WO2015067261A2

WO2015067261A2 - Supporting bearing assembly for a planetary differential

Info

Publication number: WO2015067261A2
Application number: PCT/DE2014/200551
Authority: WO
Inventors: Harald Martini; Thorsten Biermann
Original assignee: Schaeffler Technologies AG & Co. KG
Priority date: 2013-11-11
Filing date: 2014-10-14
Publication date: 2015-05-14
Also published as: WO2015067261A3; DE102013222833A1

Abstract

The invention relates to a planetary differential, comprising a drive gear (5) and two planet-gears sets supported in a planet carrier (3), of which planet-gear sets a planet gear (2) of the one planet-gear set meshes with a first sun gear (1A) and a planet gear of the other planet-gear set meshes with a second sun gear (1B), wherein the planet carrier (3) is radially rotatable and axially positionally defined on a housing (8A, 8B) by means of at least one rolling-element bearing (6, 7), the at least one rolling-element bearing (6, 7) comprises at least a first bearing shell (6A, 7A) and a second bearing shell (6B, 7B), which each have a flange end segment (6FA, 6FI, 7FA, 7FI) adjacent to the running surfaces (6GA, 6GI, 7GA, 7GI), wherein both flange end segments (6FA, 6FI, 7FA, 7FI) are oriented parallel to each other.

Description

Bez hehmino the ErftMum

Si telager arrangement for a planetend erenfial

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More particularly, the invention relates to a planetary disk with a drive wheel and two pancake wheel seats mounted in a p-net carrier, one of which is a piano wheel of a planetary red sata m ^' a first sun gear engages and a planetary gear of the other Pianetenradsa zes engages in a zw ites sun gear, the tarpaulin carrier on at least one roller bearing on a housing radially rotatable and axially goeitionsbestimrnt, where at least one Impact bearings at least a first and a second bearing shank each have a Flansebendab- section feenaohbart to the treads so. aurweisen,

After being used as a differential gear, especially for high forces and torques, such as those found in motor vehicles, eegelradiiifferentiaigetrieh has been used for around one hundred years, in 2002 the FZö monks further developed a so-called planetary differential as a front wheel divergence gear at the same power was more compact and lighter. This pianet differential fabric was further improved in the following years.

0

In such planetary differentials, a Abtnebswelle of a motor drives a front or Teilerrad as a drive wheel, there along with a dar n mounted Planefentrager to the common Ähese de Pianetendifferentlals (the common. Axis on housing, spur gear, planetary carrier and A drive shaft of the differential, is rotatable. The torsion element fed in via the spur gear lrc! The planetary carrier carries at least two planetary gears meshing over part of their width, each of which also engages in one of two differential springs. Typically, the torque is applied over several pairs of pianeta wheels uniformly distributed around the circumference two Sennori riders are connected to the A web worlds of Plaendend erentla,

For example, shows the WO 2ÖÖ8 / 11Ö425, A2 a Planetenraddiiferentlal «is designed to be particularly compact, the components can be easily manufactured and easy to assemble. The DE 102807 Q4Ö 478 AI discloses such a planetary differential, this document places greater emphasis on lightweight with high Drehmomenfkapazitat.

DE 10 2011 087 581A1 can likewise be used by way of example to explain the mode of operation of planetary differential gears: such as disc wheels. The geometrical! and functional peculiarities of said three pamphlets should be considered integrated here,

Oer advantage of such Planetendlfferentiale is a significant reduction in the Saulänge, Especially in ,, Fronttrieblerr with transversely mounted engine, a Planetendifferenfiai compared to a bevel gear differential considerable building lengths aruingen of up to? $% Achieve, that means that the planetary differential with a quarter of Long egelraddlfferentiais manages. _, Dsdureh leaves more room for other components such as the Mötor, gearbox and clutch housing,

It is the object of the present invention to eliminate the drawbacks of the prior art and to provide a piano answering pen which is less expensive and easier to produce, and where possible also a Disclosure of the invention

This object is achieved by a device according to the invention in that the plane ends are aligned parallel to one another.

A erfindungagemäSes Planetenraddifferenbai is characterized in that counter-safe to the known prior art adjacent _which: the tread Hege lighter * Flansebeudabschnitte (or "edges"} of the form are aligned ilzlagerschalen a bearing paraliei each other, are usually Pfanetenradträger of Flanetenraddiffarentialen Each Wiklager consists of two Lagerohalen (an inner and an outer, also called ÄuEenring and Innenhog), a Wilzkörperkifig and the Wilzkörpern, Kugein, cones, rollers, needles, tons or the like Bearing shells designed in such a way that on the one hand they are easy to produce, especially in terms of shape, but on the other hand can be safely changed in the radial wheel differential Erential aufzune men. On the other hand, the orientation of the fianschenda - suture on the soap of the flaxan has not been considered welter. However, due to the now-oriented orientation: the final lift pins are, as the AosfOhrungsbeiapielen clear, more cost-effective, a more compact design of the planetary differential allows. In addition, better protection against contamination and subsequent wear of the bearings can be achieved without giving up the stated advantages.

Verteilhafte developments are the ^'subject matter of the Untoransprüche and are explained in more detail below.

Thus, an advantageous embodiment is characterized in that both sides of the first bearing shell are in the same axial direction or in the same direction obliquely oriented to the axial direction. If both flanged bushes of the first bearing shaft and the same axial direction are used, this bearing shell can be manufactured by a forming process (Z3, deep drawing of a suitable bleed head) with: a comparatively lower stroke and thus shorter picking speed! As a result, the bearing shell can be produced more cheaply.

Another advantageous Aususfuhrungsform Is characterized in that the second Lagerschaie Fia schendabsehnitte has, which are aligned parallel to each other. Of course, the advantages which result for a first bearing shell as described above are also valid for the second bearing shell, d, h. In this case, this second Lagerschaie can also be produced inexpensively. In addition, if the Flahschenrfabschnitte the second Lagerschaie in the same axial direction, the above with reference. -On the first tray described benefits also for the second tagerschale. Therefore, if storage buffers become so cold, it is possible to further minimize the cost of canned meals. Alternati However, it is also possible that the Fianscbendabschnitte the second bearing shell facing in opposite axial directions. A further advantageous embodiment of the invention is characterized in that at least one bearing ring of at least one of the rolling bearings has a Li or egg-shaped cross section. Such a cross section: is simply Umferrritechnisch in Massehfertigung gehefzustete. At the same time, a bearing ring in "IT or shape encloses the cage and its cage particularly closely, so that, as a rule, a very compact bearing shape is produced, which in turn contributes to a reduction in the size of the end product.

It is also advantageous _: when sieve two Flanschendabschnitte overlap. If the bearing halves are aligned in parallel, the flange end abutments of two bearing shells may overlap. In this case, for example, a bearing plate can surround a Flanschendabschnitt a second Lagerschaie .. This gives the designer more freedom home execution of a construction according to the invention, For example, the outer ring with ^{■ at} least engage the leg of the inner ring in the leg.

It is particularly square when the connecting rings of the two bearing rings point axially or radially toward one another. If the flange end sections face one another, it follows that the bearing surrounds the rolling element. In particular in this embodiment, the gap between the Bearing rings maximum 30% of the Wäizkörperdurcb- diameter. Larger fission mats may cause smolder to penetrate the bearings during operation, shortening the life of the bearing. The above-mentioned and further specified embodiments can limit the contamination of the rolling elements and the running surface, which increases the service life of the bearings.

If the size of the inner ring in the housing is greater than the diameter of the Plao @ tentr # §ar on the outer ring and larger than the partial length of the rolling elements, further advantages are obtained. In such an embodiment, the inner ring of the bearing is radially outwardly of the pitch circle of the rolling elements and the outer surface radially inwardly within the pitch circle of the bodies Φ- gesföt t. The situation can be made smaller, more compact and cheaper on this catfish. At the same time, material can also be saved around the bearing since the bearing seat of the outer ring lies almost at the same diameter as the raceway of the inner ring. In other words, the bearing seat, an inner ring of each rolling bearing is arranged at most around the radius of a rolling body further than the bearing seat of the outer ring of the rolling bearing, and / or the bearing seat of the outer ring of each rolling bearing at a maximum about the thickness of a rolling body In this way, the bearings can be arranged so that they hug extremely compact in the radial direction, For this purpose, the inner ring partially surrounds the rolling elements outside and / or the outer ring surrounds the Wlizkörper also inside. This results in a radially extremely compact design of the Rlanefendlfterentials, In the known state of the art, How-in ^"FIG. 1, however, the inner ring and the outer ring of the bearing is so OHL supported radially inside the pitch circle OCE ätekörper by specially shaped inner and outer rings umförmfechniseh be prepared and the bearing as shown in Fig. 1 shown on »built

In a wide e Ausführungsforni the Planetenendifferentlal is characterized in that it is designed as a spur gear, Stirnraddiffeenfiaie are on Gr d Ihrm small Saulänge and rumble omenienöhertra- Fungägk iten especially in front-wheel drive vehicles sFront | riebiern ") used.

This one . eschrie enes bearings can be used particularly successfully in differenflalen planet, ^"in which two storage counter in E-Änordnung are clamped together. The above-mentioned reduction in the amount of air in comparison to conventional bevel-wheeled blindfolds also leads to a reduction in the stubborn spacing of planetary sensitiv- erals compared to Kegeirad differential. With conventional floating or fixed-sedimentation, this could lead to vibrations and forces, for example, of radicals over the fisselfiala drive shafts or are introduced via the drive shaft in the planetary differential, lead to tilting moments that damage the planetary differential long-term. This could lead to the differential, and in particular its storage, becoming more stable and thus generally more expensive and cha er,

To ake such tilting moments _u: is therefore stored at a erfindongs- like & en Planetendifierential the planet nfräger usually employed with a Stötzlagerung against the Äulenrad (front or splitter wheel) In a so-called O-configuration. This means that depending on a rolling bearing s is so arranged on each soap Pianetendifferentla _"that the two bearings are axially braced against one another, in the clamped Znstand is constantly out on both bearing an axial force bt, which causes the AEL ele- ments bearing balls or bearing ropes, on one opposite the differential aohse obliquely inclined flat © instead of ^'suf move one to sertoc len Escape. Highly accurate, the Outerlagerhnger .axon to each other and the Innenlagerhngar axially pushed away from each other. Therefore, the running surfaces of the wai elements in each individual bearing are such that perpendicular through the treads (and the rolling elements) meet outside of the bearings on the center axis of the differential. - By connecting these perpendiculars by mssi. Bearing each other so that they also cut (with the same bearing diameters usually in the middle) between the camps, then a diamond results as the name of this arrangement _; ö ^' \ Such Ö-storage can take a greater tilting moment than a FesLLlagerung with the same bearing distance, since the distance of Dryckmifteipynkfe or intersections of said vertical (on the axis of the differential) is greater than, for example, in a fixed-lot storage or a floating bearing, in which the running surfaces are perpendicular to each other and thus the pressure centers in the center of the tread. By absorbing the gre-te tilting moment a deformation de stored elements is avoided. At the same time quieter operation is achieved and the tagerlefoensdaoer increased because a "knocking ^* La" f ~ areas due to the bias practically not possible.

More preferably, the aße the storage at -.der. O ^ Mmänrn the inequality 8 (Ü - d)> 1, where B is the distance between the two bearings from each other, the so-called bearing width, D of the outer diameter of the bearing and d is the inner diameter of the bearing. In other words, this means that the bearing width is at least equal to or greater than the difference between internal and external diameter. Thus, the tolerance is at least as great as the difference between the inner and outer diameter of the bearings, which leads to an effective increase of the tilting moment compared to a conventional Fesf floating bearing or more floating bearing.

Preferably, the inner and outer rings of the bearing are removed without cutting. In particular in mass production, chip-free production methods are cost-effective, since the material is utilized efficiently, fewer accidents occur than in the case of cutting processes, and the throwing costs per part are also less expensive. Specifically, the blanks of the inner and / or outer rings of the rolling bearing are toor grown by cold-rolling a bender. Further preferably, both blanks have the same strength for the outer and outer rings and can also be made of the same material. Cold forming of sheet metal parts is an extremely cost effective one

leads. So-0 results in high strength in low-caliber bearings in combination with low coefficients, which increases the load capacity of the tag. If both blanks have the same thickness, they can be suitably manufactured together in a Ümförmvor- gang. In addition, if the same material is used, it is still possible to mold both rings together when forming inner and outer rings and to connect, for example, by a bridge, which is removed at or shortly before the final assembly. In this way, the installation can be simplified because before / during assembly few items are available. On the other hand, different aterials for inside ^"and outer ring used a camp could, for example as advertising hergesfeilt to that an easy-to-exchanging component yields faster and comparable sehleiSt, thereby protecting the mounted difficult part.

Preferably, the rolling elements are spherical. Zwa is the afore-mentioned Äyfbau also mi roles, cylinders, cones, tons, nadein or other: Watekdfpem producible, ball bearings are, however, as a mass-produced a sebr costa tion solution,

Vorzugswelse enclose the bearing rings laterally over the Bayraum de Wilzkörper outgoing parts of the bearing cage radially, in general W lzkörper are taken in a rolling bearing in a bearing cage. This bearing cage prevents the rolling elements abutting and help them from each other at a uniform distance, so that the bearing load is evenly distributed to the Wälzkör he is, this contributes to an increased bearing life If the bearing cage, which is usually designed to be weaker than the bearing rings, is enclosed by the bearing rings, it is difficult, if not impossible, to destroy the bearing cage by the action of m. Thus, by this construction, the life of the rolling bearing and thus the differential is increased

Further preferably, the lead thickness is a sheet metal finish from which the bearing shell is produced: ird, rnim, 30% of the rolling element diameter. With a sufficiently thick bearing bowl knows! this sufficient inherent stability to even then absorb the bearing forces, if it is not directly supported on another component. Since, in the case of the invention, at least one bearing shaft is not truncated, but is provided as a free surface, the bearing itself must absorb the compressive forces exerted by the shakers. For this, the sheet metal *, from which the bearing is manufactured, requires sufficient strength. This strength can be achieved, in terms of urological terms, with a sheet metal whose thickness is approximately 30% of the rolling element diameter.

In addition, it is preferred that the bearing inner ring, as one de bearing shells, is supported axially on the side wall and radially on the flange of the differential housing. In this way, the bearing inner ring is set so that when mounting the solid housing provides a defined seat of the inner ring, and the bearing preload is aufhnnghar on the outer rings acting on the bias. This facilitates the assembly, as on the outer rings in the assembled state better an adjustable force can be applied as to the inner rings. In other words, at least one of the or the storage «of the angular contact ball bearing in longitudinal section U-shaped, G örmig (lying), so in the broadest sense mauk hook or hörgelforrrtlg formed with two legs. The legs of the two rings preferably have axially or radially towards each other. Further preferably, the seat of the Innonrlnges in the housing is larger in diameter than the Sit of the planet carrier (Dlfferenzialkorbs) In the Auixenrln and also larger than the circle (ha) Wolter favors the AulSennng with at least a gift! in the Mau, so the "contour" of the inner ring S; ax ai or r dial (if not just an U-profl formed ion ring of the camp is present). Oc welter preferred two such bearings are clamped in D-arrangement,. SehiieSlieh Is mi evonugen, that the campers spanless, in esondero mtemiiec niseh ergestelit are.

One could also say, uefschnitt the $ the bearing is almost square, or otherwise in the installation space a herkdmmllrJ s camp is established, To _{E-arrangement:} realizing Is the Innenri ^ g of bearing radially outside the pitch circle of Waizkörper and Äuiennng radially inside As a result, a cost-effective stub closure for a concealed handle is obtained. The invention will be explained in more detail by means of exemplary embodiments with reference to the attached figures, in which:

1 shows a section through a support arrangement for a Planetend ifferentlsl with Hülligugeliage n in O arrangement according to the state of the ech ik,

FIG. 2 shows a section through a hinge arrangement according to the invention for a panel end lens with angular ball bearings in an O arrangement according to a first embodiment, FIG. 3 shows a section through a bearing for use in the latch arrangement according to FIG.

Figure 4 shows a sonitt, by an inventive Stutzanordriung for a planetary differential with Schr gkugeliagern In O anode according to a second A sfihrungsform, and

Figure S is a section through a Leger for use in the inventive EE Stötzanordnung nacn figure. FIG. 1 shows a scanning arrangement for a single-wheel differential as an example of a prior art planetary differential plate. Well the Stirnraddifferentiai achssymmelnsc. W rd (also in the other figures) S only e? Part shown above the Aehse.

From below (the axis of the A driebs the Diflerenfialgehäuses} upwards Dlfferenilafsonnen Sonnen / Sonnenrader 1.A, 1B, the radial m the flange of the ^: Dlfferentlaigehiuses supported and: via a toothing 1ΑΊ, io 181 rotatably with the respective (not shown) The differential gears 1A ₍ 18 engage meshing planetary gears (on average only one flange wheel 2 is to be named, which engages in the sun 1A) Each planetary wheel 2 is mounted in a planet carrier 3 via a bolt the planet carrier 3 is also a spur gear § of the differential

15 firmly connected. spur gear

the differential sunning In this prior art by means of two bearing / roller bearings (ElrsreL biger) ball bearings 0 and 7, each consisting of a ÄuEenring 6A and? A, an inner ring 0B and? B, several Wilzkörpern jewei s only one rolling body, here one Ball 6 € _" 7C, is shown) and a rolling bearing enclosing the bearing cage 6D, TD axially fixed and rotatably mounted.

The bearings 6 and:? are, as can be seen from Figure 1, constructed substantially mutually mirror-symmetrical. The bearing surfaces lie as can be seen from the figure at approximately the height of Eingrif s the planet Rider in five the sun and at the same approximate hr at the height of the extent de carrier ^"part. In addition, the inner and outer rings of the bearings are extended inwards so as to be uniformly inexpensive to produce uniformly and at the same time to be securely received in the spur gear shaft. FIG. 2 shows a spur gear differential with a suitable bearing arrangement. Comparable components receive the same Benugs elk as in Figure 1 and here only the differences from the arrangement of Figure 1 are explained in more detail In this Äus uhrüngsform falls compared to the prior art shown in Figure 1, first, that the bearings 6, 7 arranged further inside and the tagerschalen / bearing ring 6A, 68, TA, TB are significantly more compact. The inside have the reference numerals 6a and YES. The outer rings have the bowing angles iS and 78 in this arrangement are the differentiated suns 1A _; 18 radially directly in Flarv- see / Gehäusetelen 8.Ä, 88 supported the Differeniialgehäuses 2, instead of being supported in the prior art on Äusformungen La La ernnge.

In other words, the bearing seat of the outer ring 7A has almost the same diameter as the raceway of the Innenrlngs 78. It has been found that the difference of the radial Äbsfands the Lagerifze preferably maximally corresponds to the diameter of a rolling element The other components such as the Pfeten wheels 2, the Pianetenträger 3, the pin 4 and the spur gear 5 are arranged substantially as in Figure 1. Only the bearings 6 and 7 and the flanges A, 88 de housing 2 are fundamentally different ^{1 designed} as in the prior art.

More specifically, the flanges 8A, SB can surround the bearings 8 and 7 from outside, now with these bearings. Your inner rings 8A, 7A rest on an inwardly drawn flange of Pianetentrigers 3. The outer ring _$:> 7B are the Gehiuseteiien m, 88, welöhe differential suns on ^"taking .. How u see is" are the tager $ 7 and also mirror mmet- hsc each other. In contrast to the storage shown in Figure 1, in which only one of the treads 8GA, SGI, 7GA, 7G (namely the running BGA, 70A AuAenlageT 6A, 7ÄE) _. "ffef is located and by the bias of the balls as Wäizkörper resiliently ^' against the tread 6ö _; TO the Inneniagersehaie 68, 7B presses on the housing part 8A ₅ 88 rests in the inventive construction both the tread of the inner and the outer bearing absorb elastic forces. This is approximately recognizable by the features visible in the figure. C-shaped design of the cross section of the two tagerschalen achieved D durc are all f schanderendahsd nitte FA, 8FI and 7FA,? F! the inner and inner bearing shells aligned parallel to each other In addition to the more compact structure Compared to the Aylbau shown in Figure 1, there is a better distribution of the Vorspannkrall; 3 shows a section through the layer 7 (with parts 7 A to 7 U and the drawn in Fiansohendabschnitten 7FA, 7FI and treads 7GA,? OI) of Figure 2 as a olle both LaQ ^ rs by the elastic balance on both shells an example! For a situation in which the novel bearing arrangement can be used, the bearing cage 7D can be produced in this embodiment, as can be seen from FIG. 3, with very good axial set, because the rolling bodies are largely enclosed by the bearing shells and thus there are few degrees of freedom could allow an undesirable movement of the rolling elements.

In addition, contamination of the bearings is better avoided by the extensive enclosing of the bearing cage and the balls used here as Waizkörper by the bearing shells 7A, 7B. Since both the Lagerkälig and the rolling elements are largely enclosed with: this construction, it is difficult for very useful and foreign body to penetrate into the bearings. Tests have shown that the gap A between inner and outer ring is ideally at most 30% of the diameter of the rolling elements 7C. In the figure shown here by way of example, the distance Ä is less than 10% of the rolling element diameter on the less polluted inner side, on the outside it is even lower. Small spikes, on the one hand, increase the precision and thus the bearings, on the other hand, with too large gaps As already mentioned, the covering of the wicks and thus the protection against contamination can not be as extensive as desired. Thus niyss dleshezug- For each application, a compression for the gap triple could be found, which ^, however, is often at the indicated 38% of the rolling element diameter. The arrangement of the flange sections 7FA, 7F1 parallel to each other is essential to the invention. Ay & erden are in the camp here In the embodiment shown, the (not denoted) fianohes end sections opposite the flanges are also arranged 7FA, 7FI also parallel to & imrt & r and parallel to the designated sections 7FA, 7F1.

Also from Flg. 3 that the thickness of the bearing rings 7A, TB (and analogously also the rings SA, B large should be enough to cushion the prestressing mentioned above with reference to FIG. 2. At the same time, the thickness and strength should be sufficient According to experience, these requirements can be fulfilled if the bearing rings 7A, TB have a: sheet metal thickness that is at least 30% of the diameter of the rolling bodies,

Of course, this value can vary depending on the strength of the material of the bearing rings. Too thin bearing rings could cause the distortion to be insufficient or cause the bearing rings to bend under load. On the other hand, if the bearing rings (especially for solid material) are too thick, the bearings become unnecessarily heavy, and manufacturing is also made more difficult by means of forming. In other words, an excessively violent fact leads, in addition to the weight loss, both to higher material costs and to higher costs of continuation.

Figure 4 shows a Stirnraddifferenflai as an example of a Plianneraddifferentlals according to another export ngsförm de invention, As shown in Figure 4 recognizes the extension of Innebliaelf borrow 78 encompasses an area into which the Flansehendsbsohmti the Aufienlayfflache TA protrudes, At the same time could the Ausfüfliche TA in this example so In addition, the outer ring TA engages with its one flansohendahsohni with 7FA i the inner ring 7B. In addition, In In this example, although the flange face 7ΈΑ and 7FI are aligned parallel to each other, a face 7H is not parallel to these faces. Other components not emphasized in Figures 4 and 5 are similar to those of Figures 1 and 2 and who That is why we have not discussed more

This design according to Figure 4 with a tager according to Figure 5 also provides better protection against contamination than the previously mentioned prior art, because the inner ring with the Innenlayfflich the Außenri g embrace the ÄuSenlauffiäehe! and therefore the inner and outer rings form a labyhnthartlge seal.

In addition, an alternative StOt structure for the Irinenhng is shown in Figure 4. As a structure of the stems, a pot-shaped structure of thin and thus resilient sheet metal is used; which stiffens the bearing seat, the insert *, and also leads to a better balance of the forces acting on the inner ring. The stiffening with low yaferial use: results in lower-cost operating capabilities for the bearing seat. Finally, this results in storage due to the low mortality rate, also a weight and aterlaikosfenersparnis compared to storage on a conventional bearing seat. More specifically, this invention is described in a co-pending application.

Of course, modifications of the embodiments are possible, which are not shown here in detail. Scots can also be used as wilzkdfpers instead of bullets, also in Röllen _s Nadein or the cone in the camps. Instead of the here shown design of the Stlrnraddlfferenfials with straight teeth a schragverz.a ntes Stirnraddlfferentiai and of course a planetary differential without spur gear can be constructed with the shown tageranordnung. 1 & Dtffer ntialsonne sun / sun wheel / first sun wheel

18 Dif erenial s / Sun / Sunwheel / Zwelee Sonnenred 1A1 gearing

181 toothing

2 Pianetenrait lan ©!

3 planet carrier / Drägerferfalkerb

4 bolts

5 spur gear / drive wheel

6 Bearings Bearings / Bearings

6A bearing ring / e ste bearing plate

68 bearing ring second bearing shell

6C ball

SD Lagerkaftg

8.FA Flanseendabscbnitt (auSen)

6FI flange end gate (inside)

80 Ä Lau eone

8GI Lsufflaot e

7 Bearings / Rolling Bearings

7 & bearing ring / first bearing shell

78 bearing ring / second bearing shells

70 rolling bit / ball

7D bearing cage

7 ¥ A flange end (anfen

7Fi Flanso end section (inside)

TQA tread

7GI tread

7 H ue-oriented f a n o n s h o o tio n s

Flanssii Geha seteti

08: Flange / 8th part

Claims

P tenta s rü he

1. Planetary end potential with a drive wheel {5} and two planetary gear sets erroneously crossed by a planter (3), of which one planetary gear (2) of the one planetary gear sets the first ring gear (1A) and the planetary gear of the other Planetenradsatzes engages in a second Sennenrad (18}, weaves the Planententräget (3) via at least one roller bearing (6, 7} on eifern housing C8A, 88} radially rotatable and positionally determined the position is at least one roller bearing iß, 7) at least a first tagerschale (6A, 6A) and a second bearing shark (SB, 78) each having a flange end portion (BFA, 6FI, 7FA, 7PI: 7H) adjacent the treads (6A, 6ΘΙ, 7GÄ _> 7Qi): .dsdur & fo iete ni et LEB that both Fiansehendabsehnltte {$ Ä _S 6FI, 7FA, 7Fi) are aligned parallel ®r 2u © _ina.. 5 2. Flanetendsfferentlal according to claim. 1, characterized in that the ball end sections (BFA, 8PI, 7FA, 7FI) are facing the axial direction of the bearing block (8A, 7A).

3, Planetendifterentiaf according to claim 1 or 2, dadurpii gekennzeictoei _s that the second bearing shell (88, 78) Planschendabschnitte (8FÄ, 8FI, 7FÄ, 7FI), which are aligned parallel to each other.

4; Pianetendlf erenfial after

that the flange end sections (6F, 8FI _< 7FA, 7F!) of the second bearing sharks (8B, 78) point in the same axial direction,

§ Pianetendifferentia! according to claim 3, § d by ekeon aichn © t _s that the Pia schendabschnitte _(FA; 8FI, 7FÄ 7FI _t) of the second tagersshaie (68, 78} into one another have opposite axial directions,

6, flanging differential according to one of the preceding claims, characterized in that at least one bearing ring (8A _> 7A _; 88, 78) of at least one of the roller bearings (6, 7) has a II-C-shaped cross-section.

7. Planetary ifferethal, according to one of the preceding approaches, overlapping two flankseeds for F,? H).

8. The pianides according to any one of claims 1 to 8, characterized by pekenn * xefklri t, that fenschandabsohnitt ($ FA _.i $ F 7Ft 7F \) of the two bearing rings (6A, 7A _f & B,? B) axially or radially to each other,

9. Raney differentiation according to a previous A test, thereby peke nxelcrf ©! That the Sil of the Innan ring (6B _S 7B in the housing {SÄ, 88} in the Dyrc measurer gröEar as the site of the planet carrier (3) on the outside ( A _> 7A) nd grfj & er as the subcircuit of itekcrper (iC,? C)

1: 0, planetary difference according to one of the existing claims, dadyret gtkfcifti & ieijnef _» class it designed as Stirnraddifferential