COMBINED FRICTION BEARING IN A PLANETARY DRIVE

Abstract

The invention relates to a planetary gearbox comprising at least one sun gear (17, 18) and at least one planet carrier (5) arranged coaxially with and rotatably in relation to said gear, a combination of a bearing sleeve (40) and a slide ring (41) that is separate therefrom being located between the sun gear (17, 18) and the planet carrier (5). The invention also relates to a gearbox combination of a differential of the spur-gear differential type, in the form of which the planetary gearbox is configured, and an additional planetary stage, the spur-gear differential and the planetary stage preferably having a common planet carrier (5) composed of multiple planet sub-carriers (6, 7, 8) that are non-rotatably combined.

Description

CROSS-REFERENCE TO RELATED APPLICATIONS

The present application is the U.S. national stage application pursuant to 35 U.S.C. §371 of International Application No. PCT/EP2013/056653, filed Mar. 28, 2013, which application claims priority from German Patent Application Nos. DE 10 2012 208 799.0, filed May 25, 2012, and DE 10 2012 208 805.9, filed May 25, 2012, 25, 2012, which applications are incorporated herein by reference in their entireties.

TECHNICAL FIELD

The present disclosure relates generally to a planetary drive with at least one sun gear and at least one coaxially arranged planetary carrier arranged rotationally thereat.

BACKGROUND

An example of a known planetary drive is shown in German Patent Application No. DE 10 2009 032 286 A1. The disclosed planetary drive has two sun gears with each sun gear engaging a set of planetary gears, which are supported by a planetary carrier. The sun gears are radially centered by the force of gears during operation when the planetary gears are engaged. Unfortunately, the centering of the sun gears during the unloaded state is not sufficiently ensured, if ensured at all. Without sufficient centering, the sun gears can become displaced far away from the central radial position. Additionally, imbalances can develop at the sun gears during operation, despite the applied gear forces. Furthermore, misalignments are possible between the sun gear and the planetary carrier. This leads to increased wear and tear and increased noise development. These problems apply even more when strong forces are transferred between the planetary gears and the sun gears, such as is transferred in a differential.

Examples of typical transmission combinations are shown in German Patent Application No. DE 10 2008 027 992 A1. A drive device for transverse installation into motor vehicles with all-wheel drive is disclosed. The drive device is provided for transverse installation, in which the axial differential and an interim axial differential are structurally combined in one transmission housing. The differentials are spur gears, showing a first bar as an input element of the interim axial differential, which drives the sun wheel as one output element, and, via an exterior wheel the axial differential as the other output element, with the exterior wheel via the bar of the axial differential and its planetary gears driving the output elements towards the axial shafts. This publication teaches that the two differentials are embodied with regard to transmission technology such that they show a common bar. A spur differential and a planetary gear as the transmission stage are thus combined. Unfortunately, torque is deducted via the superimposed stage from a front axle to a rear axle differential of the motor vehicle in this publication.

A typical planetary gear is disclosed in U.S. Pat. No. 4,574,658, in which a planetary gear is combined with a superposed spur gear stage. A sun gear of the planetary gear is driven via an additional spur gear section by a sprocket separated from the planetary gear.

German Patent No. DE 2031654 A1 and United Kingdom Patent No. GB 1212630 A disclose transmission combinations in which different transmission stages are connected to each other. In particular, among other things, a non-rotatable connection is disclosed. The non-rotatable connection shows a transmission stage with two cooperating transmission elements, each respectively showing an annular element, which comprises an axially extending cylindrical projection and which forms a non-rotatable coupling together with the annular element of the other transmission element. The annular elements are made from sheet metal and show tooth-like indentations extending axially, which engage each other like partial gearing.

Certain parts of planetary carriers can be welded to each other, as is described in German Patent Application Nos. DE 103 33 880 A1 and DE 103 33 879 A1.

A typical transfer gearbox for a motor vehicle is disclosed in German Patent Application No. DE 10 2007 017 185 B4. The described transfer gearbox comprises a driven differential, which drives two shafts via compensation elements, with the possibility that the driven moment at the driven shafts can be changed by a drive engine, formed by a planetary gear, drivingly connected to the driven shafts directly or indirectly via superimposed transmissions. The conversion of the superimposed transmission is designed such that, during synchronized operation of the driven shafts, the driving engine is stationary. This publication suggests positioning one planetary gear upstream relative to the superimposed transmission for it to cooperate with the differential and reduce the moment. Positioning a planetary gear as such is described as improving the redistribution with respect to precision, and providing a more rapid reaction with respect to the driven moments.

Unfortunately, typical planetary gears and transmission combinations comprise a large number of components and require an abundance of structural space. The production of typical planetary gears and transmission combinations thus leads to relatively high costs and the assembly is relatively expensive.

SUMMARY

According to aspects illustrated herein, there is provided a planetary drive, comprising a sun gear; a planetary carrier operatively arranged coaxially and rotatably with respect to the sun gear; and, a support component located radially between the sun gear and the planetary carrier, the support component comprising a bearing sheath and a gliding ring.

According to aspects illustrated herein, there is provided a transmission combination comprising a differential gear embodied as a spur differential, and an additional planetary stage, with the spur differential and the planetary stage having a common planetary carrier assembled in non-rotatably with respect to several partial planetary carriers.

According to aspects illustrated herein, there is provided a planetary drive having a combination of a bearing sheath and a gliding ring, separated therefrom, located between the sun gear and the planetary carrier. This allows the wear and tear to be considerably reduced. Tolerances can be particularly well compensated, here, when the gliding ring shows an elastic section, allowing a deformation in its diameter.

An objective of the present disclosure is to avoid the disadvantages of the prior art and to allow a better spatial utilization with lower costs and a simpler assembly. Further, the resistance to wear and tear shall be improved.

It is also advantageous for the elastic section to be embodied by an elastic bar, formed at the gliding ring by one or more recesses. The gliding ring can then be arranged with little radial pre-stressing between the sun gear and the planetary carrier. This way, the sun gear can be precisely centered and the axial distances between it and the planetary gears can be precisely predetermined.

A gliding ring, variably adjustable with regards to its elastic effect, can be used in a particularly cost-effective fashion when the bar shows the form “Z”, i.e., is Z-shaped, with right angles in the circumferential direction. Here, the recesses develop, which are advantageous for the distribution of lubricant and the flow through at the gliding ring. In particular when the gliding ring is stationary these recesses serve as a reservoir for lubricant, in which said lubricant can collect in order to be redistributed during operation, particularly at the gliding area. This leads to a homogenous distribution of the lubricant.

The assembly can be facilitated when the gliding ring is inserted in the bearing sheath like a latching spring.

The costs can also be kept low during production, when the bearing sheath is produced from sheet metal and preferably surrounds, e.g., circumscribes, the gliding ring.

When the gliding ring is located between two bulges of the bearing sheath extending radially inwardly, here an axial fixation of the gliding ring can be realized in reference to the bearing sheath, which is beneficial for the functionality.

The present disclosure also relates to a transmission combination comprising a differential gear like a spur differential, as explained above, and an additional planetary stage, with the spur differential and the planetary stage preferably showing a common planetary carrier assembled in a non-rotatable fashion from several partial planetary carriers.

It is further advantageous for the surface area in the proximity of the hole for a planetary bolt to be post-processed in a cutting fashion, preferably milled.

It has also shown to be particularly space-saving when the differential gear is embodied as a spur gear differential, which shows several planetary gears engaging each other, with respectively a first planetary gear engaging a first sun gear and the other, second planetary gear engaging the second sun gear, with both planetary gears and two partial planetary carriers of the planetary carrier being supported in a rotational fashion and/or the first planetary gear showing a greater axial length than the second planetary gear. Particularly in an embodiment of the planetary gears with different lengths, here a very compact design can be realized.

When the planetary gear is supported on bolts, which rest in at least two partial planetary carriers, preferably via hardened sheaths, here an expensive hardening of the bolts can be waived and more cost-effective bolts can be used. The sheaths formed from sheet metal may be hardened in a cost-effective fashion before they are installed.

When a bolt embodied as a connecting bolt is located in the two exterior partial planetary carriers, which preferably supports on one side a planetary gear of the spur differential and on the other side a planetary gear of the planetary stage, here the number of bolts can be reduced, which in turn is beneficial for the assembly.

It is further beneficial for the connecting bolts to be guided through the hole, which is surrounded by the surface area post-processed by way of milling, which forms a contact area for a disk, preferably embodied in a hardened fashioned, with which the disk can be made to contact a planetary gear of the planetary stage. The construction space can then be used particularly efficiently and any wear and tear can be reduced which occurs when a planetary gear of the superimposed stage comes into contact with the central partial planetary carrier.

It is also beneficial when the bolt embodied as a carrying bolt is arranged in the central partial planetary carrier and the exterior partial planetary carrier, distanced from the added planetary stage, in a recess embodied preferably as a penetrating hole. While the narrower of the two planetary gears on the spur differential and one planetary wheel of the additional planetary stage are arranged on the connecting bolt, the wider of the two planetary gears of a set of planetary gears of the spur differential can be supported exclusively on the supporting bold and thus an advantageous distribution of forces can be yielded.

An advantageous exemplary embodiment is also characterized in that the penetrating hole is surrounded by a bead extending axially in the direction of the additional planetary stage. The forces developing during the operation of the transmission combination can then be compensated in a particularly effective fashion.

In order to prevent that any interaction of the planetary gear of the additional planetary stage can occur upon the bead it is advantageous for the bead, completely surrounding the penetrating hole, to be distanced from the post-processed surface area of the neighboring hole, preferably distanced by more than one tenth or one fifth of the diameter of the penetrating hole.

It is also beneficial for a radially projecting gearing to be embodied at the exterior of the planetary carrier.

Further, it is advantageous for the gearing to be embodied as an exterior gearing on one of the partial planetary carriers and/or the exterior gearing to be embodied as a helical gearing or as spur gearing, preferably as parking-lock gearing. Particularly when the exterior gearing is embodied as parking-lock gearing, a linking locking element, such as a parking brake, can engage the exterior gearing and completely block the transmission so that any moving of the motor vehicle, in which the transmission combination and/or the planetary gear is used, is no longer possible. In many countries particularly such a parking-lock gearing is necessary to fulfill statutory stipulations. Such a parking-lock gearing shall be embodied such that the counterpart of the parking-lock gearing, for example a parking-lock provided with links, can engage the parking-lock gearing in a preferably locking fashion at 6 km/h and cannot engage at higher speeds, in a particular exemplary embodiment. When a helical gearing is provided, a driving moment can also be applied upon the planetary carrier. In general, however, the spur gearing is preferred, particularly in an embodiment as a parking-lock gearing.

It is also advantageous when a planetary carrier embodied from several parts comprises three or more partial planetary carriers. This way the assembly can be simplified.

It is also beneficial for a central partial planetary carrier, arranged between two exterior partial planetary carriers, to show an exterior gearing. Any symmetric distribution of forces and torque can then easily be realized.

The lifespan is extended if the partial planetary carrier showing an exterior gearing is embodied massive, as a cast part, or as a forged part. In such a case the parking-lock gearing can be easily integrated, for example by a cutting process. An alternative to such a partial planetary carrier produced from sheet metal is also possible.

It is also possible for the second planetary gear to be supported via a bolt, which extends from one exterior partial planetary carrier through the partial planetary carrier comprising the exterior gearing to the other exterior partial planetary carrier. The non-rotatable connection is here improved and the assembly is simplified.

It is also advantageous when two of the partial planetary carriers, with preferably one of the partial planetary carriers being provided with exterior gearing, form a housing for at least the differential gear or the entire transmission combination.

The capacity of the transmission combination can also be increased when a central partial planetary carrier located between the two exterior partial planetary carriers shows a curved shaped bar, inserted in a hole of one of the two exterior partial planetary carriers, embodied in a matching fashion.

It is also beneficial for the section of the bar inserted in the hole to be processed sectionally in a cutting fashion, preferably at the interior and the exterior.

The stability is here increased particularly when the exterior partial planetary carrier showing the hole is welded to the partially planetary carrier showing the bar, in the area of said bar.

The production can be implemented in a particularly cost-effective fashion when the partial planetary carrier comprising the hole is embodied as a sheet metal part, preferably as an annular partial planetary carrier plate.

Particularly when the partial planetary carrier plate shows holes, embodied as slots and distanced from each other with identical angles, the respective introduction of force can be embodied symmetrically, preventing any imbalances and extending the life span.

Here, it is advantageous for the partial planetary carrier plate to be a part of the additional planetary stage.

It is also advantageous for the central partial planetary carrier to be riveted to an exterior partial planetary carrier, preferably representing a part of the differential gear, with further preferred always two rivets each being located in one of several recesses, with the recesses being provided at the side of the central partial planetary carrier, facing the partial planetary carrier showing the hole. The stability of the transmission combination increases, and utilization with less maintenance can be realized.

Further it is advantageous when three bag-like recesses are provided at the central partial planetary carrier and at the exterior partial planetary carrier connected thereto, in which two rivets each are located axially without projecting.

Further it is advantageous when a bearing sheath is inserted between at least one sun gear and one planetary carrier such that it axially and/or radially impacts the sun gear, supporting it in reference to the planetary carrier.

Particularly when the bearing sheath is inserted in an exterior partial planetary carrier, which represents a part of the differential gear, for the axial and/or radial positioning of a spur gear, such as a sun gear, the wear and tear is reduced.

When the bearing sheath shows at least one radial and/or axial bulging here the sun gear can be precisely positioned in reference to one of the exterior partial planetary carriers.

Here it is advantageous when the bearing sheath configured as a sheet metal part is inserted radially in the exterior partial planetary carrier in a force-fitting fashion, preferably impressed. The bearing sheath is then mounted in a consistent position in the exterior partial planetary carrier, which has reducing effects upon the play.

In order to increase the life span it is advantageous for the bulging to be embodied hardened at least sectionally, with the bearing sheath preferably further showing elastic spring features at least in partial sections.

It is also beneficial for the bulging of the bearing sheath to be provided with a first hardened section, extending axially in the direction of the two sun gears, and/or with a second hardened section, which extends radially inwardly, and/or a third hardened section is provided at the bearing sheath, which is axially distanced from the second hardened section and is located at the side of the second hardened section distanced from the sun gear. When a third hardened section is provided, the safety from the sun gear tipping is increased, with the first and the second hardened section on the one side performing an axial securing function and on the other side a radially securing function.

This tipping safety of the bearing sheath in turn is improved when the bearing sheath shows a support section extending from the bulging radially towards the outside, which contacts the exterior partial planetary carrier.

When one planetary gear each of a pair of planetary gears is shorter than the other planetary gear of said pair and preferably a friction disk is arranged between the sun gears, a particularly compact embodiment of the device develops and the desired blocking effect can be adjusted.

Planetary carriers made from thick sheet metal lead to relatively large deformation radii. The leading portion of the sun gears is thereby reduced. For compensation, here only one torque angle gauge with a bulging bead is provided, which allows greater support width. Additionally, the disk is hardened, and therefore shows better wear and tear features.

The present disclosure also relates to a drive train of a motor vehicle, such as a passenger vehicle, a truck, or a tractor, comprising a transmission combination according to the present disclosure as explained above.

BRIEF DESCRIPTION OF THE DRAWINGS

Various embodiments are disclosed, by way of example only, with reference to the accompanying schematic drawings in which corresponding reference symbols indicate corresponding parts, in which:

FIG. 1 is a perspective view of a transmission combination according to the invention from the side of a differential gear;

FIG. 2 is a perspective view of the transmission combination of FIG. 1 from the side of an additional planetary stage;

FIG. 3 is a central partial planetary carrier as installed in the transmission combination of FIGS. 1 and 2, in a perspective view from the side of the differential gear;

FIG. 4 is the central partial planetary carrier of FIG. 3 in a perspective view from the side of the additional planetary stage;

FIG. 5 is a longitudinal cross-section through the transmission combination of the exemplary embodiments of FIGS. 1 and 2;

FIG. 6 is an enlarged illustration of the connection area between two partial planetary carriers in the area of the differential gear of the transmission combination of FIG. 5;

FIG. 7 is a longitudinal cross-section through a transmission combination as illustrated in FIGS. 1, 2, and 5, in a level, in which a narrow planetary gear of the differential gear and a planetary gear of the additional planetary stage are located;

FIG. 8 is a perspective, partially cross-sectioned illustration of the transmission combination of FIG. 7;

FIG. 9 is a longitudinal cross-section of the transmission combination shown in FIGS. 1, 2, 5, and 7, however in a level in which only one wide planetary gear of the differential gear is located;

FIG. 10 is a partially cross-sectioned, perspective illustration of the transmission combination of FIG. 9;

FIG. 11 is a view from the differential gear side to the transmission combination as shown in FIGS. 1, 2, 5, and 7 to 10;

FIG. 12 is a transmission combination of FIG. 11 in a view from the side;

FIG. 13 is a view of the transmission combination of FIG. 11 from the side of the additional planetary stage;

FIG. 14 is an exploded illustration of the transmission combination of FIGS. 1, 2, 5, and 7 to 13;

FIG. 15 is a longitudinal cross-section of a part of the transmission combination with a bearing sheath located between a sun gear and an exterior partial planetary carrier;

FIG. 16 is an enlarged illustration of an area in which the bearing sheath of the exemplary embodiment is located according to FIG. 15;

FIG. 17 is another enlarged illustration of the section of the transmission combination, in which the bearing sheath is located;

FIG. 18 is a perspective illustration of a variant of a bearing sheath for the transmission combination of FIG. 1;

FIG. 19 is a perspective illustration of a variant of a bearing sheath for the transmission combination of FIG. 1;

FIG. 20 is a cross-section through a part of the transmission combination with an installed alternative bearing sheath;

FIG. 21 is an enlarged illustration of a cross-sectioned alternative bearing sheath of the exemplary embodiments as inserted in FIGS. 18 to 20;

FIG. 22 is a perspective illustration of a variant of a transmission combination according to the invention with an installed bearing sheath;

FIG. 23 is a cross-sectional illustration through a variant of a transmission combination in the area of a bearing sheath between one of the sun gears and the exterior partial planetary carrier, with additionally a gliding ring being located between the bearing sheath and an axial flange area of the sun gear;

FIG. 24 is a perspective illustration of the gliding ring only, as used in the exemplary embodiment according to FIG. 23;

FIG. 25 is a cross-sectional illustration of the gliding ring of FIG. 24 installed in a bearing sheath;

FIG. 26 is a perspective illustration of the bearing sheath and the gliding ring only; and,

FIG. 27 is a longitudinal cross-section of the gliding ring of FIG. 24.

The figures are only of a schematic nature and merely serve for understanding the invention.

DETAILED DESCRIPTION

At the outset, it should be appreciated that like drawing numbers on different drawing views identify identical, or functionally similar, structural elements of the disclosure. It is to be understood that the disclosure as claimed is not limited to the disclosed aspects.

Furthermore, it is understood that this invention is not limited to the particular methodology, materials and modifications described and as such may, of course, vary. It is also understood that the terminology used herein is for the purpose of describing particular aspects only, and is not intended to limit the scope of the present disclosure.

Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood to one of ordinary skill in the art to which this invention belongs. It should be understood that any methods, devices or materials similar or equivalent to those described herein can be used in the practice or testing of the disclosure.

By “non-rotatably connected” first and second components we mean that the first component is connected to the second component so that any time the first component rotates, the second component rotates with the first component, and any time the second component rotates, the first component rotates with the second component. Axial displacement between the first and second components is possible.

Referring now to the Figures, FIG. 1 shows transmission combination 1. Transmission combination 1 shows a section, which is differential gear 2 in an embodiment. An additional section of transmission combination 1 is embodied as planetary stage 3 complementing differential gear 2. Differential gear 2 is embodied as a planetary gear, particularly as spur differential 4.

Transmission combination 1 comprises planetary carrier 5, with exterior partial planetary carrier 6 being discernible, located in FIG. 1 on the side of the differential gear. Another exterior partial planetary carrier 7, which is a part of additional planetary stage 3, though, is particularly clearly discernible in FIG. 2, in which the side of the planetary stage 3 is located in the foreground.

Central partial planetary carrier 8 is provided between exterior partial planetary carrier 6 and exterior partial planetary carrier 7. Planetary carrier 8 ultimately represents both differential gear 2 as well as planetary stage 3.

Exterior partial planetary carriers 6 and 7, and central partial planetary carrier 8 are connected to each other to form planetary carrier 5. Each of carriers 6, 7, and 8 are secured to each other such that they are non-rotatable with respect to each other.

At the exterior of planetary carrier 5, namely embodied at central partial planetary carrier 8, radially projecting gearing 10 is embodied on exterior 9 of planetary carrier 5 in the area of the largest diameter. In an embodiment, gearing 10 is spur-geared like a parking-lock gearing. In an embodiment, central partial planetary carrier 8 is a cast part or a forged part and is a massive part, which unlike exterior partial planetary carrier 7 of planetary stage 3, is not embodied as a sheet metal part, but as a part formed by post-processing using cutting processes.

A parking-lock engages gears 10 in the blocking state of transmission combination 1. This parking-lock is not shown. Exterior partial planetary carrier 6 of differential gear 2 is connected with rivets 11 to central partial planetary carrier 8. Here, recesses 12 are provided in the two partial planetary carriers 6 and 8, in which two rivets 11 each are arranged, thereby securing partial planetary carrier 6 non-rotatably with respect to partial planetary carrier 8.

In an embodiment, differential transmission 2 is a spur differential, which shows several planetary gear pairs 13 at planetary gears 14 and 15. First planetary gear 14, contrary to second planetary gear 15, shows a greater axial length. The axial length is measured along the rotary axis of transmission combination 1. The different axial length of the two planetary gears 14 and 15 is clearly discernible in FIG. 14, among other things.

In FIG. 5, from planetary gears 14 (shown in FIG. 9) and 15 of differential gear part 2, only second planetary gear 15 as well as two additional planetary gears 16 of the additional planetary stage 3 are discernible between central partial planetary carrier 8 and exterior partial planetary carrier 7 of planetary stage 3. FIG. 5 also shows the presence of two sun gears 17 and 18, with sun gear 17 engaging first planetary gear 14, and sun gear 18 engaging second planetary gear 15. Planetary gears 14 and 15, which make up planetary gear pair 13 (shown in FIG. 14) of differential transmission part 2, may also engage simultaneously.

Second planetary gear 15 is also supported on bolt 19. Bolt 19 is also called connecting bolt 20. Connecting bolt 20 is located in hardened sheaths 21 in exterior partial planetary carriers 6 and 7. Sheaths 21 also show radially projecting flanges 22, which can be made to contact the respective planetary gears 15 and 16.

Hardened disk 23 is also provided at a radially interior end of central partial planetary gear 8, which can be made to contact sun gear 17.

Sun gears 17 and 18 each have an interior gearing, which enables by which the elements for torque transmission can be brought into engagement with the wheels of a motor vehicle. Friction disk 24 is provided between sun gears 17 and 18. Friction disk 24 can also be called a friction ring.

Connecting bolt 20 may also show a longitudinal bore, which is connected to lateral bores, so that lubricant can be brought into an area between connecting bolt 20 and planetary gear 16. This way e.g., oil can be supplied and the friction can be reduced.

With regards to planetary stage 3, embodied as a load stage, the respective hollow gear and sun gear embodiments are not shown. For example, the sun gear is usually embodied as a part connected to a hollow shaft. The hollow wheel in turn may also show a gearing at the exterior or may be rippled up with a geared flange part.

As clearly discernible from FIG. 5, disk 25 is located between planetary gear 16 and central partial planetary carrier 8, which can also be called a contact disk, preventing the wear and tear of central partial planetary carrier 8, which otherwise would develop upon planetary gear 16 contacting central partial planetary carrier 8 during rotation. Accordingly, disk 25 acts in a supporting fashion similar to radially projecting flanges 22 of sheath 21. Disk 25 can be hardened, similar to sheath 21.

Planetary gear 5 forms the housing of transmission combination 1 and could in its entirety also be called the bar.

However, here a bar is understood as an axial extension of central partial planetary carrier 8 and is marked with reference character 26.

As particularly clearly discernible in FIGS. 2 and 5, here axial end 27, which is preferably post-processed in a cutting fashion by way of milling on its radial inside 28 and its radial outside 29, projects without play into hole 30 of exterior partial planetary carrier 7 embodied as a plate. Exterior planetary carrier 7 may also be called a partial planetary carrier plate, just as it here per se forms a planetary carrier plate.

Bar 26 is welded to this partial planetary carrier plate and/or to exterior partial planetary carrier 7. Here, an induction welding method is beneficial.

Although by the welded connection between exterior partial planetary carrier 7 and central partial planetary carrier strong forces can be transferred on the one side, on the other side central partial planetary carriers 8 can also transfer strong forces upon exterior partial planetary carrier 6, because a compact rivet form of rivet 11 is possible due to recess 12. Rivet 11 and, accordingly, recess 12 are always allocated to bar 26. Recess 12 is therefore arranged radially outside bar 26, which has positive effects upon the ability to transfer forces.

While in FIGS. 1 and 2, assembled transmission combination 1 is in the foreground, in FIGS. 3 and 4, only central partial planetary carrier 8 is in the foreground. Here, material recesses 32 are provided at side 31 of central partial planetary carrier 8 facing exterior partial planetary carrier 6, in order to accept first planetary gears 14. Material recesses 32, here, convert to holes 33 and 34, which are embodied as penetrating openings. Here, holes 33 and 34 are provided in order to accept bolts 19.

Here, connecting bolt 20 is inserted into hole 33, with support bolt 35 being inserted into hole 34. Support bolt 35 is a special embodiment of bolt 19 and carries only planetary gear 14. At the other side, as shown in FIG. 4, thus the side of additional planetary stage 3, hole 35 is surrounded by bead 36.

Hole 33 is surrounded by surface area 37 arranged concentric in reference thereto. In reference to surface 38 of central partial planetary carrier 8, surface area 37 is axially offset in the direction of exterior partial planetary carrier 7. This off-setting is ensured by a cutting processing, particularly by a milling process. Here, in general polishing and lapping methods are possible, too.

In transmission combination 1, three recesses 12 are each provided with two rivets 11, three bars 26, three holes 33, and three holes 34. These parts are evenly distributed in reference to a rotary axis of transmission combination 1, not shown. However, holes 33 and 34 are not located on the same pitch diameter. It shall also be pointed out that the outside diameter of sun gears 17 and 18 are different. The outside diameter of the small sun gear is here smaller than the foot circular diameter of the large sun gear. This is caused by the small sun gear being 20% smaller than the large sun gear. In the traction mode the smaller planetary gear of pair 13 travels ahead of the large planetary gear. By the solution according to the invention, the noise emission is also reduced. Any problems arising with respect to the support width are also reduced. Even locking values up to 30% can be realized without major problems developing. This way, a so-called torsion differential can be generated.

Bead 36 is distanced from surface area 37, processed in a cutting fashion, by one-seventh of the diameter of hole 34. Hole 33 may also be embodied as a blind hole.

As clearly discernible in FIG. 4, bar 26 is curved in the circumferential direction. The section of bar 26 formed by axial end 27 is post-processed in a cutting fashion.

With reference to FIG. 13, the matching curved embodiment of hole 30 is shown in exterior partial planetary carrier 7. Here, hole 30 extends in the circumferential direction further than bar 26 so that, seen in the circumferential direction, cavities 39 develop at both sides of bar 36. Holes 30 are embodied as circumferentially displaced slots, each having the same length in the circumferential direction. However, it is also possible that one of the slots is embodied longer than the other one.

In general, it is also possible that exterior partial planetary carrier part 7, in the exemplary embodiment shown here embodied as a sheet metal part, is not embodied as an annular partial planetary carrier plate but is also produced as a cast or forged part.

While in FIGS. 1-5 particularly also the gears 10 are discernible on the exterior of central partial planetary carrier 8, in FIG. 6 only the short embodiment of the rivets 11 is discernible, as inserted in the recesses 12 in order to secure central partial planetary carrier 8 in a non-rotable manner with respect to exterior partial planetary carrier 6.

As visualized in FIGS. 5 and 7, bearing sheath 40 is provided between sun gear 18 and exterior partial planetary carrier 6. Bearing sheath 40 is also used in the exemplary embodiment according to FIG. 9. However, in the exemplary embodiment according to FIG. 15, a modified form of bearing sheath 40 is used. Bearing sheath 40 shown here is also used in the exemplary embodiment according to FIG. 16. This second embodiment of bearing sheath 40 is axially longer than bearing sheath 40 of the exemplary embodiments of FIGS. 7 and 9. The shorter bearing sheath here is also used in the exemplary embodiment of FIGS. 17 to 22, while the longer variant of bearing sheath 40 in turn is used in the exemplary embodiments of FIGS. 23, 25, and 26.

Gliding ring 41 is also used with the longer variant of bearing sheath 40, as shown in the exemplary embodiment according to FIGS. 23 to 27. Together, bearing sheath 40 and gliding ring 41 form a support component.

Before bearing sheath 40 and gliding ring 41 are discussed in greater detail it shall be pointed out that FIGS. 7 and 8 show the support of planetary gear 16 and second planetary gear 15 on the very same bolt 19, namely connecting bolt 20. However, an illustration is selected in FIGS. 9 and 10, which discloses the bearing of support bolt 35. Here, support pin 35 only carries the first planetary gear 14. The entire assembly of transmission combination 1 can be particularly clearly seen in the completely assembled version of FIGS. 11 to 13. The adaptation of axial ends 27 of bars 26 in the respectively shaped holes 30 is here also clearly discernible.

In the exemplary embodiment shown in FIG. 14, sheaths 21 are already assembled in exterior partial planetary carrier 6, exterior partial planetary carrier 7, and central partial planetary carrier 8. The different axial length of connecting bolts 20 in reference to support bolt 35 is such that support bolt 35 is approximately half the length of connecting bolts 20. In order to support the individual planetary gears 15 and 16 here the use of hardened disks 23 and rings 42 is also beneficial, with rings 42 also potentially being hardened.

Bearing sheath 40, as shown in FIGS. 15 and 17, is embodied such that it acts axially and radially supporting sun gear 18 and holds it axially and radially distanced from exterior planetary carrier 6. For this purpose the bearing sheath 40 shows at least one bulging 43, which is located between support area 44, radially projecting outwardly, and an axially aligned contact area 45. Bearing sheath 40 is located in contact area 45 in a compressed connection with exterior partial planetary carrier 6.

Bulging 43 shows first hardened section 46, which extends in the axial direction, as well as second hardened section 47, arranged at a right angle in reference thereto, which extends in the radial direction.

Distanced from first hardened section 46 by the axially aligned contact area 45, third hardened section 48 is given in the area of securing section 49, extending in the axial direction and radially off-set inwardly.

For shaping hardened sections 46, 47, 48 an induction curing method is recommended. However, carburization is also possible, in general.

As shown in FIG. 16, in the area of the bulging 43 and the securing section 49 two axially distanced radial bearing sections of the bearing sheath 40 are formed in reference to the sun gear 18. Additionally, an axial bearing section is formed. The bearing sheath 40 can show at least sectionally elastic features in order to compensate tolerances and damp any perhaps occurring impacts.

In the installed state no play is given between the axial contact area 45 and the exterior partial planetary carrier 6, while play is still given between the first hardened section 46 of the bulging 43 and a flange section of the sun gear 18 extending in the axial direction, similarly as between the first hardened section 47 and a section of the sun gear 18 extending in the radial direction. The bulging 43 may follow the exterior contour of the sun gear 18 also in a 90°-angled section and show a distance as low as possible.

The variant of the bearing sheath 40 of FIGS. 18 to 22 shows a shorter axial length than the exemplary embodiment according to FIG. 16. The shortest diameter of the bearing sheath 40 ranges from 43 to 45 mm, preferably amounts to 44 mm. The exterior diameter in the area of the axially aligned contact area 45 amounts to approximately 10% more, preferably 47.9 mm. The entire exterior diameter at the largest place shows a value of 68 mm. It is also advantageous if the exterior diameter at the largest point is greater by one third than the interior diameter at the smallest point of the bearing sheath 40. Further it is advantageous when the axial length amounts to more than one fourth of the interior diameter but less than half the interior diameter, preferably showing 16 mm. The bearing sheath of FIG. 21 is also provided with a homogenously thick wall.

In FIG. 22 the bearing sheath 40 of FIG. 21 is installed in the transmission combination 1.

The gliding ring 41 shown singularly in FIGS. 24 and 27 is installed in the exemplary embodiments of FIGS. 23, 25, and 26.

The arrangement of the gliding ring 41 radially inside the bearing sheath 40, namely axially between the bulging 43 and the axially aligned contact section 45, is particularly clearly discernible from FIGS. 23, 25, and 26.

Gliding ring 41 shows recesses 50 such that elastic bars 51 form, which can also be called spring bars. Recesses 50 can be embodied like labyrinths. In an exemplary embodiment, elastic bars 51 are Z-shaped. One recess 50 each is aligned from one axial side to the other axial side, with one recess each beginning at one side and the other recess 50 beginning at the other side so that a “Z” is embodied with a right angle. Gliding ring 41 is produced from plastic. Z-shaped bars 51 are evenly distributed over the circumference. In general, it is also possible that bearing sheath 40 is made from materials other than spring steel, particularly other types of sheet metal. Plastic gliding ring 41 can latch in the extension given between contact area 45 and securing section 49. This radially inwardly off-set securing section 49 can also be called a bulging.

The five bars 51 allow a change of the diameter of gliding ring 41. Thickness 52 of gliding ring 41 is greater than the width of recess 50 measured in the circumferential direction, as also discernible from FIG. 27.

LIST OF REFERENCE NUMBERS

• 1 Transmission combination
• 2 Differential gear
• 3 Planetary stage
• 4 Spur differential
• 5 Planetary carrier
• 6 Exterior partial planetary carrier of the differential gear
• 7 Exterior partial planetary carrier of the planetary stage
• 8 Central partial planetary carrier
• 9 Exterior side
• 10 Gearing
• 11 Rivet
• 12 Recess
• 13 Planetary Gear pair
• 14 First planetary gear
• 15 Second planetary gear
• 16 Planetary gear of the planetary stage
• 17 Sun gear
• 18 Sun gear
• 19 Bolt
• 20 Connecting bolt
• 21 Sheath
• 22 Radially projecting flange
• 23 Disk between the central partial planetary carrier and the first sun gear
• 24 Friction disk/friction ring
• 25 Disk between the planetary gear of the planetary stage and the central partial planetary carrier
• 26 Bar
• 27 Axial end
• 28 Radial interior
• 29 Radial exterior
• 30 Hole in the exterior partial planetary carrier
• 31 Side
• 32 Material recess
• 33 Hole for connecting bolt
• 34 Hole for support bolt
• 35 Support bolt
• 36 Bead
• 37 Surface area
• 38 Surface
• 39 Cavity
• 40 Bearing sheath
• 41 Gliding ring
• 42 Ring
• 43 Bulging
• 44 Radially projecting support area
• 45 Axially aligned contact area
• 46 First hardened area (axially aligned)
• 47 Second hardened area (radially aligned)
• 48 Third hardened area (axially aligned)
• 49 Radially inwardly off-set securing area
• 50 Recess
• 51 Elastic bar
• 52 Thickness

Claims

1-10. (canceled)

11. A planetary drive, comprising:

a sun gear (18);

a planetary carrier (5) operatively arranged coaxially and rotatably with respect to the sun gear; and,

a support component located radially between the sun gear and the planetary carrier, the support component comprising a bearing sheath and a gliding ring.

12. The planetary drive of claim 11, wherein the gliding ring has an elastic section and a deformable diameter.

13. The planetary drive of claim 12, wherein the elastic section is an elastic bar (51) formed by one or more recesses (50) in the gliding ring (41).

14. The planetary drive of claim 13, wherein the bar (51) has a Z-shape with right angles in a circumferential direction.

15. The planetary drive of claim 11, wherein the gliding ring (41) is made from plastic.

16. The planetary drive of claim 11, wherein the bearing sheath (40) is made from sheet metal.

18. The planetary drive of claim 11, wherein the bearing sheath circumscribes the gliding ring (41).

17. The planetary drive of claim 11, wherein the bearing sheath (40) has a first bulging (43) extending in an axial direction.

18. The planetary drive of claim 17, further comprising a second bulging (49), wherein the gliding ring (41) is located between the first and second bulges (43, 49) of the bearing sheath (40) extending radially inwardly.

19. The planetary drive of claim 17, wherein the first bulging (43) extends in the axial direction and a radial direction.

20. The planetary drive of claim 19, further comprising a second bulging (49), wherein the gliding ring (41) is located between the first and second bulges (43, 49) of the bearing sheath (40) extending radially inwardly.

21. The planetary drive of claim 11, wherein the bearing sheath (40) has a bulging (43) extending in a radial direction.

22. The planetary drive of claim 21, further comprising a second bulging (49), wherein the gliding ring (41) is located between the first and second bulges (43, 49) of the bearing sheath (40) extending radially inwardly.

23. A planetary drive of claim 11, further comprising a spur differential.

24. A transmission combination, comprising:

a differential gear (2);

a planetary stage (3);

a planetary carrier comprising a plurality of planetary carriers (6, 7, 8) assembled non-rotatably with respect to each other;

wherein the differential gear and the planetary stage share the planetary carrier.

25. The transmission combination of claim 24, wherein the differential gear is a spur differential.