DE102018130118A1 - Helical gear differential - Google Patents

Abstract

The invention relates to a spur gear differential gear with a revolving housing, a first sun gear, a second sun gear and a coupling planet arrangement with first and second coupling planets for coupling the sun gears in opposite directions, the first coupling planet engaging radially from the outside in the first sun gear, the second coupling planet engage radially from the outside in the second sun gear, engage the first coupling planet in the plane of the first sun gear in the second coupling planet and are axially shorter in terms of their toothing than the second coupling planet, the tip diameter of the first sun gear is smaller than the root diameter of the second sun gear , the first coupling planets are each supported radially via a first bearing device, the bearing surfaces of which are realized within a cylinder space which is aligned coaxially with the axis of the respective first coupling planet and on the base s the toothing of the first coupling planet protrudes, and the second coupling planets are each supported radially in the revolving housing by a second bearing device, and in this case the respective second bearing device comprises bearing surfaces which are formed by the tip circular surfaces of the second coupling planet.

Description

Field of the Invention

The invention relates to a spur gear differential gear with a revolving housing, a first sun gear, a second sun gear and a coupling planet arrangement with first and second coupling planet, the first coupling planet engaging radially from the outside in the first sun gear and the second coupling planet radially from the outside engage the second sun gear, engage the first coupling planet in the plane of the first sun gear in the second coupling planet and the tip diameter of the first sun gear is smaller than the root diameter of the second sun gear.

A spur gear differential of this type is based on the applicant DE 10 2014 206 528 A1 known. In this known spur gear differential gear, the mutually intermeshing first and second coupling planets of the coupling planetary arrangement form a planetary gear rim which surrounds the sun gears. The planet gears of the coupling planetary arrangement sit in cylindrical bores, the longitudinal axes of which are aligned parallel to the axis of rotation of the planet carrier. These holes form pockets that are delimited by cylindrical wall sections and are captured by the path space of the toothing of the respective sun gear. These cylindrical wall sections of the pockets act as bearing surfaces on which the tip circular surfaces of the coupling planets abut and are thus supported radially and rotatably.

Out DE 10 2013 202 088 A1 Another spur gear differential gear is known, in which the mutual meshing of the coupling planet takes place in the toothing plane of one of the two sun gears. The coupling planets are axially drilled through and supported by needle bearings on bolts that are anchored in the revolving housing in the area of their axial end sections.

Object of the invention

The invention has for its object to provide a spur gear of the type mentioned, which is characterized by a robust and inexpensive to implement construction and an advantageous mechanical operating behavior.

Solution according to the invention

• - einem Umlaufgehäuse,
• - einem ersten Sonnenrad,
• - einem zweiten Sonnenrad und
• - einer Koppelplanetenanordnung mit ersten und zweiten Koppelplaneten zur gegensinnig drehbaren Koppelung der Sonnenräder,

wobei

• - die ersten Koppelplaneten radial von außen her in das erste Sonnenrad eingreifen,
• - die zweiten Koppelplaneten radial von außen her in das zweite Sonnenrad eingreifen,
• - die ersten Koppelplaneten in der Ebene des ersten Sonnenrades in die zweiten Koppelplaneten eingreifen und hinsichtlich ihrer Verzahnung axial kürzer bemessen sind als die zweiten Koppelplaneten,
• - der Kopfkreisdurchmesser des ersten Sonnenrades kleiner ist als der Fußkreisdurchmesser des zweiten Sonnenrades,
• - die ersten Koppelplaneten jeweils über eine erste Lagereinrichtung radial abgestützt sind, deren Lagerflächen innerhalb eines Zylinderraumes realisiert sind, der zur Achse des jeweiligen ersten Koppelplaneten gleichachsig ausgerichtet ist und an den Fußkreis der Verzahnung der ersten Koppelplaneten heranragt, und
• - die zweiten Koppelplaneten jeweils über eine zweite Lagereinrichtung radial in dem Umlaufgehäuse abgestützt sind und hierbei die jeweilige zweite Lagereinrichtung Lagerflächen umfasst, die durch die Kopfkreisflächen der zweiten Koppelplaneten gebildet werden.

This object is achieved according to the invention by a spur gear differential gear with:

• - a circulation housing,
• - a first sun gear,
• - a second sun gear and
• a coupling planet arrangement with first and second coupling planets for coupling the sun gears in opposite directions,

in which

• - the first coupling planets engage radially from the outside in the first sun gear,
• - the second coupling planets engage radially from the outside in the second sun gear,
• the first coupling planets engage in the second coupling planet in the plane of the first sun gear and are axially shorter in terms of their toothing than the second coupling planet,
• the tip circle diameter of the first sun gear is smaller than the base circle diameter of the second sun gear,
• - The first coupling planets are each supported radially via a first bearing device, the bearing surfaces of which are realized within a cylinder space which is aligned coaxially with the axis of the respective first coupling planet and projects towards the root circle of the toothing of the first coupling planet, and
• - The second coupling planets are each supported radially in the revolving housing via a second bearing device and in this case the respective second bearing device comprises bearing surfaces which are formed by the tip circular surfaces of the second coupling planet.

This advantageously makes it possible to create a spur gear differential transmission in which the short coupling planets which engage in the first sun gear and which are smaller in terms of the tip circle diameter are arranged and mounted in the circulation housing while realizing a radial head play remaining with the circulation housing and at the same time those in the second sun gear engaging second coupling planet can be supported over their entire length on the revolving housing.

The spur gear differential gear according to the invention is preferably designed for this purpose in such a way that the first coupling planets are supported radially in the revolving housing at least on one side by structures which protrude axially over the toothing plane of the first sun gear and which rotate with the coupling planet about their planetary axes. These structures rotating together with the first coupling planets can be realized as integral peg sections with the coupling planet, which in the Extend the area of the axial ends of the coupling planets axially beyond the toothing plane of the first sun gear and penetrate into structures of the revolving housing and are rotatably supported in the revolving housing while realizing a sliding bearing. The outside diameter of these pin sections is equal to or smaller than the root circle of the first coupling planet. This makes it possible to implement a continuously cylindrical circumferential surface on the pin sections, which functions as a sliding bearing running surface.

In the spur gear differential gear according to the invention, the first coupling planets are preferably mounted in the revolving housing via a journal bearing and the second coupling planet are supported in the revolving housing via a tip circle bearing.

As an alternative to the above-mentioned mounting of the first coupling planet by means of axially projecting pin sections, it is also possible to support the coupling planet radially and preferably also axially within their base circle level by structures or bearing systems which penetrate axially into or penetrate the first coupling planet.

The spur gear differential gear according to the invention is preferably constructed in such a way that the axial length of the first coupling planet corresponds to the axial length of the toothing of the first sun gear and also the axial length of the second coupling planet corresponds to the sum of the axial lengths of the toothing of the first and second sun gear.

The circulation housing is preferably composed of a pot structure and a lid structure. Here, the first and second coupling planets as well as the first sun gear and the second sun gear are received in bores which are formed in the pot structure. The cover structure can be designed so that it forms a first axle bore through which a first output shaft can be inserted into the first sun gear. In the same way, the pot structure can be designed such that it forms a second axis bore through which a second output shaft can be inserted into the second sun gear. The lid structure and the pot structure are preferably centered on one another and the circulating housing carries a drive wheel.

The two sun gears are preferably mounted radially within the revolving housing. It is possible to form mutually complementary structures on the first sun gear and on the second sun gear, which have the effect that the two sun gears center on one another and can also be rotated relative to one another.

In the spur gear differential gear according to the invention, a set of the coupling planets with radial play of the toothing tip circle is mounted to the pockets of the circulating housing and a second set of the coupling planet is supported on the rotating housing via the tip circle. Thus, the long or short planets with radial play of the tip circle can be stored contact-free to the differential cage in the differential cage / planet carrier and the correspondingly short or long coupling planets engaging in these coupling planets are, however, supported on the differential cage / planet carrier in a contacting manner via the tip circle of their teeth. In particular, the short planets have pins made in one piece with them or one or two fixed pins and are supported by these pins in the differential carrier. The short planets can also be rotatably seated on planet bolts, in which case these planet bolts are non-rotatably seated in the differential carrier. The concept according to the invention has the advantage that only for the long planets, which form a larger support surface than the short coupling planets, is a tip circle bearing. As a result, the load is better distributed at the tip circle bearing, and in addition a part of the radial forces from the tooth engagement are passed on to the small gears due to the constellation according to the invention, so that the tooth forces are generally not as high.

Figure list

• 1 eine Axialschnittdarstellung zur Veranschaulichung des Aufbaus eines erfindungsgemäßen Stirnraddifferentialgetriebes in der Ebene der Achsen der ersten - d.h. der „kurzen“ - Koppelplaneten;
• 2 eine Axialschnittdarstellung zur Veranschaulichung des Aufbaus eines erfindungsgemäßen Stirnraddifferentialgetriebes in der Ebene der Achsen der zweiten - d.h. der „langen“ - Koppelplaneten;
• 3a bis 3j eine Darstellungsserie zur Veranschaulichung unterschiedlicher Varianten der ersten Lagereinrichtung der ersten Koppelplaneten;
• 4 eine Skizze zur Veranschaulichung einer Lagerbohrung für einen Lagerzapfen eines kurzen Koppelplaneten mit einer vollumfänglich geschlossenen und zylindrischen Bohrungswand;
• 5 eine Skizze zur Veranschaulichung einer Lagerbohrung für einen Lagerzapfen eines Koppelplaneten mit einer sektional aufgebrochenen und damit zur Verzahnung des zweiten Sonnenrades hin offenen, ansonsten ebenfalls zylindrischen, Bohrungswand.

Further details and features of the invention will become apparent from the following description in conjunction with the drawing. It shows or show:

• 1 an axial sectional view to illustrate the structure of a spur gear differential according to the invention in the plane of the axes of the first - ie the "short" - coupling planet;
• 2nd an axial sectional view to illustrate the structure of a spur gear according to the invention in the plane of the axes of the second - ie the "long" - coupling planet;
• 3a to 3y a series of illustrations to illustrate different variants of the first bearing device of the first coupling planet;
• 4th a sketch to illustrate a bearing bore for a journal of a short coupling planet with a completely closed and cylindrical bore wall;
• 5 a sketch to illustrate a bearing bore for a journal Coupling planets with a sectionally broken and thus open to the teeth of the second sun gear, otherwise also cylindrical, bore wall.

Detailed description of the figures

The representation after 1 shows an embodiment of a first embodiment of a spur gear differential transmission according to the invention with a rotating housing GH , a first sun gear S1 , a second sun gear S2 and a coupling planetary arrangement K with first and second coupling planets K1 , K2 (regarding K2 please refer 2nd ). The spur gear differential gear is constructed in such a way that the first coupling planet K1 radially from the outside into the first sun gear S1 intervene and the second coupling planet K2 radially from the outside into the second sun gear S2 intervention. The second coupling planet K2 bridge the tooth planes of the two sun gears S1 , S2 . The intervention of the first coupling planet K1 into the second coupling planet K2 takes place in the gear plane E1 of the first sun gear S1 . The first coupling planet K1 are axially shorter than the second coupling planets K2 . The tip circle diameter of the first sun gear S1 is also smaller than the root diameter of the second sun gear S2 . In the context of the present description, the term “toothing plane” used above is understood to mean a spacer disk which is radially aligned with the circumferential axis of the corresponding gearwheel and whose mutually parallel boundary planes are aligned with the end faces of the toothing of the gearwheel facing away from one another.

The spur gear differential transmission according to the invention is characterized according to the invention in that the first coupling planet K1 each via a first storage facility B1 are radially supported, their bearing surfaces B1A are realized within a cylinder space facing the axis XK1 of the respective first coupling planet K1 is aligned coaxially and to the base FK1 the gearing VK1 the first coupling planet K1 protruding, whereby (see here 2nd ) the second coupling planet at the same time K2 each via a second storage facility B2 radially in the circulation housing GH are supported and the respective second storage device B2 Storage space B2A comprises by the tip circular surfaces of the second coupling planet K2 be formed.

In the exemplary embodiment shown here, the first coupling planets are K1 on both sides through axially across the roller plane E1 of the first sun gear S1 excellent and with the coupling planet K1 around their planetary axes XK1 rotating structures in the circulation housing GH stored radially. The first coupling planets form here K1 in the region of their axial ends, pin sections ZK1 and are over these tenon sections ZK1 in the circulation housing GH rotatably mounted. The tenon sections ZK1 are dimensioned such that the outer diameter of these pin sections is smaller than the diameter of the root circle FK1 the first coupling planet K1 .

The spur gear differential transmission according to the invention shown here is constructed overall such that the first coupling planet K1 via a journal bearing in the circulation housing GH are stored and the second coupling planet K2 via a head circle bearing in the circulation housing GH are stored.

The axial length LK1 the interlocking of the first coupling planets K1 corresponds to the axial length LS1 the toothing of the first sun gear S, ie the “thickness” of the first toothing plane E1 .

As from the illustration 2nd the axial length clearly corresponds LK2 the second coupling planet K2 the sum of the axial lengths LS1 , LS2 the toothing of the first and second sun gear S1 , S2 .

The circulation housing GH consists of a pot structure T and a lid structure D together and the first and second coupling planets K1 , K2 and the first sun gear S1 and the second sun gear S2 are drilled in holes in the pot structure T are formed, the lid structure D a first axis bore AB1 forms through which a first - not shown here - output shaft in the first sun gear S1 is insertable and the pot structure T a second axle hole STARTING AT 2 forms, through which a second - also not shown here - output shaft in the second sun gear S2 can be introduced. In both holes AB1 , STARTING AT 2 slide bushings AB1 ' , STARTING AT 2' .

The lid structure D and the pot structure T are centered on each other by mating surfaces. The circulation housing GH carries a drive wheel DW . The connection of the drive wheel DW to the circulation housing GH done by screws 1 which axially penetrate a flange section of the pot structure and with a threaded section 1a in a ring element 2nd are anchored. About this ring element 2nd becomes the lid structure D axially on the pot structure T curious; excited. The pot structure T and the lid structure D are preferably made of a cast material, in particular spheroidal graphite cast iron. The ring element 2nd is preferably made of a steel material.

The first sun gear S1 and the second sun gear S2 can in particular by concentric complementary structures are rotatably centered on one another, or are aligned coaxially with one another by other bearing and guide devices and are axially and radially supported on one another.

In the embodiment shown here is the first sun gear S1 via a taper formed on it KS1 in a first bearing ring 3rd led out into the lid structure D is pressed. The second sun gear S2 also has a tapered pin KS2 on by a second bearing ring 4th is guided, which is guided in the pot structure. The second bearing ring 4th is axially by a spring 5 against the first sun gear S1 crowded. The feather 5 is supported on a circumferential shoulder T1 the pot structure T from. This bearing generates a frictional torque and causes a defined frictional coupling of the sun gears S1 , S2 .

The lid structure D and the pot structure T are in the area of the end faces of the second coupling planet K2 with holes 6 , 7 Mistake. These enable bidirectional lubricant passage and pressure compensation.

The axial length LS1 the teeth of the first sun gear S1 is greater than the axial length LS2 the teeth of the second sun gear S2 . The axial length LS1 the teeth of the first sun gear S1 is preferably 1.4 to 2.5 times the axial length of the toothing of the second sun gear S2 .

The illustration series after the 3a to 3y shows in the form of axial sectional representations different designs of the first coupling planet K1 and the functional structures of the first storage facility realized by this B1 .

In the embodiment according to 3a the first coupling planet is stored K1 due to cylindrical pins projecting axially beyond the teeth on both sides ZK1 whose outer diameter is smaller than the root circle FK1 the gearing VK1 . The outside surfaces B1A the cone ZK1 form slide bearing running surfaces of the first bearing device B1 . The cones ZK1 are in one piece with the coupling planet K1 executed.

In the embodiment according to 3b the first coupling planet is stored K1 again by axially on both sides via the toothing VK1 protruding cylindrical pins ZK. The bearing journals ZK1 have different diameters in this embodiment. The outer diameter of the in the lid structure (cf. 2nd ) penetrating and left bearing pin in this illustration LK1 is larger than the outer diameter of the bearing pin on the right in this illustration and penetrating into the pot structure ZK1 . The outer diameter of the larger journal ZK1 corresponds almost to the root diameter FK1 , the outer diameter of the smaller journal ZK1 is significantly smaller. This relatively small journal ZK1 can be stored in a bearing hole in the pot structure as in 4th is outlined.

For the embodiment according to 3c the explanations apply 3b the outer diameter of the bearing journal on the right in the illustration is analogous to this ZK1 dimensioned larger. This relatively large journal ZK1 can be stored in a bearing hole in the pot structure as in 5 is outlined.

In the embodiment according to 3d the first coupling planet is stored K1 by means of a cylindrical pin projecting axially beyond the toothing on one side ZK1 whose outer diameter is smaller than the root circle FK1 the gearing VK1 , and by a not shown here, by the circulation housing GH provided peg that is in a cylindrical blind hole BB1 immersed in the coupling planet K1 is formed and the inner diameter is smaller than the root diameter FK1 the gearing VK1 . The outside surface B1A of the cone ZK1 and the inner peripheral surface BB1 ' the blind hole BB1 form slide bearing running surfaces of the first bearing device B1 . The cone ZK1 is also in one piece with the coupling planet K1 executed.

In the embodiment according to 3e the first coupling planet is stored K1 similar to the embodiment according to 3a due to cylindrical pins projecting axially beyond the teeth on both sides ZK1 whose outer diameter is smaller than the root circle FK1 the gearing VK1 . The outside surfaces B1A the cone ZK1 form sliding bearing surfaces of the first Storage facility B1 . The cones ZK1 are in one piece with the coupling planet K1 executed. The cones ZK1 are of circumferential grooves NK1 edged. These circumferential grooves NK1 allow the storage of the cones ZK1 through these cones ZK1 to accomplish fringing structures that penetrate axially below the face level of the toothing and thus widen the bearing surfaces and force within the toothing plane.

In the embodiment according to 3f the first coupling planet is stored K1 again like regarding 3a already described by cylindrical pins projecting axially beyond the teeth on both sides ZK1 whose outer diameter is significantly smaller than the base circle FK1 the gearing VK1 . The outside surfaces B1A the cone ZK1 form slide bearing running surfaces of the first bearing device B1 . The cones ZK1 are in one piece with the coupling planet K1 executed.

In the embodiment according to 3g the first coupling planet is stored K1 in interaction with both sides axially in the plane E1 the gearing VK1 immersed blind holes BB1 whose inner diameter is smaller than the root circle FK1 the gearing VK1 . The inner surfaces BB1 ' the blind holes BB1 , ZK1 form slide bearing running surfaces of the first bearing device B1 . The first coupling planet K1 are thus within their base circle level by axially into the first coupling planet K1 immersed or radially penetrating structures.

For the embodiment according to 3h the explanations apply 3g analogous. The blind holes BB1 are designed as stepped holes.

In the embodiment according to 3i the first coupling planet is stored K1 through a bearing pin 8th that in the circulation housing GH (See. 1 and 2nd ) is firmly anchored and the coupling planet K1 along one in the coupling planet K1 trained bearing bore axially penetrates. The coupling planet K1 is over a tread formed by the inner peripheral wall of the bearing bore B1A on the bearing pin 8th stored. The inside diameter of the bearing bore is significantly smaller than the diameter of the root circle FK1 .

In the embodiment according to 3y the first coupling planet is stored K1 in the same way as for the variant 3i through a bearing pin 8th that in the circulation housing GH (see. 1 and 2nd ) is firmly anchored and the coupling planet K1 via one in the coupling planet K1 trained bearing bore axially penetrates. The coupling planet K1 is here with the inclusion of a rolling bearing RB, in particular in the form of a needle bearing, via a running surface formed by the inner circumferential wall of the bearing bore B1A on the bearing pin 8th stored. The inner diameter of the bearing bore is also significantly smaller than the diameter of the root circle FK1 .

The representation after 4th shows a sketch to illustrate the location and design of a for receiving a journal ZK1 provided bore 9 the pot structure T . This hole 9 is in the pot structure T of the circulation housing GH educated. It is in the vicinity of that hole 10th in which the second sun gear S2 sits. The diameter of the hole 9 is coordinated here so that between the hole 9 and the hole 10th a section of material 11 of the circulation housing GH remains.

In the embodiment according to 5 is the diameter of the hole 9 enlarged and the hole 9 lies to the side of the hole 10th free. This allows lubricant from the peripheral region of the second sun gear to the inner wall of the bore 9 penetrate. The hole 9 supports as by the cone reaction forces FL , FR indicated the spigot running in it ZK1 on wall sections opposite the opening 11 ' are offset relatively in the circumferential direction of the bore wall.

In the spur gear differential according to the invention, the coupling planet is supported K1 , K2 the coupling planet arrangement K thanks to two different storage concepts B1 , B2 . The bearing of the coupling planets, which are short in terms of their axial length K1 takes place through a bearing concept in which the treads are within the root circle level of the toothing VK1 of the first coupling planet K1 lie. The storage of the axially longer and the gear planes E1 , E2 of the coupling planet bridging the two sun gears K2 takes place in accordance with a storage concept B2 , in which the treads outside the root circle FK2 , especially on the tip circle of the gearing VK2 , lie. The interlocking of the short coupling planets K1 thus runs under a defined circumferential gap in the pot structure T .

QUOTES INCLUDE IN THE DESCRIPTION

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

Patent literature cited

• DE 102014206528 A1 [0002]
• DE 102013202088 A1 [0003]

Claims (10)

Helical differential gear with: - a circulation housing (GH), - a first sun gear (S1), - a second sun gear (S2) and - A coupling planet arrangement (K) with first and second coupling planet (K1, K2), wherein - The first coupling planets (K1) engage radially from the outside in the first sun gear (S1), - The second coupling planet (K2) engage radially from the outside in the second sun gear (S2), - The first coupling planets (K1) engage in the toothing plane (E1) of the first sun gear in the second coupling planet (K2) and are dimensioned axially shorter than the second coupling planet (K2), - The tip circle diameter of the first sun gear (S1) is smaller than the base circle diameter of the second sun gear (S2), - The first coupling planets (K1) are each supported radially via a first bearing device (B1), the bearing surfaces (B1A) of which are realized within a cylinder space which is aligned with the axis (XK1) of the respective first coupling planet (K1) and at the base circle the toothing of the first coupling planet (K1) protrudes, and - The second coupling planets (K2) are each supported radially in the circulating housing (GH) via a second bearing device (B2) and in this case the respective second bearing device (B2) comprises bearing surfaces (B2A) formed by the tip circular surfaces of the second coupling planet (K2) will. Spur gear differential gear after Claim 1 , characterized in that the first coupling planets (K1) radially at least on one side by structures in the revolving housing (GH) which project axially over the tooth plane (E1) of the first sun gear (S1) and which rotate with the coupling planets (K1) about their planet axes (XK1) are stored. Spur gear differential gear after Claim 2 , characterized in that the first coupling planets (K1) form pin sections (ZK1) in the region of their axial ends and are rotatably mounted in the revolving housing (GH) via these pin sections (ZK1). Spur gear differential gear after Claim 3 , characterized in that the outer diameter of these pin sections (ZK1) is smaller than the root circle (FK1) of the first coupling planet (K1). Spur gear differential according to at least one of the Claims 1 to 4th , characterized in that the first coupling planet (K1) are supported by a journal bearing in the revolving housing (GH) and the second coupling planet (K2) is supported by a tip bearing in the revolving housing (GH). Spur gear differential according to at least one of the Claims 1 to 5 , characterized in that the first coupling planets (K1) are radially supported within their base circle level by structures (8) which penetrate axially into the first coupling planets (K1) or penetrate them. Spur gear differential according to at least one of the Claims 1 to 6 , characterized in that the axial length of the first coupling planet (K1) corresponds to the axial length of the toothing of the first sun gear (S1) and that the axial length (LK2) of the second coupling planet (K2) the sum of the axial lengths (LS1, LS2) corresponds to the toothing of the first and second sun gear (S1, S2). Spur gear differential according to at least one of the Claims 1 to 7 , characterized in that the circulating housing (GH) is composed of a pot structure (T) and a cover structure (D) and that the first and second coupling planets (K1, K2) and the first sun gear (S1) and the second sun gear (S2) are received in bores which are formed in the pot structure (T), the cover structure (D) forming a first axle bore (AB1) through which a first output shaft can be inserted into the first sun gear (S1) and the pot structure (T) a second Axle bore (AB2) forms through which a second output shaft can be inserted into the second sun gear (S2). Spur gear differential according to at least one of the Claims 1 to 4th , characterized in that the lid structure (D) and the pot structure (T) are centered on one another and that the circulating housing (GH) carries a drive wheel (DW) and / or that the first sun gear (S1) and the second sun gear (S2) are centered to each other. Spur gear differential, especially according to at least one of the Claims 1 to 9 , with: - a revolving housing (GH), - a first sun gear (S1), - a second sun gear (S2) and - a coupling planet arrangement (K) with first and second coupling planets (K1, K2) which are in engagement with each other, whereby - the first coupling planets (K1) engage radially from the outside in the first sun gear (S1), - the second coupling planets (K2) engage radially from the outside in the second sun gear (S2), - the first coupling planets (K1) via a first bearing concept (B1) are supported radially in the circulation housing (GH); - The second coupling planets (K2) are supported radially in the revolving housing via a second bearing concept (B2), - The two bearing concepts (B1, B2) implement different bearing principles; - the coupling planets (K1; K2) of a coupling planet group engaging in a common sun gear (S1; S2) according to one of the bearing designs (B1, B2) are supported with radial play of the tip circle in relation to the rotating housing (GH) and - the coupling planets (K2; K1) the coupling planet group engaging in the other sun gear (S2; S1) according to the other bearing concept (B2; B1) are mounted radially in the revolving housing (GH) via their tip circular surfaces.

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