Universal joint for a steering shaft of a motor vehicle

Abstract

Universal joint (5) for a steering shaft (23, 25) of a motor vehicle, comprising a universal joint (55) with two pairs of pins (56) arranged at right angles to each other and two joint forks (51, 53) connectable to the steering shaft (23, 25), each with two opposing arms (52, 54) in which a pin (56) is rotatably mounted about a pin axis (Z) in a pin bearing (6), which has a cup-shaped outer bushing (61) fixed in the arm (52, 54) with an outer cup base (611) opposite the end face of the pin (56), wherein rolling elements (63) are arranged between the pin (56) and the outer bushing (61), and wherein a convexly projecting contact area (58, 64) is arranged on the end face of a pin (56), which forms the outer cup base (611) contacted, wherein an inner bushing (62) is fixed on the pin (56), wherein the rolling elements (63) are arranged between the inner bushing (62) and the outer bushing (61),and the contact area (58, 64) projects axially towards the end face relative to the inner sleeve (62), characterized in that the inner sleeve (62) is designed in a pot shape as an inner pot (62) with an end face inner pot base (621) which has the contact area (64).

Description

State of the art The invention relates to a universal joint for a steering shaft of a motor vehicle, comprising a joint cross with two pairs of pins arranged at right angles to each other and two joint forks connectable to the steering shaft, each with two opposing arms, in which a pin is rotatably mounted about a pin axis in a pin bearing, which has a cup-shaped outer bushing fixed in the arm with an outer pot bottom opposite the end face of the pin, wherein rolling elements are arranged between the pin and the outer bushing, and wherein a convexly projecting contact area is arranged on the end face of a pin, which contacts the outer pot bottom, wherein an inner bushing is fixed on the pin, wherein the rolling elements are arranged between the inner bushing and the outer bushing, and the contact area projects axially relative to the inner bushing at its end face. In a motor vehicle, the steering shaft transmits the steering torque applied to the steering wheel via the steering spindle and intermediate shaft to the steering gear. To compensate for angular misalignment, at least one, and usually two, universal joints are integrated along the steering shaft, typically between the steering spindle and intermediate shaft, and between the intermediate shaft and steering gear. In its basic design, each joint has two articulated forks, each attached to one end of the shaft. Each articulated fork has two arms extending in the direction of the shaft and positioned opposite each other transversely to the shaft axis. A joint cross has two pairs of radially projecting joint pins, referred to simply as pins, arranged on right-angled, intersecting pin axes. The two pins of each pair are rotatably mounted in a pin bearing within one arm of an articulated fork, about their pin axis, which extends transversely through the arms and is perpendicular to the shaft axis. The pin bearings are designed as radial roller bearings, typically radial needle roller bearings. The articulated cross has a base body which, to reliably absorb the high forces that occur, is preferably designed as a cold-forged steel part or from another high-strength material, as described in the prior art, for example, in DE 10 2014 116 271 A1. This patent proposes that, for the radial bearings, the needles roll between rolling element raceways, which are formed directly on the outer surface of the base body and in an outer bushing connected to the arm. The outer bushing is cup-shaped, forming an outer pot that is fixed in an arm and into which the journal extends, so that its end face is opposite the bottom of the outer bushing, the outer pot bottom. To achieve the smoothest possible operation and the highest possible stiffness of the joint arrangement during operation, DE 10 2014 116 271 A1 proposes axially preloading the bearing. This is achieved by the pin having a convex end face which, under elastic preload, slides against the outer cup base of the outer bushing in a contact area. An elastic deformation of the outer cup base outwards in the axial direction of the pin axis results in the outer bushing exerting a permanent elastic preload force on the pin pair. Axial preloading effectively increases stiffness. However, this requires high-precision machining of the journals in the area of ​​the rolling element raceways, which is complex. Furthermore, the convex end face shortens the axial area of ​​the journal available for the rolling element raceway, thus reducing the width of the raceway and limiting the permissible bearing load of the journal bearing. While the journal could be lengthened axially to increase the permissible bearing load, the possible lengthening is limited by the given distance between the arms of the pivot fork, as increasing the journal length makes inserting the pivot cross into the pivot fork difficult or impossible. A similar joint arrangement is described in DE 10 2009 016 169 B4, in which a centering element is elastically clamped axially between the end face of the journal and the outer cup base. This also shortens the axial area of ​​the journal usable as a rolling element raceway and limits the bearing load. A universal joint of the type mentioned above is known from US 2007 / 0 087 846 A1. In view of the problem explained above, it is an object of the present invention to provide a joint arrangement which allows a higher bearing load in the case of a pre-tensioned mounting of a joint cross. Description of the invention This problem is solved according to the invention by a universal joint having the features of claim 1. Advantageous further developments are set out in the dependent claims. According to the invention, a universal joint for a steering shaft of a motor vehicle is comprised of a joint cross with two pairs of pins arranged at right angles to each other and two joint forks connectable to the steering shaft, each with two opposing arms in which a pin is rotatably mounted about a pin axis in a pin bearing, which has a cup-shaped outer bushing fixed in the arm with an outer pot bottom opposite the end face of the pin, wherein rolling elements are arranged between the pin and the outer bushing, and wherein a convexly projecting contact area is arranged on the end face of a pin, which contacts the outer pot bottom, wherein an inner bushing is fixed on the pin, wherein the rolling elements are arranged between the inner bushing and the outer bushing, and the contact area projects axially relative to the inner bushing at its end face,that the inner box is pot-shaped, forming an inner pot with an inner pot base at the front, which has the contact area. Preferably, the convexly protruding contact area of ​​the pin contacts the inner bushing, particularly preferably the bottom of the inner bushing. The outer casing, as is known in the first place, is designed as an outer pot, in which a hollow cylindrical tubular outer sleeve is closed at the end by an outer pot bottom. The inner sleeve has a hollow cylindrical, tubular casing, which is preferably permanently and coaxially attached to the pin, for example by press-fitting, thereby creating a firm and rigid force-fit connection. The connection can additionally or alternatively be material-bonded, for example by adhesive bonding, and additionally or alternatively form-fit, for example by riveting the sleeve to the pin, or by interlocking form-fit structures such as knurling or roughening, which can also be permanently joined together by plastic deformation during press-fitting. Because the connection is rigid, the inner sleeve is fixed radially and axially immovably on the pin and thus precisely positioned. On its radial outer surface, the sleeve has an outer cylindrical surface which, measured along its axial width in the direction of the journal axis, can be used as a rolling element raceway. Preferably, the inner bushing can be made of bearing steel and at least partially hardened and / or provided with a hard coating in the area of ​​the rolling element raceway, thereby ensuring low-backlash, smooth, and low-wear operation of the rolling bearing. A particular advantage results from the fact that the contact area of ​​the inventive combination of the inner bushing with the journal projects axially at the end face, i.e., viewed from the inner bushing in the direction of the journal axis, relative to the inner bushing. The convex contact area projects particularly beyond the area of ​​the inner bushing designed as a rolling element raceway. While in the prior art the area usable as a rolling element raceway on the journal is axially shortened by the forming of the journal to create the convex contact area, the invention makes it possible to realize a rolling element raceway with a greater axial width on such a journal through the inner bushing than would be possible with a rolling element raceway arranged directly on the journal.The sleeve of the inner bushing, whose axial width determines the maximum axial width of the rolling element raceway, can have a larger dimension in the direction of the journal axis than the potentially usable cylindrical outer circumference of the journal as a rolling element raceway. The sleeve of the inner bushing can extend axially into the convexly converging area at the end face of the journal, with the contact surface projecting axially beyond the rolling element raceway at its outermost point. This allows for a higher permissible bearing load for a given journal length with a convex end-face contact surface. Preferably, the outer pot base and the convexly projecting contact area of ​​the pin are spaced apart by a gap, with contact between the pin and the outer pot base occurring at least temporarily. An advantageous embodiment of the invention provides that the inner bushing is designed in a pot shape, forming an inner pot with an end face containing the contact area. The inner pot has a hollow cylindrical sleeve, which, as described above, includes the rolling element raceway and is closed at its end face by the inner pot base. The inner pot, with its opening facing away from the end face, also referred to as the pot opening, is axially fitted onto the pin. Preferably, the outer cup base and the convexly projecting contact area of ​​the pin only come into direct contact once the inner bushing is deformed towards the outer bushing. This results in better radial support and improved force transmission. The contact between the pin and the outer pot base and / or between the pin and the inner pot base and / or between the end face of the inner pot base and the outer pot base can preferably occur simultaneously, so that a double contact can temporarily exist. The contact area is not formed on the main body of the pin itself, as in the prior art, but rather on the inner bushing mounted on the pin. This results in the previously described advantage that the axial width usable as a rolling element raceway can be increased. A further advantage is that expanded possibilities are available for the design and functional optimization of the contact area. For example, the inner bushing is easier to shape and form compared to a solid pin, for instance, by manufacturing it as a thin-walled sheet steel part, which can be produced efficiently and precisely by pressing, deep drawing, and other known cold and hot forming processes. This allows for a high degree of design freedom in specifying the local wall thickness and individually adapted shapes of the sleeve and cup base.The contact area can be achieved, for example, by plastically pressing in the inner pot base, which requires less manufacturing effort than forming a convex end face of a solid pin. The contact area is centrally located on the pin axis and is smaller than the open inner cross-section of the inner bushing, which essentially corresponds to the cross-section of the pin. Furthermore, the material selection can be independent of the pin material. As described above, partial hardening can be applied to the sleeve area, for example, to optimize the rolling element raceway. Similarly, partial hardening, surface treatment, coating, or the like can be applied to the cup base to reduce sliding friction in the contact area with the outer bushing. This allows for easier optimization of the contact area's shape and functional properties than is possible when shaping the pin itself. Furthermore, it is possible for the first time to implement elastic properties in the inner bushing to preload the articulating cross in the articulated fork, as explained below. Preferably, the contact area on the inner cup is axially resilient. The contact area is convexly shaped and protrudes outwards from the cup base in the direction of the pin axis. Through an adapted shape, material composition, and wall thickness, the inner bushing can be axially elastic, so that the contact area located on the cup base is resilient relative to the sleeve attached to the pin with respect to pressure on the end face relative to the pin. In contrast to the prior art, the inner bushing itself forms a spring element acting in the direction of the pin axis, which is connected to the pin and enables the preloaded mounting of the articulating cross between the arms of the articulated fork.Consequently, according to the invention, the inner pot has multiple functions, namely the enlargement of the rolling element raceway, as a support for the contact area and as a spring element for the elastic tensioning of the joint cross in the joint fork. The axial elasticity of the inner sleeve can be achieved by connecting the inner pot base to the sleeve in an axially resilient manner, for example by a flat design or a circumferential groove. An advantageous embodiment is that the contact area is formed by a dome formed on the inner pot base. The inner pot base can be flat, i.e., planar, to at least 50%, preferably 75% to 80%, outside the contact area. The convex shape is provided by the dome, which projects convexly outwards from the end face and can, for example, be shaped as a segment-shaped spherical projection, which may also be flattened in the area of ​​the central contact surface, or it can be frustoconical. The dome can be a plastic indentation introduced from the inside into the otherwise planar pot base, which is essentially flat perpendicular to the pin axis, and which is produced, for example, by pressing. The dome extends centrally only over a portion of the pot base and is preferably surrounded and held by the planar, annular area of ​​the pot base remaining outside the contact area.The cap itself is relatively rigid, which advantageously provides a consistently defined contact area with the outer bushing. The flat, annular area surrounding the cap can form a spring element, allowing elastic displacement of the cap relative to the sleeve and thus creating a resilient contact surface relative to the pin. The cap is preferably formed integrally with the inner bushing. Furthermore, it is conceivable and possible for the contact surface to have a corrugated structure to improve force transmission. The spring constant of the spring element can be determined by the material thickness and the relative ratio of the dimensions of the spherical cap and the flat area of ​​the pot base. To provide sufficient elasticity, it is advantageous for the contact area to be at least 50% flat, preferably 75% to 80%, which results in higher elasticity. It is also conceivable to provide additional or alternative axially elastically deformable areas in the bottom of the pot or in the sleeve, for example by means of corrugated or wave-shaped indentations, material thinnings or the like. It can be provided that the inner cup base has an axial clearance from the end face of the pin. This provides a free spring area into which the cup base can deflect axially, at least in the contact area with the end face of the pin, when the pins are inserted under preload between the arms of the articulated fork. The clearance can be dimensioned such that sufficient elastic deformation of the inner bushing can occur to generate a predetermined preload force. An advantageous embodiment of the invention provides that the outer pot base is flat. The contact area formed on the pin, or preferably on the inner sleeve, is rotatably supported on the inner surface of the pot-shaped outer sleeve about the pin axis. Because the outer pot base is flat, at least on its inner surface facing the end face of the pin, a defined contact and bearing surface is provided. The outer pot with the flat outer pot base can be manufactured efficiently with the required stiffness. The flat outer pot base primarily provides axial support and is not significantly deformed by the preload force applied via the contact areas. This is advantageous because, firstly, the external shape does not change due to the preload force, and secondly, any external influences have no effect on the preload force. The contact area can have a centrally projecting centering pin on its end face, which engages in a centering recess in the outer bushing. This ensures the coaxially centered bearing of the pin or inner bushing relative to the outer bushing with respect to rotation about the pin axis. The inner bushing may be designed with an outwardly projecting flange section. This flange section may be collar-shaped and circumferential around the edge of the rear opening of the inner bushing, into which the pin engages. The flange section provides an axial sealing surface against which an elastic sealing element can abut to seal against the outer bushing. It is also possible for the outer cup to have a radially projecting retaining projection. This retaining projection can preferably extend inwards from the outer sleeve at the edge of the outer cup's opening, gripping and holding the rolling elements. Furthermore, a sealing element, for example a sealing ring, can be arranged between sealing surfaces on the retaining projection and an outwardly projecting flange section of the inner bushing to seal the bearing interior in which the rolling elements are located. Preferably, the inner bushing can be connected to the pin and / or the outer bushing to the arm by frictional, positive, and / or material-bonded connection. A frictional connection can be achieved by pressing the inner bushing onto the pin or pressing the outer bushing into an opening of the fork. To create a positive connection, for example, a local plastic deformation can be produced by riveting, against which the inner or outer bushing rests on the pin or fork. A material-bonded connection can include gluing, welding, or the like. Description of the drawings Advantageous embodiments of the invention are explained in more detail below with reference to the drawings. Specifically, Fig. 1 shows a steering column in a schematic perspective view, Fig. 2 shows a universal joint of a steering column according to Fig. 1 in a schematic perspective view, Fig. 3 shows a longitudinal section through a pivot bearing of a universal joint according to Fig. 2 in a first embodiment according to the invention, Fig. 4 shows a longitudinal section through a pivot bearing of a universal joint according to Fig. 2 in a second embodiment according to the invention, Fig. 5 shows a longitudinal section through a pivot bearing of a universal joint according to Fig. 2 in a third embodiment according to the invention, Fig. 6 shows a longitudinal section through a pivot bearing of a universal joint according to Fig. 2 in a fourth embodiment according to the invention, Fig. 7 shows a longitudinal section through a pivot bearing of a universal joint according to Fig. 2 in a fifth embodiment according to the invention.8 a partially separated view of the universal joint according to Fig. 2 in the first embodiment according to Fig. 3, Fig. 9 a longitudinal section through a pivot bearing of a universal joint according to the invention according to Fig. 2 in a sixth embodiment, Fig. 10 a partially separated view of the universal joint according to Fig. 7, Fig. 11 a partially separated view of the universal joint according to Fig. 5 . Embodiments of the invention In the various figures, identical parts are always marked with the same reference symbols and are therefore usually only named or mentioned once. Fig. 1 shows a steering column 1 according to the invention schematically in a perspective view obliquely from behind (relative to the direction of travel of a motor vehicle not shown). The steering column 1 comprises an actuating unit 2 with a sleeve unit 21 in which a sleeve tube 22 is received. A steering spindle 23 is rotatably mounted in the sleeve unit 21 about a longitudinal axis L. The steering spindle 23 forms a rear or upper part of the steering shaft and has a connection section 24 at its rear end for a steering wheel (not shown). The actuating unit 2 is pivotably mounted in its front area on a support unit 3, which can be attached to a body of a motor vehicle (not shown), in a pivot bearing 31 about a horizontal pivot axis, so that the steering spindle 23 can be pivoted in a vertical direction H for adjusting the height of the steering wheel in the area of ​​the connecting section 24. At the rear of the actuating unit 2, a clamping device 4 is located at a distance from the pivot bearing 31. Actuating a clamping lever 41 allows the actuating unit 2 to be releasably clamped to the support unit 2, thus fixing the set height adjustment. Releasing the clamping device 4 also allows the outer tube 22 to be telescopically adjusted relative to the outer tube 21 for longitudinal adjustment. When the clamping device 4 is locked, the outer tube 22 is also releasably clamped in the outer tube 21, thereby fixing the longitudinal adjustment. At its front end, which protrudes to the left from the outer casing unit 21 in Fig. 1, the steering spindle 22 is pivotally coupled to an intermediate shaft 52 via a universal joint 5, which is rotatable about a shaft axis W inclined to the longitudinal axis L. The joint 5 has a first joint fork 51, which is rigidly connected to the steering spindle 22 and has two arms 52 opposite each other with respect to the longitudinal axis L. A similarly constructed joint fork 53 is attached to the intermediate shaft 25, which has two arms 54 opposite each other with respect to the shaft axis W. The articulated forks 51 and 53 are connected to each other by means of a joint cross 55, also called a pivot cross. Fig. 2 shows an enlarged view of the joint 5, with only the joint fork 51 depicted for clarity. The joint cross 55 has two pairs of oppositely projecting radial pins 56, also referred to as joint pins, which are arranged on right-angled intersecting pin axes Z and Y. The two pins 56 of each pair are each rotatably mounted in a pin bearing 6 in an arm 52, 54 of a joint fork 51, 53 about their pin axes Z and Y, respectively, which extend transversely to the longitudinal axis L and the shaft axis W through the arms 52 and 54, respectively. Since the invention relates to the design of the pivot bearings 6, and the first arrangement in the arms 52 of the fork 51 is essentially identical to the second arrangement in the arms 54 of the articulated fork 53, only the reference numerals of the first arrangement are mentioned below, whereby the second arrangement is implicitly included. Fig. 3 shows a section along the pin axis Z through the joint cross 55. It can be seen that the pin 56 is formed integrally with a base body of the joint cross 55, which is preferably manufactured as a cold-pressed steel part. The pivot bearing 6 has an outer bushing designed as an outer pot 61, with a substantially flat outer pot base 611 that closes a cylindrical outer sleeve 612 at its end face. The outer sleeve 612 is firmly connected to the arm 52, for example by being pressed into an opening 521. An inner sleeve designed as an inner pot 62 has a tubular inner sleeve 622 which is firmly attached to the pin 56, for example by being pressed on, and which is closed at its end face by an inner pot bottom 621 and, on the other hand, in the unpreloaded state, is axially spaced from the end face of the pin 56 by a gap 600, via a projection 58 of the pin 56 which serves as a contact area. The pivot bearing 6 is designed as a radial rolling bearing, wherein cylindrical needles are arranged to roll between the rolling element raceways formed on the inner surface of the outer sleeve 612 and the outer surface of the inner sleeve 622 as rolling elements 63. The inner pot base 621 has a convexly projecting contact area 64 on its end face, which rests against the outer pot base 611 from the inside. In the example shown, the contact area 64 is designed as a frustoconical cap, which is axially spring-elastically connected to the inner sleeve 622 by the inner pot base 621 in the direction of the pin axis Z. This allows the contact area 64 to deflect axially elastically in the direction of the pin axis Z against the spring force exerted by the inner pot base 621 against the end face of the pin 56, thereby clamping the pin 56 elastically against the outer pot base 611 in the direction of the pin axis Z. In the illustration of Fig. 3, the spring force exerted by the axially elastic inner pot 62 via the contact area 64 pushes the joint cross 55 to the right, so that the end face of the joint cross 55, in particular via the projection 58, is in direct contact with the bottom of the inner pot 621. A correspondingly equal spring force directed to the left is exerted by the pivot bearing formed in a mirror image on the other, opposite pin 56 of the pair, so that the joint cross is elastically clamped between the arms 52 of the joint fork 51 by this spring force. The interior of the journal bearing 6, which receives the needles 63, is sealed to the outside by an elastomer sealing ring 7, which is axially located between a collar-like radially outwardly projecting flange 65 on the inner sleeve 622 and a retaining projection 66 projecting inwards from the outer sleeve 612. Fig. 8 shows the individual components isolated in an exploded view. Fig. 4 shows an embodiment as in Fig. 3, in which the arm 52 has the rivets 57 which form plastic deformations for the positive locking fixation of the outer pot 61 in the opening 521 and, unlike Fig. 3, shows a pre-tensioned pin bearing 6. The embodiment shown in Fig. 5 essentially corresponds to the embodiment according to Fig. 3 or Fig. 4. In this embodiment, the inner pot 62 has, in the area of ​​the contact surface, an additional central centering pin 67 projecting axially at its end face. This pin is rotatably mounted about the pin axis Z in a corresponding recess 613. The end face of the pin is axially spaced from the inner pot base 621 by the gap 600. The centering pin 67 acts as the contact area with the outer pot base 611. Fig. 11 shows the individual components isolated in an exploded view. It is shown that at least one pin 56 has a flat or planar contact surface 56a onto which the inner bushing 62 is pressed. Fig. 6 shows a possible further development of the embodiments shown in Fig. 3, Fig. 4, or 5, in which connecting means 68 are arranged in the area of ​​the connecting surface between the arm 52 and the outer pot 61 on the inner surface of the opening 521 and / or on the outer surface of the outer pot 61, for example positive locking elements such as knurling, roughening or the like. In the alternative embodiment according to Fig. 7, the inner sleeve 62 is designed as an inner sleeve 622 open on both sides, which therefore has no inner pot bottom at its end face. The convexly projecting contact area 64 is arranged on a centrally projecting projection 58 of the pin 56 at its end face. The projection 58 is integrally formed with the pin 56 and projects from the inner sleeve 622 at its end face, bearing against the outer pot bottom 611. The outer pot bottom 611 can be designed to be axially spring-like in the direction of the pin axis Z. Fig. 10 shows the individual components isolated in an exploded view. The projection 58 of the pin 56 serves as a centering element for the outer bushing 61. Figure 9 shows a possible further development of the embodiments depicted in Figures 3, 4, or 5, wherein the inner pot bottom 621 is axially spaced from the projection 58 of the pin 56 by a gap 600 and abuts the outer pot bottom 611. The pot bottom of the inner pot 62 is corrugated and, in the preloaded state, abuts both the outer pot bottom 611 and the projection 58 of the pin. Reference symbol list 1 Steering column 2 Actuating unit 21 Sleeve unit 22 Sleeve tube 23 Steering spindle 24 Connection section 25 Intermediate shaft 3 Support unit 31 Swivel bearing 4 Clamping device 41 Clamping lever 5 Universal joint 51, 53 Joint fork 52, 54 Arm 521 Opening 55 Joint cross (pin cross) 56 Pin (joint pin) 57 Rivet 58 Projection 6 Pin bearing 61 Outer cup 611 Outer cup base 612 Outer sleeve 613 Recess 62 Inner cup 621 Inner cup base 622 Inner sleeve 63 Rolling element 64 Contact area 65 Flange 66 Retaining projection 67 Centering mandrel 68 Fastener 7 Sealing ring L Longitudinal axis W Shaft axis Z, Y Pin axis

Claims

Universal joint (5) for a steering shaft (23, 25) of a motor vehicle, comprising a universal joint (55) with two pairs of pins (56) arranged at right angles to each other and two joint forks (51, 53) connectable to the steering shaft (23, 25), each with two opposing arms (52, 54) in which a pin (56) is rotatably mounted about a pin axis (Z) in a pin bearing (6), which has a cup-shaped outer bushing (61) fixed in the arm (52, 54) with an outer cup base (611) opposite the end face of the pin (56), wherein rolling elements (63) are arranged between the pin (56) and the outer bushing (61), and wherein a convexly projecting contact area (58, 64) is arranged on the end face of a pin (56), which forms the outer cup base (611) contacted, wherein an inner bushing (62) is fixed on the pin (56), wherein the rolling elements (63) are arranged between the inner bushing (62) and the outer bushing (61),and the contact area (58, 64) projects axially towards the end face relative to the inner sleeve (62), characterized in that the inner sleeve (62) is designed in a cup shape as an inner pot (62) with an end face inner pot base (621) which has the contact area (64). Universal joint according to claim 1, characterized in that the contact area (64) on the inner pot (62) is axially resilient. Universal joint according to one of claims 1 to 2, characterized in that the contact area (64) is formed by a calotte formed on the inner pot bottom (621). Universal joint according to claim 3, characterized in that the inner pot bottom (621) is flat to at least 50%, preferably to 75% to 80% outside the contact area (64). Universal joint according to one of claims 3 or 4, characterized in that the inner pot bottom (621) has an axial distance to the end face of the pin (56). Universal joint according to one of the preceding claims, characterized in that the outer pot base (611) is planar. Universal joint according to one of the preceding claims, characterized in that the inner bushing (62) has an outwardly projecting flange section (65). Universal joint according to one of the preceding claims, characterized in that the outer cup (61) has a radially projecting retaining projection (66). Universal joint according to one of the preceding claims, characterized in that a sealing element (7) is arranged between the outer pot (61) and the inner bushing (62). Universal joint according to one of the preceding claims, characterized in that the inner bushing (62) is connected to the pin (56) and / or the outer bushing (61) to the arm (52, 54) by frictional locking and / or form locking and / or material locking.

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