WO2009156516A1

WO2009156516A1 - Tripod joint for a motor vehicle and method for the production thereof

Info

Publication number: WO2009156516A1
Application number: PCT/EP2009/058074
Authority: WO
Inventors: Luis Hoeks; Jessica Andresen; Christian Felchner
Original assignee: Tedrive Holding B.V.
Priority date: 2008-06-27
Filing date: 2009-06-26
Publication date: 2009-12-30
Also published as: DE102008030151A1

Abstract

The invention relates to a tripod joint (1) for a motor vehicle, comprising a tripod star (40) forming a plurality of journals (42), a plurality of rolling bearings (60) carried by the journals (42) of the tripod star (40), and an outer joint (20) having a plurality of raceway recesses (22) extending in the axial direction, in each of which a rolling bearing (60) carried by a journal (42) is supported displaceably in the axial direction, wherein two raceways (24) disposed opposite each other are designed in each raceway recess (22) for mechanical contact with the rolling bearing (60) guided therein. The outer joint is characterized in that the rolling bearings (50) each have an outer ring (64), in the outer circumferential surface of which a circumferential annular groove (66) is designed. In the raceways (24) a rail-like guide element (26) is designed, which engages in the annular groove (66) designed on the outer ring (64), wherein during rolling of a rolling bearing (60) on a raceway (24) at least three point contacts are formed between the outer ring (64) and raceway (24).

Description

Designation: Tripod joint for a motor vehicle and method for its production

The present invention is a tripod joint for a motor vehicle according to the preamble of claim 1 and a method for producing a tripod joint according to the preamble of claim 18.

Automotive tripod joints have long been known in the art, and are particularly used as inner joints for the drive shafts of front wheel drive motor vehicles. They have excellent synchronous characteristics and can be angled up to angles of typically over 10 °. In addition, tripod joints can be advantageously used for propshafts rear-wheel drive or four-wheel drive motor vehicles.

Tripod joints typically have a tripod star forming a plurality of pins, each pin carrying a rolling bearing. Furthermore, a tripod joint comprises an outer joint, which is often referred to as "tulip", wherein the outer joint has a plurality of in the axial direction, ie in the direction of rotation D of the outer race extending Laufbahnausnehmungen.In each Laufbahnausnehmung a rolling bearing supported by a pin is slidably mounted in the axial direction Each raceway recess forms two oppositely arranged raceways for mechanical contact with the rolling bearing guided therein.

Although the basic construction of the tripod joints, which are also known as "homokinetic joints", has long been known, nevertheless great efforts are still being made to improve the running properties of tripod joints, for example during load change processes DE 41 301 83 A1 discloses a tripod joint in which a special design of the raceways in the raceway recesses and the outer rings of the rolling bearings prevents tilting of the rolling bearing outer ring in the raceway recess, for example during a load introduction or a load change only comes to rest on on a track of the raceway recess, so that the outer ring can roll friction in the Laufbahnausnehmung. Also EP 1 253 337 A1 discloses a homokinetic joint with reduced rotational play. Both the raceways of the Laufbahnausnehmungen and the surface of the rolling bearing outer ring are designed spherical. Furthermore, the rolling bearing outer ring is divided into two parts.

Both Tripodegelenken is a relatively complex configuration of the bearings together, which brings cost disadvantages.

Object of the present invention is therefore to provide a tripod joint with advantageous operating characteristics, in particular with minimal rotational clearance, which has a simplified structure. Furthermore, a method for producing an advantageous tripod joint is to be specified.

This object is achieved by a tripod joint with the features of claim 1 and by a method according to claim 18.

An inventive tripod joint is provided for a motor vehicle, in particular for the drive shaft of a front wheel drive motor vehicle. It includes a tripod star, which forms a plurality of cones. Each of the pins of the tripod star carries a rolling bearing. Furthermore, the tripod joint comprises an outer joint, which has a plurality of axially extending raceway recesses. In each raceway recess, a rolling bearing supported by a pin in the axial direction, i. along the direction of the rotation axis D of the outer joint, slidably mounted. Each raceway recess has two oppositely arranged raceways for mechanical contact with the roller bearing guided therein. When torque is introduced into an angled tripod joint, the rolling bearings then perform an oscillating rolling motion on the raceways in the outer joint.

According to the invention it is now provided that the rolling bearings each have an outer ring, in whose outer peripheral surface a circumferential annular groove is formed. Furthermore, in each case a rail-like guide element is formed in the raceways, which engages in the annular groove formed on the outer ring. The shape of the rail-like guide element and the circumferential annular groove in the rolling bearing outer ring is chosen so that when rolling a Wälzlageraußenring be formed on a career at least three point contacts P between the outer ring and the raceway. It should be understood in the context of the present invention, a rail-like guide element, a structure which extends in the direction of the axis of rotation D of the outer joint and rises from a track. It may, for example, rise substantially in the circumferential direction of the outer joint of the raceway. Furthermore, the rail-like guide element should form at least one guide surface on which the outer ring of a roller bearing can roll. However, the rail-like guide element preferably forms two or more guide surfaces which, in the case of two guide surfaces, are arranged on opposite sides of the guide element. In a particularly preferred embodiment, the separate rail-like guide element forms at least three guide surfaces.

Due to the special design of the rolling bearing outer rings and the raceways in the outer joint effective securing of Wälzlageraußenringe is realized in the raceways against tilting at a torque introduction in the trip odgelenk. This results in a significantly reduced torsional backlash of the tripod joint according to the invention. In that the rolling bearing outer ring is secured in the raceway against tilting, can also be prevented that the rolling in the raceway rolling bearing outer ring in addition to the pure rolling movement on the track additionally performs a sliding movement. This is done by preventing the roller bearing outer ring outside the raceways of the outer joint comes to rest on this. This further results in significantly improved running properties of the tripod joint according to the invention and a significantly reduced wear.

The rolling of the rolling bearing outer ring in the raceway of the outer joint takes place particularly friction and thus wear, when the inventively designed at least three point contacts P are on a straight line L. In this case, this straight line L is preferably parallel to the axis of rotation R of the rolling bearing.

The rail-like guide elements can advantageously be formed integrally with the outer joint, for example, they can be forged in the manufacture of the outer joint with. Alternatively, it is also possible to separate the rail-like guide elements as a separate component from the outer to train the steering wheel. In this case, the rail-like guide element may be made of the same material as the outer joint, but here another material with improved wear properties, for example greater hardness, is preferably used. A separately designed rail-like guide element is mechanically fixed at least at one point to the outer joint, but preferably at a plurality of attachment points. In this case, the mechanical connection is made from the separately formed rail-like guide element with the outer joint at an attachment point, for example by means of welding, for example, welding point, caulking, soldering or gluing. In addition, all other known from the prior art joining methods can be used with which a permanently stable mechanical connection between two metal workpieces can be produced.

In a particularly preferred embodiment of the tripod joint according to the invention, the outer rings of the roller bearings form the following:

a) two sliding surfaces, which are inclined in a first direction against the rotational axis R of the rolling bearing, and on each of which a contact point Pl is formed with the raceway in the outer joint,

b) a stop surface, which is inclined in a second direction opposite to the first direction against the direction of rotation R of the rolling bearing, and on which forms another contact point P2 with the raceway in the outer joint.

At least one of the sliding surfaces of the roller bearing outer rings preferably has a circular cross section in sections. In this way, a sliding movement of the rolling bearing outer ring on the rail-like guide element in the outer joint at a torque introduction in the tripod joint can be facilitated to bring the rolling bearing outer ring in a defined position and to fix it in this. By virtue of the fact that the sliding surfaces have a circular cross-section at least in sections, the Hertzian contact stresses in the region of the contact points P can furthermore be minimized. In a further preferred embodiment of the tripod steering according to the invention, the raceways in the outer joint of the tripod joint have the following features:

a) two sliding surfaces, which are arranged opposite to the two sliding surfaces of the roller bearing outer ring, and on each of which one of the contact points Pl forms with the outer ring,

b) a stop surface, which is arranged opposite the stop surface of the outer ring, and on which the further contact point P2 forms with the raceway.

At least one of the sliding surfaces on the track in the outer joint also preferably has an at least partially circular cross-section. Particularly preferably, the radius of curvature of this sliding surface on the track in the outer joint is greater than the radius of curvature of the formed on the outer ring complementary sliding surface with partially circular cross-section. By this measure, it is possible to further minimize the Hertzian contact voltages at the contact points P.

In an alternative embodiment, at least one of the sliding surfaces on the roller bearing outer ring is configured in sections, ie. it is formed in sections as a flat pyramid shell surface. In this case, the first contact point Pl advantageously forms on this lateral surface.

Particularly preferably, a sliding surface and the stop surface of the raceway are formed in the outer joint on the rail-like guide element, in particular when the rail-like guide element is formed as a separate component. In this case, then the second sliding surface of the raceway in the outer joint i.d.R. formed by the outer joint itself. It is also conceivable, however, a corresponding shape of the rail-like guide element.

Basically, the Tripodegelenk each known from the prior art suitable shaping with respect. The pins of the tripod star or the inner rings of the rolling bearing have. In a particularly preferred embodiment, the pins of the tripod star are formed spherical, which to that effect is understood that the pins are at least partially form spherical surfaces. The complementary surfaces in the inner ring of the rolling bearing can be configured, for example, cylindrical, so that the rolling bearing has an inner ring with a cylindrical inner recess. Alternatively, it is also possible to provide the inner rings of the rolling bearing with an inner recess, the shape of which in turn is formed at least partially spherical surface. In both embodiments, the inner rings can perform a tilting movement on the pin of the Tripodesterns. In the latter embodiment, it is of particular advantage if the inner ring and the outer ring of the rolling bearing in the direction of the axis of rotation of the bearing are mutually displaceable. By contrast, such a degree of freedom of movement is not absolutely necessary if the inner ring of the roller bearing has a cylindrical inner recess, since here the spherical pin of the tripod stator can slide back and forth in the inner recess of the roller bearing inner ring.

An inventive method for producing a tripod joint for a motor vehicle comprises the following method steps:

1. Provide: a. a tripod star forming a plurality of pins, b. a plurality of rolling bearings, which are supported by the pins of the tripod star and each having an outer ring, in whose outer peripheral surface a circumferential annular groove is formed, c. an outer joint having a plurality of axially extending raceway recesses, in each of which a bearing supported by a pin bearing can be mounted displaceably in the axial direction, wherein formed in each Laufbahnausneh- mung two oppositely disposed raceways for mechanical contact with the rolling bearing guided therein are in each case, and in the raceways a rail-like guide element is formed, which can engage in the annular groove formed on the outer ring,

2. placing the bearings on the pins of the tripod esters, and

3. Introduce the bearings in the Laufbahnausnehmungen. wherein the rail-like guide elements in engagement with the circumferential annular grooves arrive, so that when rolling a rolling bearing on a track at least three point contacts between the outer ring and raceway are formed.

In a preferred development, the method according to the invention has the following additional method steps:

4. Provision of a plurality formed as separate components rail-like guide elements, and

5. Determining the rail-like guide elements on the outer joint.

Further advantages and features of the inventive Tripodege- lenk result from the subclaims and the embodiment, which is explained in more detail in the appendix of the drawing. In this show:

1 is a perspective view of a first embodiment of a tripod joint according to the invention,

2 shows a partial sectional view of the tripod joint of Figure 1,

3 shows an enlarged partial sectional view through the outer joint, roller bearings and tripod testers of the exemplary embodiment according to FIG. 1.

4 shows a perspective partial sectional view of the tripod joint

FIG. 1

5 is a perspective view of the outer joint of a tripod joint according to a second embodiment with a rolling bearing used,

6 is an enlarged partial view of Figure 5,

7 shows the view from FIG. 4 for a third exemplary embodiment of a tripod joint according to the invention, 8 is an enlarged partial view of Figure 7 in a first embodiment, and

9 shows an enlarged partial view from FIG. 7 in a second embodiment.

Figure 1 shows a schematic representation of a first embodiment of a tripod joint 1 according to the invention in a perspective view. The outer joint 20 has a rotation axis D and is open on one side. At its closed end, the outer joint 20 opens into a shaft shank 28 for connection to, for example, an output shaft of a transmission of the motor vehicle. In the outer joint 20 three Laufbahnausnehmungen 22 are formed, which extend in the direction of the axis of rotation D. Each raceway recess 22 forms two oppositely disposed raceways 24 on which roller bearings 60 inserted in the raceway recess 22 roll, of which only one is shown in FIG. 1 for reasons of clarity. The dimensioning of the bearings 60 is selected so that when a force is introduced, for example, in the outer joint 20 of the tripod joint 1, the roller bearing 60 actually rolls with its outer ring 64 only on a raceway 24 of the raceway recess 22.

As is further apparent from FIG. 1, each raceway recess 22 in the outer joint 20 is assigned a pin 42 of the tripod stator 40 inserted into the outer joint 20. The pins 42 each carry a rolling bearing 60. The tripod star 40 has an inner recess, in the inner wall of a plurality of splines 44 are formed for connecting a connecting shaft, for example, a ball displacement joint.

Preferably, the outer joint 20 and shaft shaft 28 are integrally formed as a forged part, wherein the formed in the Laufbahnausnehmungen 22 raceways 24 are subjected to the forging of the outer joint 20 further processing steps for finishing and curing.

2 shows the first embodiment of a tripod joint according to the invention 1 according to FIG 1 again in a partially sectioned view, from which the structure of the rolling bearing 60, in particular of its outer ring 64, as well as the shape of the raceway 24 of the raceway recess 22 in the outer joint 20 can be seen. The supported by the pins 42 of the tripod stator 40 bearings 60 have an inner ring 62 and an outer ring 64, between which a plurality of cylindrical rollers 68 is arranged. Inner ring 62 and outer ring 64 are displaceable relative to each other in the direction of the axis of rotation R of the rolling bearing 60. As is apparent from the sectional view of the rolling bearing 60 in Figure 2, the outer ring 64 of the rolling bearing 60 is provided with a circumferential annular groove 66. In this engages a rail-like guide member 26, which is formed in each case on the raceway 24 of the raceway recess 22. In this case, this rail-like guide member 26 may be integrally formed with the outer joint 20, but it may also be formed as a separate component, for example in the form of an insert which each inserted into a trained in the raceway 24 of the Laufbahnausnehmung 22 receiving recess 25 and preferably mechanically fixed there is. In the exemplary embodiment shown in FIGS. 1 and 2, the rail-like guide element 26 is formed integrally with the forged outer joint 20.

As can also be seen from FIG. 2, the pins 42 of the tripod star 40 have spherical surface sections 43. At the same time, the inner recess 62 of the inner ring 62 is formed partially spherical, so that the pin 42 supported by the inner ring 62 of the rolling bearing 60 and thus this total can perform a tilting movement about the pin 42.

In the first exemplary embodiment according to FIGS. 1 to 4, only one rail-like guide element 26 is formed in the raceways 24 of the raceway recess 22 in the outer joint 20, as can be seen again in detail from FIG. At the same time only a circumferential annular groove 66 is formed in the outer ring 64 of the rolling bearing 60, in which the rail-like guide member 26 engages. Due to the special shape of the raceway 24 and the outer peripheral surface of the outer ring 64 of the rolling bearing 60 arise when rolling the roller bearing 60 on the track 24 mech. Contacts only between the outer ring 64 and the raceway 24. These are marked in Figure 3 with Pl or P2. All three contact points P1, P2 lie on the straight line L denoted by "L" and are at the same distance from the axis of rotation R of the rolling bearing 60, so that a pure rolling movement of the rolling bearing 60 on the track 24 is possible which the running characteristics of the tripod joint 1 according to the invention could adversely affect, is avoided.

The three contact points P1, P2 of the roller bearing outer ring 64 with the raceway 24 realized in the first exemplary embodiment of the tripod joint 1 according to the invention also ensure a position stabilization of the rolling bearing outer race 64 in the raceway 24, e.g. with a load introduction into the tripod joint 1 according to the invention. Tilting of the axis of rotation R of the rolling bearing 60 is thereby avoided. In this way it can be ensured that even with a load introduction into the tripod joint 1, mechanical contact between the roller bearing 60 and a raceway recess 22 takes place only in the rolling region of a raceway 24. A sliding application of the roller bearing outer ring 66 at this or the opposite track 24 can be safely avoided thereby. The sliding movement of the outer ring of the rolling bearing occurring in many prior art tripod joints occurring in the prior art, e.g. on the path away from the force path 24 therefore omitted in this construction.

If one imagines a situation in which the rolling bearing outer ring is not in its defined end position, but rather only two contact points P 1 in the region of the sliding surfaces 72, 82 of roller bearing outer ring 66 and raceways 24 in the outer joint 20 is formed. If the pin 42 now exerts a force directed in the direction of the arrow K in FIG. 3 onto the roller bearing inner ring 62, this is transmitted via the rollers 64 to the roller bearing outer ring 66. This force introduction results in a movement of the roller bearing outer ring in the direction of the arrow labeled "B", ie, the rolling bearing outer ring 66 slides with its sliding surfaces 72 on the sliding surfaces in the outer joint raceway 24. This sliding movement is limited by contacting the stop surfaces 74 , 84 on the roller bearing outer ring 66 and the raceway 24 in the outer joint 28, wherein the third contact point P2 between roller bearing inner ring 62 and raceway 24 forms in the outer joint 20. In this situation, which is characterized by the presence of three contact points (2x contact point Pl, lxKontaktpunkt P2), the spatial position of the roller bearing outer ring 66 is uniquely determined in the raceway recess 22 of the outer joint 20. In addition, by applying the technical teaching of DE 41 301 83 A1, it is ensured that the force introduction of the pin 42 into the shaft is up to the maximum bending angle of the tripod joint 1 according to the invention Rolling Inne nring 62 takes place so that only such a tilting moment is exerted on the roller bearing 60, which allows tilting of the rolling bearing 60 only in the direction of the axis of rotation D of the outer joint 20 out. Basically, however, it should be noted that the position of the roller bearing outer ring 66 on the track 24 is uniquely determined by the special inventive shaping of Wälzlageraußenring 66 and raceway 24 in the outer joint 20 and the formation of three points of contact Pl, P2 between Wälzlageraußenring 66 and raceway 24 and already on this Tilting of the rolling bearing in the Laufbahnausnehmung 22 is largely excluded even in the introduction of higher torques D or load change operations.

FIG. 3 furthermore shows the special shape of the roller bearing 60 and the pin 42 of the tripod star 40. In particular, the spherical surface portion 43 of the pin 42 of the tripod star 40 can be seen. With this, the spherical inner recess 63 in the inner ring 62 of the rolling bearing 60 corresponds, so that a total of a tilting movement of the axis of rotation of the rolling bearing 60 on the pin 42 is possible. The outer circumference of the roller bearing inner ring 62 and the inner circumference of the roller bearing outer ring 64 are each configured as a cylindrical surface, so that between the inner ring 62 and outer ring 64 cylindrical rollers 68 can roll. The rollers 68 are fixed in the direction of the axis of rotation R of the rolling bearing 60 in the inner ring 62 in position. By contrast, the position of the outer ring 64 on the rollers 68 is limited essentially only by a securing projection 65 which is formed at the inner end of the roller bearing outer ring 64. As a result, the roller bearing outer ring 64 is displaceable in the direction of the axis of rotation R of the rolling bearing 60 against the inner ring 62. The securing projection 65 limits the displacement movement of the outer ring 64 on the inner ring 62 and thus prevents falling apart of the supported by the pin 42 rolling bearing 60, for example, in the final assembly of the tripod joint 1 of the invention.

Figure 4 shows again the structure of the outer joint 20, the tripod star 40 and the rolling bearing 60 of the tripod joint 1 according to the invention according to the first embodiment in a perspective view.

FIG. 5 now also shows the outer joint 20 of a second embodiment of a tripod joint 1 according to the invention in a perspective representation. ment, wherein it was omitted for reasons of clarity, the Trip odestern 40 again in detail. In this embodiment, the structure of the tripod stator 40 and the rolling bearings 60 substantially corresponds to that according to the first embodiment. The second exemplary embodiment differs from the first exemplary embodiment essentially in that two circumferential annular grooves 66 are formed on the outer circumferential surface of the roller bearing outer ring 64. At the same time two rail-like guide elements 26 are formed on the track 24 in the Laufbahnausnehmungen 22 of the outer joint 20, each forming two guide surfaces and engage in the two circumferential annular grooves 66 in the rolling bearing outer ring 64. This is again clear from the enlarged detail according to FIG. 6, from which the rail-like guide elements 26 in the raceway 24 of the raceway recess 22 of the outer joint 20 can be seen. Also, the complementary circumferential annular grooves 66 in the outer ring 64 of the rolling bearing 60 can be seen. In the second embodiment according to Figures 5 and 6, the rail-like guide elements 26 are integrally formed with the outer joint 20, for example, forged.

This differs from the embodiment according to FIG. 7 in that the rail-like guide elements 26 are designed as separate components of the outer joint 20. These are placed in complementary, in the direction of rotation D of the outer joint 20 extending receiving recesses 25 in the raceway 24 and mechanically fixed there, for example by means of one or more welds. The rail-like guide elements 26 may consist, for example, of hardened round steel.

In the exemplary embodiments according to FIGS. 6 and 7, the rail-like guide elements 26 each partially have a circular arc-shaped cross section. Likewise, the circumferential annular grooves 66 formed in the roller bearing outer ring 64 have, in sections, a circular arc-shaped cross section. In this case, the radius of curvature of the arcuate portion of the rail-like guide element 26 is at most as large as the radius of curvature of the circumferential annular groove 66 in the rolling bearing outer ring 64, but preferably smaller than the radius of curvature. The latter embodiment is shown in Fig. 8 as an enlarged view of Figure 7. This results in a minimized Hertzian contact voltage at the contact points P between the rail arm In the exemplary embodiments according to FIGS. 5 to 7, two contact points P are formed in the region of each circumferential annular groove 66, each with a rail-like guide element 26 engaging in the annular groove 66, so that a total of between the roller bearing outer ring 64 and the Runway 24 of the outer joint 20 each four contact points P occur. In this case, these contact points P are preferably again on a straight line which is oriented parallel to the axis of rotation R of the rolling bearing 60. Provided that four contact points P are provided, a further stabilization of the roller bearing outer ring 64 against tilting, for example when force is introduced into the tripod joint 1, is prevented, so that a pure rolling movement of the rolling bearing outer ring 64 on a raceway 24 of a raceway recess 22 is ensured. This in turn leads to particularly advantageous running properties of the tripod joint 1 according to the invention.

In an alternative embodiment, which is shown in FIG. 9, the structure of the tripod joint 1 essentially corresponds to that shown in FIGS. 5 and 7. Here too, the rail-like guide elements 26 designed as separate components have, in sections, a circular-arc-shaped cross-section. On the other hand, the peripheral annular grooves 66 formed in the outer ring 64 of the roller bearing 60 do not have a sectionally circular-arc-shaped cross-section, but rather a Gothic shape is selected here for the annular grooves. As has already been explained, this is to be understood as two mutually inclined spherical surface sections, which enclose with one another an angle α which lies between 45 ° and 170 °, preferably between 90 ° and 150 °.

Claims

claims

1. Tripod joint 1 for a motor vehicle, with a. a tripod stator 40 which forms a plurality of pins 42, b. a plurality of rolling bearings 60 carried by the pins 42 of the tripod stator 40, c. an outer joint 20 having a plurality of axially extending Laufbahnausnehmungen 22, in each of which a supported by a pin 42 rolling bearing 60 is slidably mounted in the axial direction, wherein in each Laufbahnausnehmung 22 two oppositely disposed raceways 24 for mechanical contact with the therein guided rolling bearings 60 are formed,

characterized in that

d. the rolling bearings 60 each have an outer ring 64, in whose outer peripheral surface a circumferential annular groove 66 is formed, e. in the raceways 24 each have a rail-like guide member 26 is formed, which engages in the formed on the outer ring 64 annular groove 66, wherein at a rolling of a rolling bearing 60 on a track 24 at least three point contacts between the outer ring 64 and raceway 24 are formed.

2. Tripod joint 1 according to claim 1, characterized in that the three point contacts lie on a line L.

3. tripod joint 1 according to claim 1, characterized in that the line L is parallel to the axis of rotation R of the rolling bearing 60.

4. tripod joint 1 according to claim 1, characterized in that the outer ring 64 forms the following: a. two sliding surfaces 82 in a first direction against the

Rotary axis R of the rolling bearing 60 are inclined and on each of which a contact point Pl is formed with the raceway 24, b. a stop surface 84, which is inclined in a second direction opposite to the first direction against the rotation axis R of the rolling bearing 60 and on which a further contact point P2 with the raceway 24 is formed.

5. tripod joint 1 according to claim 4, characterized in that at least one of the sliding surfaces 82 sections has a circular cross-section.

6. tripod joint 1 according to claim 4, characterized in that the raceway 24 forms the following: a. two sliding surfaces 72, which are arranged opposite the two sliding surfaces 82 of the outer ring 64 and on each of which one of the contact points Pl forms with the outer ring 64, b. a stop surface 74, which is arranged opposite the stop surface 84 of the outer ring 64 and on which the further contact point P2 with the raceway 24 is formed.

7. tripod joint 1 according to claim 5 and 6, characterized in that at least one of the sliding surfaces 72 sections has a circular cross-section whose radius of curvature is greater than the radius of curvature of the outer ring 64 formed at least one sliding surface 82 with sections of circular cross-section.

8. tripod joint 1 according to claim 5, characterized in that at least one of the sliding surfaces 82 sections a planar pyramid shell surface.

9. tripod joint 1 according to claim 4, characterized in that a sliding surface 72 and the stop surface 74 are formed on the rail-like guide member 26.

10. tripod joint 1 according to claim 1, characterized in that the pins 42 are at least partially spherical. ll.Tripodegelenk 1 according to claim 1, characterized in that the rolling bearings 60 have an inner ring 62 with a cylindrical inner recess.

12.Tripodegelenk 1 according to claim 1, characterized in that the rolling bearings 60 have an inner ring 62 with an inner recess whose shape is at least partially spherical surface.

13.Tripodegelenk 1 according to claim 1, characterized in that at least one rail-like guide member 26 is formed integrally with the outer joint 20.

14.Tripodegelenk 1 according to claim 1, characterized in that at least one rail-like guide member 26 is formed as a separate component.

15.Tripodegelenk 1 according to claim 14, characterized in that the separately formed rail-like guide member made of a different material than the outer joint 20th

16.Tripodegelenk 1 according to claim 15, characterized in that the separately formed rail-like guide element is mechanically fixed to the outer joint 20 at at least one point.

17.Tripodegelenk 1 according to claim 16, characterized in that the mechanical connection of the separately formed rail-like guide member is made with the outer joint 20 by means of welding, caulking, soldering or gluing.

18. A method for producing a tripod joint 1 for a motor vehicle, comprising the following method steps: a. Provide: i. a tripod stator 40 which forms a plurality of pins 42, ii. a plurality of rolling bearings 60, which are supported by the pins 42 of the tripod star 40 and each one Outer ring 64 have, in whose outer peripheral surface a circumferential annular groove 66 is formed, iii. an outer joint 20 having a plurality of axially extending Laufbahnausnehmungen 22, in each of which a supported by a pin 42 rolling bearing 60 is slidably mounted in the axial direction, wherein in each Laufbahnausnehmung 22 two oppositely disposed raceways 24 for mechanical contact with the therein guided rolling bearing 60 are formed, and in the raceways 24 each have a rail-like guide member 26 is formed, which engages in the formed on the outer ring 64 annular groove 66, b. Placing the rolling bearings 60 on the pins 42 of the tripod star 40, and c. Introducing the bearings 60 in the Laufbahnausnehmungen 22. wherein at a rolling of a rolling bearing 60 on a track 24 at least three point contacts between the outer ring 64 and raceway 24 are formed.

19. The method according to claim 18, characterized by the following further method steps: a. Providing a plurality of rail-like guide elements formed as a separate component, and b. Determining the rail-like guide elements on the outer joint 20th