (34; 34b) which is in the direction of the second planetary axis of rotation (P2) between the first toothing area (28; 28b ) of the second planet (18; 18b) and the second toothing area (30; 30b) of the second planet (18; 18b), and the second planet (18; 18b) by means of the bearing area (34; 34b) on the planet carrier ( 14; 14b) is stored.

7. Planetary differential gear according to aspect 6, in which the planet carrier (14) forms an open first bearing shell (36) into which the bearing area (34) of the second planet (18) is inserted, and one mounted on the planet carrier (14). Bearing component (38) is provided, by means of which the bearing area (34) of the second planet (18) is mounted in the first bearing shell (36).

8. Planetary differential gear according to aspect 6, in which the second planet (18b) has a planetary shaft (40) which forms the bearing area (34b), the planet carrier (14b) has a first through hole (42) for supporting the bearing area (34b) of the second planet (18b), and at least one the toothing areas (28b, 30b) of the second planet (18b) is fastened on the planetary shaft (40) after inserting the bearing area (34b) of the second planet (18b) into the first through hole (42).

9. Planetary differential gear according to aspect 4, in which the second planet (18a) has a continuous toothing (44) in the direction of the second planetary axis of rotation (P2), which has the first toothing area of the second planet (18a) and the second toothing area of the second Planet (18a) formed.

10. Planetary differential gear according to aspect 9, in which the first planet (16a) has a toothing area (32a) with a toothing width which corresponds to the toothing width of the internal toothing (22) of the first ring gear (20), and / or the toothing area (32a ) of the first planet (16a) is preferably in engagement with the teeth of the first ring gear (20) over its entire width.

11. Planetary differential gear according to aspect 9 or 10, further comprising a second planet bearing pin (46) for supporting the second planet (18a), in which the second planet bearing pin (46) on the planet carrier (14a) so it is provided that it protrudes towards the side of the first ring gear (20) and / or the planet carrier (14a) is at least partially axially between an end of the second planet (18a) facing the second ring gear (24) and the second ring gear (24). extends.

12. Planetary differential gear according to aspect 11, in which the planet carrier (14a) has a second planetary receiving area (48) which projects axially towards the second ring gear (24) and on which one towards the first ring gear (20 ) opposite end of the second planet bearing bolt (46) is held. 13. Planetary differential gear according to aspect 11 or 12, further comprising a bearing disk (50) with at least one through hole (52), and an end of the second planetary bearing pin (46) facing the first ring gear (20) in the at least one Through hole (52) is held.

14. Planetary differential gear according to one of aspects 1 to 13, further comprising a first planet bearing pin (54; 54a) which is provided on the planet carrier (14; 14a; 14b), in which the first planet (16; 16a) is mounted on the first planet bearing pin (54; 54a) and/or an end of the first planet bearing pin (54; 54a) facing the second ring gear (24) is provided on the planet carrier (14; 14a; 14b). is.

15. Planetary differential gear according to aspect 14, as far as related to aspect 13, in which an end of the first planetary bearing bolt (54) facing the first ring gear (20) is held in a further through hole (56) in the bearing disk (50).

16. Planetary differential gear according to one of aspects 1 to 15, in which the second planet (18; 18a; 18b) is not in engagement with the first ring gear (20) and / or the second planet (18; 18a; 18b) only is in engagement with the second ring gear (24) and the first planet (16; 16a), and/or the first planet (16; 16a) only with the first ring gear (20) and the second planet (18; 18a; 18b) is in action.

17. Planetary differential gear according to one of aspects 1 to 16, which further has a first bearing (58) for storage, in particular for radial storage, of the input wheel (12), in which the input wheel (12) has a cylindrical ring gear area (60 ), on the outer circumference of which a toothing (62) is provided, and a planet carrier area (64) which Planet carrier (14; 14a; 14b) and is formed radially on the inside of the gear rim region (60), and the first bearing (58) on a first axial side of the planet carrier region (64) has the cylindrical gear rim region (60) from a radial inside supported.

18. Planetary differential gear according to aspect 17, further comprising a housing (66), in which the first bearing (58) is a ball or roller bearing, the housing (66) forming a first bearing support flange (68) which forms the first bearing (58) is supported from a radial inside, and the cylindrical ring gear region (60) is supported on its radial inside on the first bearing (58).

19. Planetary differential gear according to aspect 17 or 18, which further comprises a second bearing (70) for storage, in particular for radial storage, of the input gear (12), in which the second bearing (70) is on the relative to the first bearing (58) opposite axial side of the planet carrier area (64) supports the cylindrical ring gear area (60) from the radial inside.

20. Planetary differential gear according to aspect 19, as far as related to aspect 18, in which the second bearing (70) is a ball or roller bearing, the housing (66) forms a second bearing support flange (72), which the second bearing (70) supported from a radial inside, and the cylindrical gear rim region (60) is supported on its radial inside on the second bearing (70).

21. Drive device for motor vehicles with a planetary differential gear according to one of aspects 1 to 20, in which the input wheel (12) is designed to be driven by a drive machine, and each of the ring gears (20, 24) is designed as an output wheel to be connected in a torsionally rigid manner to an axle shaft.

The term “plane of engagement” of a (tooth) engagement (toothing) of two gears is preferably understood to mean a plane perpendicular to the axes of rotation of the gears. The teeth of the gears mesh with each other in the meshing plane. Since the teeth of the gears each have a certain width (tooth width) and the teeth of the gears overlap at least partially (in the radial direction of the respective gears) for the engagement, the gear engagement usually does not take place in just a single plane perpendicular to the axes of rotation, but in all (parallel) planes that intersect the tooth mesh (i.e. in a family of mesh planes). The planes are defined by the overlap width of the teeth (width of tooth mesh). The claimed “common engagement level” is a single level of the usually many levels that intersect both engagements (between first planet and second planet and between first planet and first ring gear). This preferably does not necessarily mean that all levels of engagement between the first planet and the second planet are identical to those between the first planet and the first ring gear. Instead, the claimed “common engagement level” is already present when there is a single level in which the two tooth engagements take place. Preferably, the engagement planes of both tooth meshes are essentially identical, i.e. the tooth area (in relation to the tooth width) of the first planet that comes into engagement with the second planet is essentially the same tooth area that in the further rotation of the first planet with the first Ring gear engages.

In order to achieve the support of the input wheel when mounted (preferably O-arrangement, but also X-arrangement), the bearings for supporting the input wheel are preferably designed as angular contact bearings (e.g. angular contact ball bearings, tapered roller bearings).

One or more embodiments of the disclosure are described below with reference to the figures, which show

1 is a schematic partial exploded view of a planetary differential gear according to a first embodiment, 2 shows a side view of the planetary differential gear according to the first embodiment,

3 shows a schematic cross-sectional view of the planetary differential gear according to the first embodiment along the section line AA in FIG. 2,

4 is a schematic enlarged partial cross-sectional view of the planetary differential gear according to the first embodiment in the direction of a Y axis,

5 is a schematic partial exploded view of a planetary differential gear according to a second embodiment,

6 shows a side view of the planetary differential gear according to the second embodiment,

7 is a schematic cross-sectional view of the planetary differential gear according to the second embodiment along the section line AA in FIG. 6,

8 is a schematic partial exploded view of a planetary differential gear according to a third embodiment,

9 shows a side view of the planetary differential gear according to the third embodiment, and

Fig. 10 is a schematic cross-sectional view of the planetary differential gear according to the third embodiment along the section line AA in Fig. 9.

A first embodiment of the planetary differential gear 10 is described below with reference to Figures 1 to 4. Reference is made here to the coordinate system (X-Y-Z directions) shown in the figures.

The planetary differential gear 10 has an input gear 12, the axis of rotation Y1 of which runs parallel to the Y axis. The input gear 12 is integrally formed from a planet carrier area 64 and a gear ring area 60. The planet carrier area 64 forms the planet carrier 14 and is designed as a (circular) disk with recesses. The input gear 12 is designed as a spur gear. The toothing 62 is located radially on the outside, is designed as helical teeth (usually for reasons of noise) and is provided on the cylindrical gear ring area 60. The cylinder axis of the gear ring area 60 corresponds to the axis of rotation Yl. The gear ring area 60 is connected to the planet carrier area 64 radially on the inside and axially in the middle. The (here three) recesses in the piano net carrier area 64 are essentially V-shaped, with a half-open first bearing shell 36 being formed in the bottom of the V-shape to accommodate a bearing area 34 of a second planet 18 described below.

Three first planets 16 are provided in the Y direction on one side of the planet carrier 14 (on the side in the positive Y direction). The first planets 16 are mounted on the planet carrier 14 so that they can rotate about respective first planetary axes of rotation PI on a first-planet bearing pin 54. The storage is carried out in a known manner, for example via preferably plain bearings or alternatively rolling bearings and is therefore not described or shown in more detail. Each first planet bearing pin 54 is rigidly attached to the planet carrier 14 at its end facing the planet carrier (end in the negative Y direction), for example in a corresponding through hole 74. The attachment is carried out in a known manner, for example by pressing. The first planetary axes of rotation PI or the axis of the first planetary bearing pin 54 of all three first planets 16 run parallel to the Y-axis and lie on a common first radius RI in relation to the axis of rotation Yl. When the planet carrier 14 rotates about the axis of rotation Yl, the first planetary axes of rotation PI rotate around the axis of rotation Yl.

Each first planet 16 has a toothing area 32 and thus forms, for example, a spur gear with straight teeth, as shown.

Three second planets 18 are also provided. The second planets 18 are rotatably mounted on the planet carrier 14 about respective second planetary axes of rotation P2. In this embodiment, every second planet 18 extends in the Y direction on both sides of the planet carrier 14 (i.e. from one side to the other side). The second planetary axes of rotation P2 run parallel to the Y axis and all lie on a common second radius R2 in relation to the axis of rotation Y 1. The radius R2 is smaller than the radius RI. When the planet carrier 14 rotates about the axis of rotation Y1, the second planetary axes of rotation P2 rotate around the axis of rotation Y1.

In this embodiment, the second planets 18 are each preferably constructed as follows: every second planet has a first toothing region 28 and a second toothing region 30 along its second planetary axis of rotation P2. The above-mentioned storage area 34 is provided between the toothing areas 28, 30. Preferably points the bearing area 34 has a smaller outer diameter than the root circles of the toothing areas 28, 30.

The gear areas have the same gear geometry. The entire second planet 18 is preferably machined from one piece. The first toothing area 28 is here connected in a torsionally rigid manner to the second toothing area 30 due to the one-piece production.

To support the second planets 18 on the planet carrier 14, the storage areas 34 of the second planets 18 are inserted into the first bearing shells 36. Furthermore, bearing components 38 are provided, by means of which the storage areas 34 can be held in the bearing shells 36. The storage areas 34 and bearing shells 36 and bearing components 38 preferably form plain bearings, so that the second planets 18 are mounted on the planet carrier 14 so that they can rotate about the second planetary axis of rotation P2. Alternatively, additional bearings, for example a roller bearing, are provided between the bearing area 34 and the bearing shells 36 and the bearing component 38. The bearing components 38 are preferably attached to the planet carrier 14 via screws.

In the state in which the second planet 18 is mounted on the planet carrier 14, the first gear portion 28 is on the side of the planet carrier 14 on which the first planet 16 is not disposed, and the second gear portion 30 is on the side of the planet carrier 14, on which the first planet 16 is arranged.

A first ring gear 20 is provided on the side of the first planets 16 of the planet carrier 14 (side in the positive Y direction). The first ring gear 20 is closed here on one side, on the side opposite to the planet carrier. The first ring gear 20 has an outer circumference that is smaller than the circumference of the ring gear region 60 of the input gear 12.

The first ring gear 20 is designed and installed in such a way that its internal teeth 22 mesh with the first planet 16. The first ring gear 20 can therefore be driven by the first planets 16, both by rotation of the first planets 16 about the first planetary axis of rotation PI and also by rotation of the planet carrier 14 about the axis of rotation Y 1 when the first planet 16 is stationary with respect to the planetary carrier 14. In the latter case moves the first ring gear with the rotating first planet 16. Of course, a combination of movements also comes into consideration. Due to the circumferentially uniform distribution of the first planets 16, the ring gear 20 is preferably supported radially by the first planets 16 with little play.

The second planets 18 in turn are arranged and designed in such a way that every second planet 18 is arranged in pairs with a first planet 16 and (on the side of the planet carrier 14 on which the first planets 16 are arranged) meshes with a first planet 16 without simultaneously meshing with or engaging with the internal toothing 22 of the first ring gear 20. The toothing area 32 of each first planet 16 is therefore in engagement with a second toothing area 30 of a second planet 18 and in engagement with the internal toothing 22 of the first ring gear 20. As can be clearly seen in Figure 4, the first planet 16 also engages the first ring gear 22 at a position that has the largest possible radius in relation to the axis of rotation Y1. The engagement with the second planet 18 takes place radially further inwards with a smaller radius, so that the second toothing region 30 of the second planet 18 does not come into engagement with the internal toothing 22 of the first ring gear 20.

The second ring gear 24 is designed and installed in such a way that its internal teeth 26 mesh with the first toothing region 28 of the second planet 18. The second ring gear 24 can therefore be driven by the second planets 18, both by rotating the second planets 18 about the second planetary axis of rotation P2 and also by rotating the planetary carrier 14 about the axis of rotation Y1 when the second planet 18 is stationary with respect to the planetary carrier 14. In the latter In this case, the ring gear moves with the rotating second planet 18. Of course, a combination of movements also comes into consideration. Due to the circumferential distribution of the second planets 18, the second ring gear 24 is preferably supported radially by the second planets 18 with little play.

Since the toothing areas 28, 30 of the second planet 18, as stated above, are designed in this embodiment with the same/same toothing geometry and (also due to the integral design) lie on a common second planetary axis of rotation P2, which is radially further inward than the first planetary axis of rotation PI is located, the second ring gear 24 must have a smaller tip circle diameter (inner diameter) in order to be compatible with the first To be able to come into engagement with the toothed area 28 of the second planet 18. In order to realize that a gear ratio between the second planet 18 and the second ring gear 24 is equal to the gear ratio between the first planet 16 and the first ring gear 20, the tooth number ratios of the interventions must be designed to be the same.

In the present embodiment, the toothing area 32 of the first planet 16 preferably also has the same toothing geometry as the toothing areas 28, 30 of the second planet 18. In order to achieve the same translations mentioned above, the second ring gear 24 has the same number of teeth as the first ring gear 20 but has a reduced tip circle diameter. This is achieved by profile shifting, as is known in the art.

4, the construction of the planetary differential gear is preferably such that, with the same toothing geometries of the toothing areas 28, 30, 32 of the planets 16, 18, the second planetary axes of rotation P2 of the second planets are on a smaller radius R2 are arranged with respect to the axis of rotation Y 1. The smaller radius R2 results, for example, from the formula

R2 = 0.5 x DKHI - 0.5 x DKP2 - s (Formula 1) where

DKHI is the tip circle diameter of the first ring gear 20,

DKP2 is the tip circle diameter of the second toothing region 32 of the second planet 18, and s is a desired distance between the tip circle of the first ring gear 20 and the

Tip circle of the second toothing area 32 of the second planet 18 is. For example, s is preferably in the range from 0.01 mm to 5 mm, more preferably between 0.1 mm and 3 mm, such as 0.2 mm or 1 mm.

The common radius R2 is smaller than the common radius RI.

The necessary profile shift for the second ring gear 24 then results from R2 in conjunction with the toothing geometry of the first toothing region 28 of the second planet 18. For uniform torque transmission, as is desired in differential gears, especially axle differential gears, it is advantageous if, on the one hand, the engagement between the planets is implemented with a gear ratio of value 1 and, on the other hand, the gear ratios between the planets and the ring gears each have the same value have. The former is realized, for example, in that at least the toothing area 32 of the first planet 16 and the second toothing area of the second planet 18 have the same toothing geometry. The latter is achieved, for example, in that the tooth number ratios of the engagement between the toothing area 32 of the first planet 16 and the first ring gear 20 and the engagement of the first toothing area 28 of the second planet 18 and the second ring gear 24 have the same value.

This can be achieved particularly advantageously if all the toothing areas of the planets have the same toothing geometry and the internal toothing of the ring gears only differs by profile shift.

It should be noted that in a possible embodiment, the toothing area 32 of the first planet 16 has a greater width than the internal toothing 22 of the first ring gear 20 and/or than the width of the second toothing area 30 of the second planet 18 due to its alternating load or the two interventions may have. In advantageous embodiments, the width of the toothing area 32 of the first planet 16 is designed with alternating load factor and the internal toothing 22 of the first ring gear 20 and/or the second toothing area 30 of the second planet 18 have the same widths as the width of the toothing area 32 of the first planet 16 , are then oversized. The first toothing area 28 of the second planet 18 and the internal toothing 26 of the second ring gear 24 preferably also have the same width as the toothing area 32 of the first planet 16.

The planetary differential gear 10 also has a housing 66. The housing serves to store the components in the housing and to fasten the planetary differential gear 12 to other units, for example of a motor vehicle. The housing 66 is composed of two half-shells that at least partially enclose the input wheel 12. The housing 66 forms a bearing support flange 68, 72 which extends axially in the direction of the planet carrier 14 on both sides of the planet carrier 14, radially on the inside of the gear rim area 60 of the input wheel 12. The input wheel 12 is mounted on the housing 66 via a first bearing 58 and a second bearing 70, both of which are designed as ball bearings here, for example. The bearing axes lie in the rotation axis Yl. In particular, an inner ring of the first bearing 58 is provided radially on the inside on the radial outside of the first bearing support flange 68. The inner ring of the first bearing 58 rests axially on the housing 66. An outer ring of the first bearing 58 supports an axial side of the ring gear region 60 radially from the inside. The outer ring of the first bearing 58 rests axially on the planet carrier area 64. The second bearing 70 is correspondingly provided on the other axial side of the planet carrier 14. Both bearings 58, 70 together support the input wheel 12 essentially in an O-arrangement. As a result, the calculated bearing width becomes larger than the real bearing distance of the rolling bearings, making the bearing “stiffer”. The bearing arrangement is advantageously such that, in addition to radial support, there is also axial support.

In the present embodiment, the ring gears 20, 24 are radially and/or axially supported and/or sealed on the radial outside on the radial insides of the bearing support flanges 68, 72. The gear interior designed in this way for the planetary differential gear can be at least partially filled with a special lubricant, such as grease.

In a drive device for a motor vehicle, the input wheel 12 is driven by a drive machine and each of the ring gears 20, 24 is connected to an axle shaft with which one wheel is driven. The axle shafts are preferably attached directly to the ring gears 20, 24 via corresponding end flanges, for example by screwing with the provided threaded holes 78.

Further embodiments will be described below with reference to FIGS. 5 to 10. The planetary differential gear or drive device of the further embodiments correspond to those of the first embodiment unless otherwise described or shown in the figures. For the same or similar components or groups of components, the same reference numerals or reference numerals are used, some of which are provided with an additional letter for better differentiation. Individual features of the further embodiments can be combined with other individual features of the first embodiments described above or the other other embodiments, as far as this is not technically impossible or does not make sense. In principle, formula 1 above and/or the representation of FIG. 4 preferably also applies to the other embodiments.

Figures 5 to 7 show a planetary differential gear 10a according to a second embodiment. It should be noted that the view of FIG. 5 is rotated 180 degrees about the Z axis compared to the view of FIG. 1, so that therefore the first ring gear 20 in FIG. 5 is the right ring gear. Some reference numbers are indicated in the figures, which are not explained separately in the following description of the embodiment. To explain these reference numbers, reference is made to the description of the first embodiment.

The planetary differential gear 10a according to the second embodiment differs from the planetary differential gear 10 according to the first embodiment in particular in that the structure or construction of the second planet and the planet carrier is modified.

As in the first embodiment, the first planet 16a is arranged on the side of the first ring gear 20 with respect to the planet carrier 14a and is in engagement with it. Similar to the first embodiment, the first planet 16a is supported by a first planet bearing pin 54a held in a through hole 74a in the planet carrier 14a.

The planetary differential gear 10a according to the second embodiment has a second planet 18a, which is designed as a spur gear with continuous teeth 44. The second planet 18a therefore does not have the bearing area 34 present in the first embodiment, which is provided between the first toothing area 28 and the second toothing area 30. The second planet 18a according to the second embodiment, as in the first embodiment, has a first toothing area for engagement with the second ring gear 24 and a second toothing area for engagement with the first planet 16a. Since the toothing 44 of the second planet 18a is continuous, the first toothing area merges integrally into the second toothing area. The second planet 18b is therefore easy to manufacture as an elongated spur gear. The second planet 18a is supported on the planet carrier 14a via a second planet bearing pin 46, on which the second planet 18a (or its toothing 44) is rotatably mounted about the second planetary axis of rotation P2, for example via plain bearings or roller bearings.

The second planetary bearing pin 46 is attached to the planet carrier 14a in a similar manner to the first planetary bearing pin 54 in the first embodiment, for example pressed into a corresponding through hole 80 in the planetary carrier 14a.

The through hole 80 is formed in the bottom of a cup-shaped recess formed in the planet carrier 14a and extending toward the second ring gear 24. A side wall region of the cup-shaped recess that lies radially outward with respect to the axis of rotation Y1 is recessed (or opened in such a way) that the toothing 44 (or a first toothing region) of the second planet 18a is exposed radially outwards in the installed state of the second planet 18a and through the recess is in engagement with the internal teeth of the second ring gear 24.

Due to the described design of the cup-shaped recess, a second planet receiving area 48 is formed in the planet carrier 14a. At least that part of the second planet 18a which is in engagement with the second ring gear 24 is partially accommodated in this. With this construction, both the first planetary bearing pin 54a and the second planetary bearing pin 46 can be attached to the planet carrier 14a from the side of the first ring gear 20, which can facilitate assembly.

A bearing disk 50 is provided on the end side of the second planetary bearing pin 46, which is opposite the second ring gear 24 (the end side facing the first ring gear 20). The bearing disk 50 has first through holes 52 for receiving corresponding end sides of first planetary bearing pins 54a and second through holes 56 for receiving the second planetary bearing pins 46. For example, the bearing bolts are also pressed in here. The bearing disk 50 is, as can be seen for example from FIG. 7, designed as a circular disk with an outer circumference that is smaller than the tip circle diameter of the internal toothing of the first ring gear 20. When installed, the bearing disk 50 is provided radially within the internal teeth of the first ring gear 20.

In this embodiment, the bearing disk 50 serves not only to support the second planetary bearing pins 46 but also to support the ends of the first planetary bearing pins 54a facing the first ring gear 20.

The planets can be rotatably mounted on the bearing pins. Alternatively, the bearing pins can be rotatably mounted on the bearing disk and the planet carrier and rigidly connected or designed to be connected to the planets.

By storing the bearing pins from both end sides, a particularly torsion-resistant construction is created.

The tooth engagement and other constructions are otherwise the same as the first embodiment. In particular, in this embodiment too, the first planet and the second planet mesh radially within the internal toothing of the first ring gear.

Figures 8 to 10 show a planetary differential gear 10b according to a third embodiment. It should be noted that the view of Fig. 8 is rotated 180 degrees about the Z axis compared to the view of Fig. 1, so that therefore the first ring gear 20 in Fig. 5 is the right ring gear. Some reference numbers are indicated in the figures, which are not explained separately in the following description of the embodiment. To explain these reference numbers, reference is made to the description of the first embodiment.

The planetary differential gear 10b according to the third embodiment differs from the planetary differential gear 10 according to the first embodiment in particular in that the structure or construction of the second planet and the planet carrier is modified. The planet carrier 14b according to the second embodiment has, instead of the recesses with which the first bearing shells 36 are formed, further through holes 42 in which bearing areas 34b of the second planets 18b are stored. Also present are the through holes 74 known from the first embodiment for receiving the first planet bearing bolts 54 for the first planets 16.

In the present embodiment, the second planets 18b are preferably supported not only radially but also axially in the through holes 42. For this purpose, the second planets 18b as well as the second planets 18 of the first embodiment have bearing areas 34b whose outer circumference is smaller than the root circle of the toothing areas 28b and 30b of the second planets 18b. In order to enable assembly of the second planets 18b in the through holes 42, the second planets 18b are each made at least in two parts and these at least two parts are connected to one another for assembly of the respective second planet 18b on the planet carrier 14b.

Every second planet 18b is basically constructed like the second planet 18 according to the first embodiment, i.e. has a first toothing area 28b for engagement with the second ring gear 24, a second toothing area 30b for engagement with the first planet 16 radially inside the first ring gear 20 and a bearing area 34b arranged axially between them for storage on the planet carrier 14b. In contrast to the first embodiment, the second planet 18b is not formed in one piece, but rather at least the first or second toothing region 28b, 30b is fastened on a correspondingly designed fastening section 84 of a planetary shaft 40 after the planetary shaft 40 has been passed through the through hole 42.

The attachment is carried out in a known manner, for example by pressing on, shaft-hub connection, etc.

Such a construction offers a simple construction of the planet carrier with a compact design, in particular the bearing component 38 and its fastening are eliminated.

A combination of the embodiments is also possible in such a way that, for example, the second planet of the third embodiment is also used in the first embodiment becomes. It is also possible for the bearing area of the second planet according to the third embodiment to have a larger outer diameter than the tip circle of its first and/second toothing area. In this case, the axial guidance can take place through the ring gears or can be made possible via axial bearings in the through hole.

The drive device and/or the planetary differential are made from known and commonly used materials, for example metal and/or plastics.

The preferred use is in motor vehicles. The planetary differential gear can also be used in other applications, such as in the drives of machines or devices.

It is expressly emphasized that all features disclosed in the description and/or the claims are considered to be separate and independent from each other for the purpose of the original disclosure as well as for the purpose of limiting the claimed invention, regardless of the combinations of features in the embodiments and/or the claims should. It is explicitly stated that all range statements or statements of groups of units disclose every possible intermediate value or subgroup of units for the purpose of the original disclosure as well as for the purpose of limiting the claimed invention, in particular also as a limit of a range statement.

Reference symbol list

10 planetary differential gears

12 input wheel

14 planet carriers

16 first planet

18 second planet

20 first ring gear

22 Internal teeth of the first ring gear

24 second ring gear

26 Internal teeth of the second ring gear

28 first gearing area of the second planet

30 second gear area of the second planet

32 gear area of the first planet

34 storage area

36 first bearing shell

38 bearing component

40 planetary shaft

42 through hole

44 gearing

46 second-planet bearing pins

48 Second Planet Recording Area

50 bearing washer

52 through hole

54 first planet bearing pins

56 through hole

58 first camp

60 sprocket ranges

62 gearing

64 planet carrier areas

66 cases

68 first bearing support flange

70 second camp

72 second bearing support flange Through hole threaded hole through hole mounting section

Claims

Expectations

1. Planetary differential gear (10), with an input wheel (12), which is rotatable about an axis of rotation (R), a planetary carrier (14; 14a; 14b), which is designed as part of the input wheel (12) or is rotationally rigid the axis of rotation (Yl) is connected to the input wheel (12), a first planet (16; 16a), which is mounted on the planet carrier (14; 14a; 14b) in such a way that it can be rotated about a first planetary axis of rotation (PI), which runs parallel to the axis of rotation (R) and rotates around the axis of rotation (Yl) with the rotation of the input wheel (12), a second planet (18; 18a; 18b), which is mounted in this way on the planet carrier (14; 14a; 14b). is that it is rotatable about a second planetary axis of rotation (P2), which runs parallel to the axis of rotation (Yl) and rotates around the axis of rotation (Yl) with the rotation of the input gear (12), a first ring gear (20) with internal teeth ( 22), which is provided in the direction of the rotation axis (Yl) on one side of the planet carrier (14; 14a; 14b) and rotatable about the rotation axis (Yl) and by means of its internal teeth (22) with the first planet (16; 16a) is in engagement, and a second ring gear (24) with internal teeth (26) which is in the direction of the axis of rotation (Yl) on the side of the planet carrier (14; 14a; 14b) opposite the first ring gear (20) and is rotatable about the axis of rotation (Yl) and is in engagement with the second planet (18; 18a; 18b) by means of its internal teeth (26), and a first bearing (58) for supporting, in particular for radially supporting, the input wheel (12 ), in which the second planet (18; 18a; 18b) is in engagement with the first planet (16; 16a) radially within the internal toothing (26) of the first ring gear (20) with respect to the axis of rotation (Yl) and the interventions between the first planet (16; 16a) and the second planet (18; 18a; 18b) and between the first planet (16; 16a) and the first ring gear (20) lie in a common engagement plane, the input gear (12) has a cylindrical one Gear ring area (60), on the outer circumference of which a toothing (62) is provided, and a planet carrier area (64), which Planet carrier (14; 14a; 14b) and is formed radially on the inside of the gear rim region (60), and the first bearing (58) on a first axial side of the planet carrier region (64) has the cylindrical gear rim region (60) from a radial inside supported.

2. Planetary differential gear according to claim 1, further comprising a housing (66), in which the first bearing (58) is a ball or roller bearing, the housing (66) forming a first bearing support flange (68) which forms the first bearing (58) is supported from a radial inside, and the cylindrical ring gear region (60) is supported on its radial inside on the first bearing (58).

3. Planetary differential gear according to claim 1 or 2, which further comprises a second bearing (70) for storage, in particular for radial storage, of the input gear (12), in which the second bearing (70) is on the one with respect to the first Bearing (58) opposite axial side of the planet carrier area (64) supports the cylindrical ring gear area (60) from the radial inside.

4. Planetary differential gear according to claim 3, as far as dependent on claim 2, in which the second bearing (70) is a ball or roller bearing, the housing (66) forms a second bearing support flange (72) which supports the second bearing (70). supported from a radial inside, and the cylindrical gear rim region (60) is supported on its radial inside on the second bearing (70).

5. Planetary differential gear according to claim 4, in which the first bearing and the second bearing support the input wheel in the turned position, preferably in an O-arrangement.

6. Planetary differential gear according to one of claims 1 to 5, in which the tip circle diameter of the first ring gear (20) is larger than the tip circle diameter of the second ring gear (24), and/or the number of teeth of the first ring gear (20) is equal to the number of teeth of the second ring gear (24), and/or the toothing geometry of the second ring gear (24) is obtained by shifting the profile of the tooth geometry of the first ring gear (20).

7. Planetary differential gear according to one of claims 1 to 6, in which the second planet (18; 18b) has a first toothing region (28; 28b) which is designed to engage in the internal toothing (26) of the second ring gear (24), and has a second toothing region (30; 30b) which is designed to engage in the first planet (16).

8. Planetary differential gear according to claim 7, in which the first toothing area (28; 28b) of the second planet (18) and the second toothing area (30; 30b) of the second planet (18) have the same toothing geometry.

9. Planetary differential gear according to claim 7 or 8, in which the first toothing region (28; 28b) of the second planet (18; 18b) has a toothing width which corresponds to a toothing width of the internal toothing (26) of the second ring gear (24), and / or the second toothing area (30; 30b) of the second planet (18; 18b) has a toothing width that corresponds to a toothing width of the first planet (16), and / or the first planet (16; 16a) has a toothing area (32; 32a ) with a toothing width that corresponds to the toothing width of the internal toothing (22) of the first ring gear (20) and / or the toothing area (32a) of the first planet (16a) preferably over its entire width with the toothing of the first ring gear (20). intervention is.

10. Planetary differential gear according to one of claims 7 to 9, in which the second planet (18; 18b) has a bearing area (34; 34b) which is in the direction of the second planetary axis of rotation (P2) between the first toothing area (28; 28b ) of second planet (18; 18b) and the second toothing area (30; 30b) of the second planet (18; 18b), and the second planet (18; 18b) by means of the bearing area (34; 34b) on the planet carrier (14; 14b) is stored.

11. Planetary differential gear according to claim 10, in which the planet carrier (14) forms an open first bearing shell (36) into which the bearing area (34) of the second planet (18) is inserted, and one mounted on the planet carrier (14). Bearing component (38) is provided, by means of which the bearing area (34) of the second planet (18) is mounted in the first bearing shell (36).

12. Planetary differential gear according to claim 10, in which the second planet (18b) has a planetary shaft (40) which forms the bearing area (34b), the planet carrier (14b) has a first through hole (42) for supporting the bearing area (34b) of the second planet (18b), and at least one of the toothing areas (28b, 30b) of the second planet (18b) after inserting the bearing area (34b) of the second planet (18b) into the first through hole (42) on the planetary shaft (40 ) is attached.

13. Planetary differential gear according to claim 8, wherein the second planet (18a) has a continuous toothing (44) in the direction of the second planetary axis of rotation (P2), which includes the first toothing area of the second planet (18a) and the second toothing area of the second Planet (18a) forms.

14. Planetary differential gear according to claim 13, in which the first planet (16a) has a toothing area (32a) with a toothing width which corresponds to the toothing width of the internal toothing (22) of the first ring gear (20), and / or the toothing area (32a ) of the first planet (16a) is preferably in engagement with the teeth of the first ring gear (20) over its entire width.

15. Planetary differential gear according to claim 12 or 14, further comprising a second planetary bearing pin (46) for supporting the second planet (18a), in which the second planetary bearing pin (46) on the planet carrier (14a) so it is provided that it protrudes towards the side of the first ring gear (20) and / or the planet carrier (14a) is at least partially axially between an end of the second planet (18a) facing the second ring gear (24) and the second ring gear (24). extends.

16. Planetary differential gear according to claim 15, in which the planet carrier (14a) has a second planetary receiving area (48) which projects axially towards the second ring gear (24) and on which one towards the first ring gear (20 ) opposite end of the second planetary bearing bolt (46).

17. Planetary differential gear according to claim 15 or 16, further comprising a bearing disk (50) with at least one through hole (52), and an end of the second planetary bearing pin (46) facing the first ring gear (20) in the at least one Through hole (52) is held.

18. Planetary differential gear according to one of claims 1 to 17, further comprising a first planet bearing pin (54; 54a) which is provided on the planet carrier (14; 14a; 14b), in which the first planet (16; 16a) is mounted on the first planet bearing pin (54; 54a) and/or an end of the first planet bearing pin (54; 54a) facing the second ring gear (24) is provided on the planet carrier (14; 14a; 14b). is.

19. Planetary differential gear according to claim 18, as far as referred to in claim 17, in which an end of the first planetary bearing bolt (54) facing the first ring gear (20) is held in a further through hole (56) in the bearing disk (50).

20. Planetary differential gear according to one of claims 1 to 19, in which the second planet (18; 18a; 18b) is not in engagement with the first ring gear (20) and / or the second planet (18; 18a; 18b) only is in engagement with the second ring gear (24) and the first planet (16; 16a), and/or the first planet (16; 16a) only with the first ring gear (20) and the second planet (18; 18a; 18b) is in action.

21. Planetary differential gear (10), with an input wheel (12), which is rotatable about an axis of rotation (R), a planetary carrier (14; 14a; 14b), which is designed as part of the input wheel (12) or is rotationally rigid the axis of rotation (Yl) is connected to the input wheel (12), a first planet (16; 16a), which is mounted on the planet carrier (14; 14a; 14b) in such a way that it can be rotated about a first planetary axis of rotation (PI), which runs parallel to the axis of rotation (R) and rotates around the axis of rotation (Yl) with the rotation of the input wheel (12), a second planet (18; 18a; 18b), which is mounted in this way on the planet carrier (14; 14a; 14b). is that it is rotatable about a second planetary axis of rotation (P2), which runs parallel to the axis of rotation (Yl) and rotates around the axis of rotation (Yl) with the rotation of the input gear (12), a first ring gear (20) with internal teeth ( 22), which is provided in the direction of the rotation axis (Yl) on one side of the planet carrier (14; 14a; 14b) and rotatable about the rotation axis (Yl) and by means of its internal teeth (22) with the first planet (16; 16a) is in engagement, and a second ring gear (24) with internal teeth (26) which is in the direction of the axis of rotation (Yl) on the side of the planet carrier (14; 14a; 14b) opposite the first ring gear (20) and is rotatable about the axis of rotation (Yl) and is in engagement with the second planet (18; 18a; 18b) by means of its internal teeth (26), in which the second planet (18; 18a; 18b) is in relation to the axis of rotation (Yl ) is in engagement radially within the internal toothing (26) of the first ring gear (20) with the first planet (16; 16a) and the engagement between the first planet (16; 16a) and the second planet (18; 18a; 18b) and between the first planet (16; 16a) and the first ring gear (20) lie in a common engagement plane, and the second planet (18a) has a continuous toothing (44) in the direction of the second planetary axis of rotation (P2), which forms the first toothing area of the second planet (18a) and the second toothing area of the second planet (18a).

22. Planetary differential gear according to claim 21, in which the first planet (16a) has a toothing area (32a) with a toothing width which corresponds to the toothing width of the internal toothing (22) of the first ring gear (20), and / or the toothing area (32a ) of the first planet (16a) is preferably in engagement with the teeth of the first ring gear (20) over its entire width.

23. Planetary differential gear according to claim 21 or 22, further comprising a second planetary bearing pin (46) for supporting the second planet (18a), in which the second planetary bearing pin (46) on the planet carrier (14a) so it is provided that it protrudes towards the side of the first ring gear (20) and / or the planet carrier (14a) is at least partially axially between an end of the second planet (18a) facing the second ring gear (24) and the second ring gear (24). extends.

24. Planetary differential gear according to claim 23, in which the planet carrier (14a) has a second planetary receiving area (48) which projects axially towards the second ring gear (24) and on which a first ring gear (20 ) opposite end of the second planetary bearing bolt (46).

25. Planetary differential gear according to claim 23 or 24, further comprising a bearing disk (50) with at least one through hole (52), and an end of the second planetary bearing pin (46) facing the first ring gear (20) in the at least one Through hole (52) is held.

26. Planetary differential gear (10), with an input wheel (12), which is rotatable about an axis of rotation (R), a planetary carrier (14; 14a; 14b), which is designed as part of the input wheel (12) or is rotationally rigid the axis of rotation (Yl) is connected to the input wheel (12), a first planet (16; 16a), which is mounted on the planet carrier (14; 14a; 14b) in such a way that it can be rotated about a first planetary axis of rotation (PI), which runs parallel to the axis of rotation (R) and with the rotation of the Input wheel (12) rotates around the axis of rotation (Yl), a second planet (18; 18a; 18b), which is mounted on the planet carrier (14; 14a; 14b) in such a way that it can be rotated about a second planetary axis of rotation (P2), which runs parallel to the axis of rotation (Yl) and rotates around the axis of rotation (Yl) with the rotation of the input wheel (12), a first ring gear (20) with internal teeth (22) which is in the direction of the axis of rotation (Yl) on a Side of the planet carrier (14; 14a; 14b) and rotatable about the axis of rotation (Yl) and is in engagement with the first planet (16; 16a) by means of its internal teeth (22), and a second ring gear (24) with internal teeth (26), which is in the direction of the axis of rotation (Yl) on the side of the planet carrier (14; 14a; 14b) and is rotatable about the axis of rotation (Yl) and is in engagement with the second planet (18; 18a; 18b) by means of its internal teeth (26), in which the second planet (18; 18a; 18b) is in relation to the Axis of rotation (Yl) is in engagement radially within the internal teeth (26) of the first ring gear (20) with the first planet (16; 16a) and the engagement between the first planet (16; 16a) and the second planet (18; 18a; 18b) and between the first planet (16; 16a) and the first ring gear (20) lie in a common engagement plane, the planet carrier (14) forms an open first bearing shell (36) into which the bearing area (34) of the second planet ( 18) is used, and a bearing component (38) mounted on the planet carrier (14) is provided, by means of which the bearing area (34) of the second planet (18) is mounted in the first bearing shell (36).

27. Drive device for motor vehicles with a planetary differential gear according to one of claims 1 to 26, in which the input wheel (12) is designed to be driven by a drive machine, and each of the ring gears (20, 24) is designed as an output gear to be connected in a torsionally rigid manner to an axle shaft.