Multi-ball-pin type universal joint

Abstract

The invention relates to a multi-ball-pin universal joint (1), comprising: a universal joint outer part (2) having a first longitudinal axis (3) and a cavity (4) extending parallel to the first longitudinal axis (3) and having an open end (5), at least two recesses (7) extending parallel to the first longitudinal axis (3) being formed in the universal joint outer part (2) distributed in a circumferential direction (6) extending around the first longitudinal axis (3); and a joint inner part (8) having a second longitudinal axis (9), comprising at least one central body (10) on which at least two trunnions (11) are molded, said trunnions having trunnion axes (12) extending radially from the second longitudinal axis (9), a rolling body (13) being arranged on each trunnion (11), said rolling body being at least rotatable about the trunnion axis (12).

Description

TECHNICAL FIELD

[0001] The invention relates to a multipode goniometer having a goniometer outer part and a goniometer inner part, the goniometer inner part having a center body with at least two molded trunnions. On each trunnion, a rolling body is arranged. Furthermore, the invention relates to a motor vehicle having such a multipode goniometer. BACKGROUND

[0002] A multipode goniometer is in particular a bipode goniometer having exactly two trunnions, which are in particular offset at an angle of 180 degrees, that is to say, they are molded opposite one another on the center body. As an alternative, a multipode goniometer is a tripode goniometer having exactly three trunnions, which are in particular molded on the center body offset at an angle of 120 degrees relative to one another. The following embodiments are in particular suitable for all such goniometer types, taking into account the different number of trunnions.

[0003] A tripode goniometer of this type generally comprises a goniometer outer part having a first longitudinal axis and a cavity having an open end extending parallel to the first longitudinal axis, wherein three recesses extending parallel to the first longitudinal axis are formed in the goniometer outer part. Furthermore, the tripode goniometer comprises a goniometer inner part having a second longitudinal axis, which comprises at least one center body on which three trunnions are molded, which have trunnion axes extending radially from the second longitudinal axis. On each trunnion, a rolling body is arranged, which has at least an outer ring and an inner ring rotatable relative to the outer ring about a common axis of rotation, and a bearing body arranged between the outer ring and the inner ring. Each rolling body is movably accommodated in one recess along the first longitudinal axis.

[0004] For the assembly of the multipode goniometer, the goniometer inner part can be inserted into the cavity of the goniometer outer part through the open end, together with the trunnions and the rolling bodies arranged on the trunnions.

[0005] The center body itself can form a shaft or be connected to a shaft, for example by means of a spline coupling.

[0006] The goniometer inner part is displaceable relative to the goniometer outer part along the first longitudinal axis and is bendable relative to the goniometer outer part at a bend angle. The bend angle is the smallest angle between the first longitudinal axis and the second longitudinal axis. In the extended state of the goniometer, the bend angle is zero degrees. In the bent state of the goniometer, the bend angle is greater than zero degrees.

[0007] For a long time, the applicant has been manufacturing and selling tri- ball pin joints, such as the AAR tri-ball pin joint. They are used, inter alia, on half shafts of motor vehicles, which are used, for example, for the driving connection between the differential and the drive wheels. Here, so-called constant-velocity ball cage fixed joints are usually used on the wheel side, while the AAR tri-ball pin joint mentioned here is used as a mobile joint at the differential. The AAR tri-ball pin joint is designed, inter alia, for bending angles in the order of magnitude of approximately 23 to 26 degrees (or less).

[0008] In one sub-type of the AAR tri-ball pin joint, the AAR i tri-ball pin joint, the inner ring is embodied cylindrical towards the trunnion and is fixed at the outer ring with respect to the direction along the rotational axis by means of the fixing ring.

[0009] The trunnion is in contact with the bearing body or the inner ring of the rolling body by means of a so-called sliding surface (contact surface), which is embodied, inter alia, as a spherical segment. The sliding surface is oriented in the circumferential direction around the second longitudinal axis, such that a torque acting around the longitudinal axis of the joint, that is to say a torque acting in the circumferential direction around the first longitudinal axis, is transmitted to the rolling body by means of the sliding surface of the trunnion and from the rolling body to the concave segment (or vice versa).

[0010] The rolling body rolls on the raceways provided for this purpose, such that it can be displaced within the concave segment along the first longitudinal axis. Each concave segment thus has two raceways opposite one another, on which the rolling body can be supported with respect to the circumferential direction extending around the first longitudinal axis. Between the raceways of one concave segment, abutment surfaces can be provided The rolling body can be supported on the abutment surfaces if necessary.

[0011] During the operation of a motor vehicle, different states can occur, for example on a half shaft, which extends substantially parallel to the axle of the motor vehicle and by means of which the wheels can be driven by a drive unit. In the traction mode of operation, the wheels are driven by the drive unit. In the coasting mode of operation, the motor vehicle is driven by the inertia mass in motion. For a tri-ball pin joint arranged on a half shaft, the contact between the trunnion and the rolling body and between the rolling body and the concave segment is different in certain states.

[0012] For example, when the motor vehicle is driving forward, the direction of rotation of the half shafts is constant. When switching between coasting operation and traction operation, the contact between the sliding surface of the trunnion and the rolling body and between the rolling body and the recess changes, i.e. from one side to the other, for example, as seen in a cross section extending transversely to the first and / or second longitudinal axis. Even if the motor vehicle changes its driving direction (from forward to reverse), the contact between the trunnion and the rolling body and between the rolling body and the recess changes to the other side of the trunnion or the recess in the circumferential direction.

[0013] In principle, the side of the sliding surface or the recess on which the contact (transmitting the torque) is present is referred to as the "active side", while the other side of the sliding surface or the recess on which the contact is not present is referred to as the "passive side".

[0014] In traction operation of the motor vehicle, i.e. when the motor vehicle is driven by the drive unit, the trunnion is in contact with the rolling body using one of the sliding surfaces, and the rolling body is in particular in contact with one side (active side) of the recess. In coasting reverse traction operation or coasting idle operation (both cases are referred to as "coasting") of the motor vehicle, i.e. when a driving torque is introduced from the wheel and the drive unit is still connected (coasting reverse traction operation) or has been disconnected (coasting idle operation), the trunnion is in contact with the rolling body using the other of the sliding surfaces, and the rolling body is in particular in contact with the other side (active side) of the recess. In coasting reverse traction operation or coasting idle operation, the direction of the introduced torque is opposite to the direction of rotation of the universal joint, while in traction operation, the directions are the same.

[0015] The properties of the multi-ball pin universal joint are defined, inter alia, by the so-called ACFG value (Axial Cyclic Force Generation, i.e. undesired axial forces generated by the universal joint). This value is given as the root mean square value of the force in Newton root mean square [Nrms]. This value changes depending on the bending angle of the universal joint, wherein for each universal joint, the curve of the value as a function of the bending angle is definable or determinable. In this way, the range of application of the universal joint is limited by the maximum bending angle, at which the ACFG value does not exceed an absolute value which is still considered permissible.

[0016] Furthermore, in the case of a multi-ball pin universal joint, the movement of the rolling body needs to be controlled in the operation of the universal joint. For example, in particular when the universal joint is operated with a bending angle greater than zero, the rolling body can also come into contact with the recess on the passive side. This contact can on the one hand generate noise and on the other hand friction losses, wherein wear can also occur on the rolling body and / or the recess, which in fact limits the service life of the universal joint.

[0017] In order to control the movement of the rolling bodies, it is known, for example, to provide the abutment faces described at the outset in the recesses, that is to say between the rolling tracks of a recess in the circumferential direction. This makes it possible to limit the tilting of the rolling bodies (about the so-called tilt axis or pitch axis, also referred to below as the first pivot axis). However, the contact between the abutment faces and the rolling bodies also produces noise or friction losses. The tilting of the rolling bodies about the so-called rolling axis, which extends transversely to the extent of the respective recess, should also be controlled, since in this case, in particular, contact between the rolling bodies and the rolling tracks or recesses on the passive side can occur.

[0018] A three-ball joint is known, for example, from the subsequently published DE 102023117277 A1. SUMMARY

[0019] It is now the task of the present application to at least partially solve those problems described with respect to the prior art. In particular, a multi-ball joint is to be presented with which the ACFG forces can be reduced and with which contact between the rolling bodies and the recesses on the passive side is to be prevented. Furthermore, contact between the rolling bodies and the abutment faces of the recesses is to be prevented as far as possible.

[0020] These tasks are solved with a multi-ball joint having the features according to claim 1. Further advantageous design proposals are given in the dependent claims. It is pointed out that the features listed individually in the dependent claims can be combined with one another in any technically reasonable manner in order to define further design proposals of the application. Furthermore, the features given in the claims are explained and illustrated more precisely in the description, in which further preferred design proposals of the application are also shown.

[0021] A multi-ball joint is presented having:

[0022] • a joint outer part having a first longitudinal axis and a cavity extending parallel to the first longitudinal axis and having an open end, wherein at least two, in particular exactly two or exactly three, recesses extending parallel to the first longitudinal axis are formed distributed along a circumferential direction extending around the first longitudinal axis in the joint outer part; and

[0023] • a joint inner part having a second longitudinal axis, which comprises at least one central body on which at least two, in particular exactly two or exactly three, trunnions are molded, which have trunnion axes extending radially from the second longitudinal axis, and on each of which at least one rolling body is arranged which can be rotated about the trunnion axis.

[0024] Each rolling body, in particular the outer ring of the rolling body, extends in the shape of a ring around an axis of rotation of the rolling body.

[0025] Each rolling body is movably accommodated in a recess along a first longitudinal axis. Each recess has two raceways opposite each other in a circumferential direction. Each raceway has a first section and a second section along a radial direction extending transversely to the first longitudinal axis. In the event of a prescribed operation of the joint, in the transmission of a torque directed in the circumferential direction, the rolling body, in particular the outer ring, is supported on one of the two raceways via a plurality of contact points with respect to the circumferential direction. Here, only the contact points in the first section of the raceway (by the first and second contact points, if necessary by an additional fourth contact point) form a center of instantaneous rotation for the rolling body, while at least one (third) contact point in the second section only supports the rolling body in its rotation around the center of instantaneous rotation.

[0026] Alternatively or additionally, the properties of a multi-ball pin joint can also be described as follows:

[0027] Each rolling body is movably accommodated in a recess along a first longitudinal axis. Each recess has two raceways opposite each other in a circumferential direction. Each raceway has a first section and a second section along a radial direction extending transversely to the first longitudinal axis. In the event of a prescribed operation of the joint, in the transmission of a torque directed in the circumferential direction, the rolling body, in particular the outer ring, is supported on one of the two raceways via a plurality of contact points with respect to the circumferential direction. These contact points, in particular, form a center of instantaneous rotation. Here, the rolling body is in contact with the raceway in the first section via at least two contact points (either exactly two contact points or exactly three contact points, i.e. the first, second, and if necessary fourth contact points), and in the second section via at least one or exactly one (third) contact point (which contact point or contact points can only support the rolling body in its rotation around the center of instantaneous rotation).

[0028] The sections of the raceway are arranged adjacent to each other along the radial direction (or, in the case of the joint in the stretched arrangement: along a direction parallel to the axis of rotation or the trunnion axis). If necessary, a further section without a special function (for example, only for spacing the first section from the second section) can also be provided between the sections.

[0029] Each rolling body extends annularly around an axis of rotation of the rolling body. Each rolling body has, in particular, a first region and a second region along the axis of rotation. The regions are arranged adjacent to one another along the axis of rotation. If desired, a further region without a special function (for example, only for spacing the first region from the second region) can also be provided between the regions. In particular, the first region and the second region are each characterized by a special profile of the peripheral surface of the rolling body.

[0030] The rolling body comprises, in particular, only the outer ring and the inner ring, which are able to rotate relative to one another. They can in particular be in direct contact with one another. As an alternative, in particular, further support bodies (rolling bodies, for example, needle-shaped rolling bodies) are arranged between the inner ring and the outer ring. These support bodies, which are in particular embodied as cylindrical, are arranged in a mounting space of the inner ring or the outer ring. A large number of such support bodies are arranged along a circumferential direction around the axis of rotation. The support bodies are in particular prevented from being displaced along the axis of rotation by means of a securing ring arranged in a corresponding recess on the outer ring.

[0031] The rotation of the inner ring relative to the outer ring makes it possible for the rolling bodies to roll along the recesses or raceways in the outer part of the joint, thereby enabling the inner part of the joint to be moved relative to the outer part of the joint along the first longitudinal axis.

[0032] When the inner part of the joint is bent relative to the outer part of the joint, the rolling bodies are further guided by the raceways, wherein at least the trunnion is pivoted relative to the rolling bodies.

[0033] The rolling bodies are in particular guided by the recesses in such a way that a pivoting of the rolling bodies relative to the recesses is not possible, or is as far as possible limited (that is, in particular, no pivoting about the first and / or second pivot axes occurs).

[0034] As an alternative, the rolling bodies are also pivoted relative to the recesses when the inner part of the joint is bent.

[0035] In addition to being able to rotate relative to one another, the inner ring and the outer ring are in particular (only) also able to move relative to one another along a common axis of rotation. For example, the movement of the inner ring towards the second longitudinal axis can be limited by the securing ring, or can also not be provided with a limit. In particular, the movement of the inner ring away from the second longitudinal axis relative to the outer ring is limited by the securing ring.

[0036] In particular, the outer ring and the inner ring form (exactly or only) one first stop which limits the movement of the inner ring relative to the outer ring along the rotational axis and away from the second longitudinal axis. In particular, the first stop is formed by a protrusion on the outer ring or on the inner ring, which the inner ring or the outer ring hits when the inner ring is moved into the maximum position. Thus, the inner ring can only be moved in this direction, i.e. along the rotational axis, in particular away from the second longitudinal axis, up to the point of contact with the stop face. In the other direction along the rotational axis, i.e. towards the second longitudinal axis, the inner ring, in particular when running as intended, can be moved without restriction, at least relative to the outer ring, but not relative to the trunnions.

[0037] In particular in a double ball pin type cardan joint (with only two trunnions), it is also possible to provide no stop between the outer ring and the inner ring, so that the inner ring can be moved without restriction relative to the outer ring along the rotational axis.

[0038] The starting point or zero point of the movement is in particular the position in which the inner ring starts from the PCR1, i.e. from the PCR of the inner part of the cardan joint, when the cardan joint is not bent, i.e. when the longitudinal axes of the outer part of the cardan joint and the inner part of the cardan joint are arranged coaxially. From this position, at least a large part of the movement of the inner part of the cardan joint, corresponding to the ROM, i.e. the movement path of the respective trunnion along the rotational axis away from the second longitudinal axis starting from the PCR1, is achieved by the possible movement path towards the first stop. If the inner ring comes into contact with the outer ring at the first stop before the maximum bending angle is reached, further movement of the inner part of the cardan joint, in particular up to the maximum bending angle which is only reached when the cardan joint is assembled, can be received by the play of the respective rolling body in the respective recess on the outer part of the cardan joint.

[0039] The inner ring forms (exactly or only) one second stop with the trunnions at least when the rotational axis and the trunnion axis are arranged coaxially. The second stop limits the displacement of the inner ring along the trunnion axis towards the second longitudinal axis. In the intended running, i.e. when the inner part of the cardan joint is arranged together with the outer part of the cardan joint as a multi-ball pin type cardan joint, the displacement of the inner ring relative to the trunnions along the trunnion axis away from the second longitudinal axis is not restricted, i.e. is only limited by the first stop. In particular, the outer ring is supported on the recess, so that the first stop prevents further displacement of the inner part of the cardan joint.

[0040] In the coasting operation (coasting reverse traction operation and coasting idle operation), the movement of the inner ring, in particular, can be limited by the first stop.

[0041] In the traction operation, the displacement of the inner ring, in particular, can be controlled by the second stop.

[0042] In particular, the first stop is arranged on a first side of the bearing body facing the second longitudinal axis along the rotational axis or on a second side of the bearing body facing away from the second longitudinal axis.

[0043] If the first stop is arranged on the first side of the bearing body facing the second longitudinal axis along the rotational axis, the first stop can in particular be formed by a protrusion of the inner ring, which extends in a radial direction away from the rotational axis and at least partially beyond the outer ring.

[0044] If the first stop is arranged on the second side of the bearing body facing away from the second longitudinal axis along the rotational axis, the first stop can in particular be formed by a protrusion of the outer ring, which extends in a radial direction towards the rotational axis and at least partially beyond the inner ring.

[0045] In particular, the first stop is formed by the outer ring itself or by a securing ring arranged on the outer ring. The securing ring can for example be embodied in the form of a so-called snap ring. The securing ring can be arranged in a circumferential groove on the outer ring and protrude from the groove, so that the securing ring comes into contact with the inner ring when the inner ring is moved far enough away from the second longitudinal axis along the rotational axis.

[0046] The securing ring or the groove required for this requires additional installation space, so that the rolling body must be designed larger, if necessary. On the other hand, the manufacturing costs of the outer ring can be lower if a securing ring is provided instead of a protrusion constructed on the outer ring.

[0047] In particular, the installation space for the bearing body on the outer ring is limited by a securing ring arranged on the outer ring. In particular, on both sides of the bearing body, that is to say on the first side facing the second longitudinal axis and on the second side facing away from the second longitudinal axis, the installation space is limited by one securing ring, respectively.

[0048] In particular, the inner ring has a stepped shape in a cross section extending transversely to the second longitudinal axis, so that the contact faces of the inner ring interacting with the bearing body are arranged offset outwards, that is to say away from the second longitudinal axis, along the rotational axis relative to one end face of the inner ring. The end face of the inner ring in particular refers to the innermost surface of the inner ring (inward along the rotational axis, that is to say towards the second longitudinal axis).

[0049] The stepped shape can comprise sections at right angles to one another or sections inclined to one another.

[0050] The securing ring is in particular designed to be slotted, so that it can be elastically deformed when fitted into the groove of the outer ring.

[0051] In particular, the second stop can be formed by a securing ring arranged in a groove on the outer ring.

[0052] The prescribed operation of a multi-ball-pin universal joint (also called cardan joint) in particular comprises that the inner part of the joint and the outer part of the joint are arranged relative to each other for a specific application case. For example, all rolling bodies are arranged in recesses and the joint is operated only in a certain range of the bending angle, for example between 0 degrees and 30 degrees or between 0 degrees and 26 degrees. Furthermore, a torque is transmitted between the outer part of the joint and the inner part of the joint which is considered to be allowed for the joint, and a movement of the rolling bodies along the first longitudinal axis only occurs to a certain extent.

[0053] The non-prescribed operation for example comprises an assembly of the joint or an assembly of parts of the joint, for example an arrangement of the rolling bodies onto the trunnions.

[0054] In particular, each rolling body is supported on (only) one of the two raceways (that is, on the so-called active side) by means of a plurality of contact points. Preferably, (at least) three contact points are provided.

[0055] Each raceway in particular has a first section and a second section along a radial direction extending transversely to the first longitudinal axis. The sections are arranged adjacent to each other along the radial direction. If necessary, a further section without a special function (for example, only for spacing the first section from the second section) can also be provided between the sections. In particular, the first section and the second section are characterized by a special and mutually different shape of the raceway surface, respectively. The surface of each raceway in particular is designed to be constant along the first longitudinal axis (at least in the region through which the rolling body passes when operating as intended).

[0056] The contact points in particular are all located within a cross section extending transversely to the first longitudinal axis.

[0057] In particular, the contact points are arranged spaced apart relative to each other along a radial direction extending transversely to the first longitudinal axis.

[0058] In particular, only (that is, completely) by means of the contact points in the first section a momentary center (Momentanpol) is formed for the rolling body.

[0059] In the first section exactly two contact points (a first contact point and a second contact point) can be provided, but also more than two contact points. A further contact point, in the following referred to as fourth contact point, is then arranged between the first contact point and the second contact point along the radial direction. The second contact point in particular is arranged between the first contact point and a third contact point (in the second section) along the radial direction.

[0060] The momentary center is a generally known abstract concept in kinematics, for example used in the design of transmissions, robotics and also in the design of wheel guiding devices of automobiles.

[0061] For the planar motion of a rigid body, the instantaneous center is a point in space around which the rigid body can be considered to rotate at the instant in question (instantaneously, at an infinitely small point in time) and to be treated. The velocity at the instantaneous center is zero at the instant in question, or the velocity would be zero if the rigid body extended to the instantaneous center. In particular, the instantaneous center is formed by the intersection of the face normal of the first contact point and the face normal of the second contact point. In particular, the face normal of the fourth contact point, if present, also extends through the instantaneous center.

[0062] The rolling body (or the outer ring of the rolling body) is in contact with the raceway in the first section via the contact points (of the first region) on the drive side. The instantaneous center makes these contact points form a rotational cardan joint with the cardan axis (i.e. the instantaneous center) in order to enable the rolling body or the outer ring to pivot.

[0063] In particular, at any time, the instantaneous center is formed exclusively by the contact points in the first section. The first section and the second section of the respective raceway are in particular determined, i.e. unchangeable, due to the shape or profile of the raceway. That is, in particular, the instantaneous center is always formed exclusively by the contact points in the first section, and the support of the rotation around the instantaneous center is always achieved by the contact points in the second section.

[0064] In this way, in particular, the position of the contact points is always defined or determined by the special design of the raceway.

[0065] However, at least (in particular exactly) one contact point is provided in the second section, on which the rolling body is supported, so that a rotation (pivoting) around the instantaneous center is exactly not possible (i.e. when transmitting a torque and in contact with the raceway on the drive side).

[0066] In particular, the contact points are arranged along the trunnion axis or in the radial direction, so that on the drive side, a rotation of the rolling body or the outer ring around the instantaneous center is always supported by the contact points arranged in the second section, at least during the prescribed operation of the multi-ball-pin cardan joint.

[0067] In particular, the position of the rolling body or the outer ring in the radial direction (relative to the recess or the raceway, i.e. relative to the outer part of the cardan joint) is defined or stabilized by the contact points of the first section. Stabilization in particular means that the rolling body (in particular due to the existing torque and the contact surface of the rolling body with the raceway) always automatically returns to this position.

[0068] In particular, the rolling body (or outer ring) is controlled (or the tilting or pitching of the rolling body (or outer ring) is reduced or prevented) about a first pivot axis (tilt axis or pitch axis) which extends transversely to the rotational axis and transversely to the raceway, in particular by the contact point of the first section.

[0069] In particular, the rolling body (or outer ring) is controlled (or the rolling motion of the rolling body (or outer ring) is reduced or prevented) about a second pivot axis (rolling axis) which extends transversely to the rotational axis and parallel to the raceway, in particular by the at least one contact point of the second section.

[0070] In particular, the rolling body (or outer ring) is controlled (or the rolling motion of the rolling body (or outer ring) is reduced or prevented) about a second pivot axis (rolling axis) which extends transversely to the rotational axis and parallel to the raceway, in particular by the at least one contact point of the second section.

[0071] In particular, the tilting about the first pivot axis can be limited to a maximum of 10 degrees, in particular a maximum of 5 degrees, preferably a maximum of 3 degrees, particularly preferably a maximum of 1 degree, in absolute terms, or can even be completely suppressed (tilting angle of 0 degrees), in particular when the joint is operating as intended and starting from an arrangement in which the rolling body is not tilted in the recess, i.e. when the joint is in the stretched arrangement.

[0072] In particular, the rolling motion about the second pivot axis can be limited to a maximum of 5 degrees, in particular a maximum of 3 degrees, preferably a maximum of 2 degrees, particularly preferably a maximum of 1 degree, in absolute terms, or can even be completely suppressed (rolling angle of 0 degrees), in particular when the joint is operating as intended and starting from an arrangement in which the rolling body is not tilted in the recess, i.e. when the joint is in the stretched arrangement.

[0073] In particular, the rolling body is supported by exactly three contact points of the raceway (when the joint is operating as intended), wherein only the first and second contact points arranged in the first section form the instantaneous center, and the third contact point arranged in the second section only supports the rolling motion of the rolling body about the instantaneous center.

[0074] In particular, each rolling body is in contact with the respective recess at any time only via a plurality of contact points on the respective raceway, preferably only via the first, second and third contact points (and if necessary also via the fourth contact point), in particular when the joint is operating as intended.

[0075] In particular, the raceway and the rolling bodies are designed such that, when the multi- ball pin joint is in the stretched arrangement, i.e. when the longitudinal axes are coaxially aligned with each other (at which the bending angle is 0°), the distances of the contact points from the gimbaling axis are arranged at respective distances from each other, wherein the deviations of these distances from each other are at most 10%, in particular at most 5%, preferably at most 2%, or even at most 1% (in particular all distances are equal) of the smallest distance. In particular, the (fourth) distance of the fourth contact point, if present, can have a greater deviation. In particular, the (fourth) distance of the fourth contact point is greater than the distances of the other contact points.

[0076] If these distances are designed to be as equal in size as possible, the sliding friction of the rolling bodies at the contact points with the raceway (when the rolling bodies are rolling on the raceway) can be minimized as much as possible.

[0077] In particular, the raceway and the rolling bodies are designed such that, when the multi- ball pin joint is in the stretched arrangement, i.e. when the longitudinal axes are coaxially aligned with each other, and in a cross section extending transversely to the longitudinal axes, at each contact point, the face normal of the rolling body surface has a contact angle with the tangential direction extending transversely to the gimbaling axis and transversely to the longitudinal axes. The contact angles of the (first and second) contact points forming the instantaneous center are each at least 5°, in particular at least 8°, preferably at least 10°. The contact angles of the (first and second) contact points forming the instantaneous center are preferably at most 45°, preferably at most 30°, particularly preferably at most 20°.

[0078] In particular, the fourth contact angle of the fourth contact point, if present, is smaller than the contact angles of the first and second contact points. In particular, the fourth contact angle is 0°.

[0079] In particular, the absolute values of the contact angles of the (first and second) contact points forming the instantaneous center are equal or different. In particular, they differ from each other by 1 to 10°, preferably by 1 to 5°.

[0080] In particular, the first contact angle is greater than the second contact angle, wherein the second contact angle is arranged between the first contact angle and the third contact angle along the radial direction. In particular, the orientation of the first contact angle is different from the second contact angle and, if the third contact angle is not zero, from the third contact angle. In particular, the sum of the second contact angle and the third contact angle differs from the value of the first contact angle by at most 10°, preferably by at most 5°, particularly preferably by at most 2°, or in particular is equal to the value of the first contact angle.

[0081] In particular, the contact angle of the (third) contact point, which only supports the rotation of the rolling body about the instantaneous center, is smaller than the contact angles of the (first and second) contact points forming the instantaneous center. In particular, the contact angle of the (third) contact point is at most 10°, preferably at most 5°, particularly preferably at most 2°, or even 0°.

[0082] In particular, the absolute value of the contact angle of the (third) contact point, which only supports the rotation of the rolling body around the instantaneous center, is less than 1 degree.

[0083] In particular, the first section of the raceway, which is in contact with the contact point or has the (first and second) contact point forming the instantaneous center of the rolling body, has a Gothic shape (i.e. a pointed arch shape composed of two circular arcs) in a cross section extending transversely to the first longitudinal axis. If a fourth contact point is provided, the fourth contact point is arranged between the first and second contact points along the radial direction. The raceway can have a different shape between the pointed arches, for example.

[0084] The first profile and shape of the raceway are in particular designed such that a specific proportional relationship exists between the distance of the (first and second) contact point in the first section and the difference between the (first, second and fourth) distances. The proportional relationship consists of the distance between the first and second contact points (or the absolute value without sign, in millimeters) parallel to the axis of rotation (when the gimbal is extended) and the difference between the smaller of the first distance (of the first contact point) and the second distance (of the second contact point) and the fourth distance (of the fourth contact point) (or the absolute value without sign, in millimeters).

[0085] For the distance, it applies that:

[0086] Distance = First contact point - Second contact point

[0087] For the difference, if the first distance is the smaller distance, it applies that:

[0088] Difference = Fourth distance - First distance

[0089] Or, if the second distance is the smaller distance, it applies that:

[0090] Difference = Fourth distance - Second distance

[0091] For the proportional relationship, it applies that:

[0092] Proportional relationship = Distance / Difference

[0093] The proportional relationship is in particular greater than 1.5, preferably between 4 and 1.5, particularly preferably between 2.5 and 1.5.

[0094] The circular arcs can in particular have the same or different radii from each other. The (first and second) contact points between the rolling body and the raceway are then located on the circular arcs, i.e. on the side limbs of the pointed arches. Depending on the (first and second) contact angle or the shape of the pointed arches or the shape of the circular arcs, the (first and second) contact points are arranged at equal distances from the trunnion axis or at different distances from the trunnion axis.

[0095] In particular, the raceways have a straight, concave (i.e. curved away from the rolling body) or convex (i.e. curved towards the rolling body) shape in a cross-section extending transversely to the first longitudinal axis in the second section in contact with the (third) contact point supporting only the rolling movement of the rolling body about the instantaneous center. If the second section is designed straight, these shapes extend parallel to each other in the cross-section, or can also extend inclined to each other and open or close towards the second longitudinal axis. In the case of a parallel arrangement, these shapes can also be inclined in the cross-section relative to the rotation axis or trunnion axis (when the joint is extended).

[0096] In particular, the rolling body has a first profile of the outer circumference surface in the first region containing the (first, second and, if necessary, fourth) contact points and a second profile of the outer circumference surface in the second region containing the at least one (third) contact point in a cross-section containing the rotation axis.

[0097] The first profile can be formed by one or more radii or have a curved course. For example, the first profile can have a first curvature (defined by at least one radius) at the first contact point and a second curvature (defined by at least one radius) which is the same or different at the second contact point. In particular, the first profile can also have other courses between the curved courses at the contact points, if necessary also straight courses.

[0098] In particular, the first profile is formed by a first radius (i.e. spherical) and the second profile is formed by a second radius (i.e. spherical or ellipsoidal). In particular, these radii are different from each other or of equal size.

[0099] In particular, the second radius is greater than the first radius, in particular at least 1.1 times or at least 1.2 times (i.e. second radius = factor x first radius).

[0100] As an alternative, the radii are of equal size.

[0101] If the radii are of equal size, the two raceways of the concave recess contacted by the rolling body can be designed differently from each other, so that the arrangement of the first section and the second section in the raceways is different.

[0102] In particular, the PCR1 of the inner joint part and the PCR2 of the outer joint part are arranged along the radial direction between the instantaneous center and the at least one third contact point. The respective PCR is the pitch circle radius (Teilkreisradius) of the respective joint part.

[0103] The definition of the pitch circle radius (also called pitch circle radius - PCR) is basically known, in particular also for multi-ball pin joints.

[0104] The pitch circle radius (PCR1) of the trunnion or the inner part of the universal joint is the so-called effective radius. This is defined when the universal joint is stretched, i.e. the longitudinal axes are arranged coaxially to each other. The effective radius defines the lever arm of the resultant force when transmitting torque. Thus, the pitch circle radius of the trunnion or the inner part of the universal joint is the radius from the second longitudinal axis of the inner part of the universal joint, for example the centre point of the spherical segment sliding surface of the trunnion is arranged on this radius when the universal joint is stretched.

[0105] The pitch circle radius (PCR2) of the outer part of the universal joint or the concave segment is here also the so-called effective radius, which is likewise defined when the universal joint is stretched, i.e. the longitudinal axes are arranged coaxially to each other. The effective radius defines the lever arm of the resultant force when transmitting torque.

[0106] Furthermore, a motor vehicle having at least one multi-trunion universal joint according to the application is claimed here.

[0107] The use of the indefinite article ("ein", "eine", "einer" and "eines") especially in the claims and the corresponding description is to be understood as the indefinite article itself and not as the numeral. Thus, the corresponding introduced concept or component is to be understood as it exists at least once, especially also multiple times.

[0108] It is to be noted in advance that the numerals ("first", "second",...) used here are mainly (only) used to distinguish between multiple objects, quantities or processes of the same kind, thus in particular no dependency and / or sequence between these objects, quantities or processes is intended to be prescribed. If a dependency and / or sequence is intended, this is explicitly stated here or is obvious to the person skilled in the art when studying the embodiments described in detail. As long as a component can occur multiple times ("at least one"), a description of one of these components can also apply to all or some of the multiple components, but this is not necessarily the case. BRIEF DESCRIPTION OF DRAWINGS

[0109] The application and the technical background will be explained in more detail below with reference to the drawings. It is to be noted that the application is not to be restricted to the embodiments listed. In particular, features described for a particular universal joint type (double-trunion universal joint or triple-trunion universal joint) can also be applied to other universal joint types (for example to other universal joint types than double-trunion universal joints and triple-trunion universal joints). In particular, it is to be noted that the dimensions of the figures and in particular the scale of the illustrations are only schematic. Therein:

[0110] Figure 1 A cross-sectional detail of a first embodiment variant of a triple-trunion universal joint 1 is shown;

[0111] Figure 2Cross-sectional detail of a first embodiment variant of a three-ball-pin joint 1 is shown;

[0112] Figure 3 Cross-sectional detail of a second embodiment variant of a three-ball-pin joint in an extended state is shown;

[0113] Figure 4 Three-ball-pin joint according to Figure 3 in a downwardly bent posture is shown;

[0114] Figure 5 Three-ball-pin joint according to Figure 3 and Figure 4 in an upwardly bent posture is shown;

[0115] Figure 6 Three-ball-pin joint according to Figures 3 to 5 in a leftwardly bent posture is shown;

[0116] Figure 7 Three-ball-pin joint according to Figures 3 to 6 in a rightwardly bent posture is shown;

[0117] Figure 8 Cross-sectional detail of a third embodiment variant of a three-ball-pin joint is shown;

[0118] Figure 9 Cross-sectional detail of a fourth embodiment variant of a three-ball-pin joint is shown;

[0119] Figure 10 Cross-sectional detail of a fifth embodiment variant of a three-ball-pin joint is shown;

[0120] Figure 11 Detail of a first embodiment variant of a three-ball-pin joint according to Figure 2 is shown;

[0121] Figure 12 Cross-sectional detail of a sixth embodiment variant of a three-ball-pin joint is shown;

[0122] Figure 13 Cross-sectional detail of a seventh embodiment variant of a three-ball-pin joint is shown;

[0123] Figure 14 Cross-sectional detail of an eighth embodiment variant of a three-ball-pin joint is shown;

[0124] Figure 15 Cross-sectional detail of a ninth embodiment variant of a three-ball-pin joint is shown;

[0125] Figure 16: shows a cross-sectional detail of a tenth embodiment variant of a tripod joint;

[0126] Figure 17 : shows a cross-sectional detail of an eleventh embodiment variant of a tripod joint;

[0127] Figure 18 : shows a cross-sectional detail of a twelfth embodiment variant of a tripod joint;

[0128] Figure 19 : shows a cross-sectional detail of a thirteenth embodiment variant of a tripod joint;

[0129] Figure 20 : shows a cross-sectional detail of a fourteenth embodiment variant of a tripod joint;

[0130] Figure 21 : shows a cross-sectional detail of a fifteenth embodiment variant of a tripod joint;

[0131] Figure 22 : shows a cross-sectional detail of a sixteenth embodiment variant of a tripod joint;

[0132] Figure 23 : shows a cross-sectional detail of a seventeenth embodiment variant of a tripod joint;

[0133] Figure 24 : Shows cross-sectional details of a double ball and pin universal joint;

[0134] Figure 25 : shows a sectional side view of a tripod joint according to a second embodiment variant in an extended state; and

[0135] Figure 26 :Shows the basis in the bent state Figure 25 Tripod universal joint. DETAILED DESCRIPTION

[0136] Figure 1 A cross-sectional detail of a first embodiment variant of a tripod joint 1 is shown. Figure 2 A cross-sectional detail of a first embodiment variant of a tripod joint 1 is shown. Figure 3 A cross section through a second embodiment variant of the tripod joint 1 is shown in the extended state. Figure 4 Shown in a downward bending position Figure 3 Tripod universal joint 1. Figure 5 Shown in an upward bending position Figure 3 and Figure 4 Tripod universal joint 1. Figure 6Shown in a left-bending position Figures 3 to 5 Tripod universal joint 1. Figure 7 Shows the basis in the right bending posture Figures 3 to 6 Tripod universal joint 1. Figures 1 to 7 They will be described together below.

[0137] The tripod joint 1 comprises a joint outer part 2 having a first longitudinal axis 3 and a cavity 4 extending parallel to the first longitudinal axis 3 and having an open end 5. Three recesses 7 extending parallel to the first longitudinal axis 3 are formed in the joint outer part 2, distributed along a circumferential direction 6 extending around the first longitudinal axis 3. The tripod joint 1 further comprises a joint inner part 8 having a second longitudinal axis 9. The joint inner part 8 comprises a central body 10, onto which three trunnions 11 are integrally formed, the trunnions having trunnion axes 12 extending radially from the second longitudinal axis 9. A rolling element 13 is arranged on each trunnion 11, which is rotatable at least about the trunnion axis 12.

[0138] Each rolling body 13 extends in an annular shape around an axis of rotation 14 of the rolling body 13 .

[0139] Each rolling element 13 is accommodated in a respective recess 7 so as to be movable along the first longitudinal axis 3 . Each recess 7 has two raceways 17 , 18 that face each other in the circumferential direction 6 . Each raceway 17 , 18 has a first section 15 and a second section 16 along a radial direction 37 extending transversely to the first longitudinal axis 3 . When transmitting a torque directed in the circumferential direction 6 , the rolling element 13 , together with the outer ring 39 , is supported relative to the circumferential direction 6 on one of the two raceways 17 , 18 via a plurality of contact points 19 , 20 , 21 . The instantaneous center 22 for the rolling element 13 is formed solely by the contact points 19 , 20 in the first section 15 (on one of the raceways 17 , 18 ), while the at least one contact point 21 in the second section 16 supports the rolling element 13 solely for rotation about the instantaneous center 22 .

[0140] Each rolling element 13 extends in an annular shape around its axis of rotation 14. Each rolling element 13 has a first region 44 and a second region 45 along the axis of rotation 14. Regions 44 and 45 are arranged adjacent to each other along the axis of rotation 14. A second region with no specific function is located between regions 44 and 45 (e.g., serving only to separate first region 44 from second region 45 or to form a transition between regions 44 and 45). The first and second regions 44 and 45 are characterized by the special profiles 31 and 32 of the outer circumference of the rolling element 13, respectively.

[0141] The rolling body 13 comprises an outer ring 39 and an inner ring 40, which can rotate relative to one another. For this purpose, between the inner ring 40 and the outer ring 39, bearing bodies 41 (rolling elements, here needle-shaped rolling elements) are arranged. These bearing bodies 41 are arranged in mounting spaces of the outer ring 39, wherein the mounting spaces are limited in their direction relative to the rotation axis 14 by a retaining ring 46. A large number of such bearing bodies 41 are arranged along a circumferential direction 6 around the rotation axis 14. The bearing bodies 41 are prevented from being displaced along the rotation axis 14 by the retaining ring 46, which is arranged in a corresponding recess of the outer ring 39.

[0142] The rotation of the inner ring 40 relative to the outer ring 39 makes it possible for the rolling body 13 to roll along the recesses 7 or raceways 17, 18 in the gimbal outer part 2, and thus for the gimbal inner part 8 to be moved relative to the gimbal outer part 2 along the first longitudinal axis 3.

[0143] When the gimbal inner part 8 is bent relative to the gimbal outer part 2, the rolling body 13 is further guided by the raceways 17, 18, wherein at least the trunnion 11 is pivoted relative to the rolling body 13.

[0144] Here, the rolling body 13 is guided by the recesses 7 such that it cannot or hardly can be pivoted relative to the recesses 7.

[0145] The inner ring 40 and the outer ring 39, in addition to being able to rotate relative to one another, can also be moved relative to one another along the common rotation axis 14. For example, a movement of the inner ring 40 towards the second longitudinal axis 9 can be limited by the retaining ring 46 (see, for example, Figure 8 ) or can also not be provided (see, for example, Figures 1 to 7 ). A movement of the inner ring 40 relative to the outer ring 39 away from the second longitudinal axis 9 is limited by the retaining ring 46.

[0146] The outer ring 39 and the inner ring 40 form a first stop 47 (just or only) by means of the retaining ring 6, which limits the movement of the inner ring 40 relative to the outer ring 39 along the rotation axis 14 and away from the second longitudinal axis 9. The first stop 47 is formed by a protrusion (retaining ring 46) on the outer ring 39, against which the inner ring 40 comes when it is moved away from the second longitudinal axis 9 to the greatest extent. The inner ring 40 can thus only be moved in this direction, that is to say along the rotation axis 14 (away from the second longitudinal axis 9), up to the point of contact with the stop face. In the other direction along the rotation axis 14, that is to say towards the second longitudinal axis 9, the inner ring 40 can be moved without limitation when functioning as intended, at least relative to the outer ring 39, but not relative to the trunnion 11.

[0147] The starting point or zero point of the movement is when the gimbal 1 is not bent, that is to say when the longitudinal axes 3, 9 of the gimbal outer part 2 and the gimbal inner part 8 are arranged coaxially (see, for example, Figure 3) from which at least a major part of the movement of the joint inner part 8 (corresponding to the ROM, i.e. the movement path of the respective trunnion 11 along the rotational axis 14 away from the second longitudinal axis 9 starting from the PCR 135) is effected by a possible movement path towards the first stop 47. If the inner ring 40 comes into contact with the outer ring 39 at the first stop 47 before the maximum bending angle 52 is reached, further movement of the joint inner part 8, in particular up to the maximum bending angle 52 which is only reached when the joint 1 is assembled, can be received by the play of the respective rolling body 13 in the respective recess 7 of the joint outer part 2.

[0148] At least when the rotational axis 14 and the trunnion axis 12 are arranged coaxially, the inner ring 40 forms (just or only) one second stop 48 with the trunnion 11. The second stop 48 limits the displacement of the inner ring 40 along the trunnion axis 12 towards the second longitudinal axis 9. In the prescribed operation, i.e. when the joint inner part 8 is arranged together with the joint outer part 2 to a three-ball-pin joint 1, the displacement of the inner ring 40 relative to the trunnion 11 along the trunnion axis 12 away from the second longitudinal axis 9 is not limited, i.e. only by the first stop 47. At this time, the outer ring 39 is supported on the recess 7 or raceway 17, 18, so that the first stop 47 prevents further displacement of the joint inner part 8.

[0149] The movement of the inner ring 40 can be limited by the first stop 47 in the coasting operation (coasting drag operation and coasting free operation).

[0150] The displacement of the inner ring 40 can be controlled by the second stop 48 in the traction operation.

[0151] The first stop 47 is arranged on the second side of the bearing body 41 away from the second longitudinal axis 9 along the rotational axis 14.

[0152] The first stop 47 is formed by a fixing ring 46 arranged on the outer ring 39. The fixing ring 46 is designed in the form of a so-called snap ring. The fixing ring 46 is arranged in an annular groove on the outer ring 39 and projects from the groove, so that the fixing ring 46 comes into contact with the inner ring 40 when the inner ring 40 is moved far enough away from the second longitudinal axis 9 along the rotational axis 14.

[0153] The mounting space for the bearing body 41 on the outer ring 39 is limited by the fixing ring 46 arranged on the outer ring 39. The mounting space is defined on both sides of the bearing body 41, i.e. on the first side towards the second longitudinal axis 9 and on the second side away from the second longitudinal axis 9, by one fixing ring 46 each.

[0154] Each rolling body 13 is supported on one of the two raceways 17, 18 (that is, on the so-called active side) by means of a plurality of contact points 19, 20, 21. Three contact points 19, 20, 21 are provided.

[0155] Each raceway 17, 18 has a first section 15 and a second section 16 along a radial direction 37 extending transversely to the first longitudinal axis 3. These sections 15, 16 are arranged next to each other along the radial direction 37. Between these sections 15, 16, a further section is provided which does not have a special function (for example, only serves to space the first section 15 from the second section 16, or to form a transition between these sections 15, 16). The first section 15 and the second section 16 are each characterized by a special shape of the raceway 17, 18 surface. The surface of each raceway 17, 18 is designed to be constant along the first longitudinal axis 3 (at least in the region through which the rolling body 13 passes when running as intended).

[0156] The contact points 19, 20, 21 are all located in a cross section extending transversely to the first longitudinal axis 3. The contact points 19, 20, 21 are arranged spaced apart from each other along a radial direction 37 extending transversely to the first longitudinal axis 3. Only through the contact points 19, 20 in the first section 15, a momentary center 22 is formed for the rolling body 13. Here, the momentary center 22 is formed by the intersection of the surface normal 26 of the first contact point 19 and the surface normal 26 of the second contact point 20.

[0157] For the planar movement of a rigid body (here: the rolling body 13 or the outer ring 39), the momentary center 22 is a spatial point around which the rigid body can be considered to be rotating and to be handled at this moment (instant, infinitesimally small point in time) (because, as a result of the action of the torque, the rigid body is pressed onto the contour of the raceway 17, 18). The velocity of the momentary center is zero at the instant considered.

[0158] The rolling body 13 (or the outer ring 39 of the rolling body 13) is in contact on the active side with the first raceway 17 in the first section 15 by means of the contact points 19, 20 (of the first region 44). The momentary center 22 makes it possible for the contact points 19, 20 to form a rotational cardan joint with the cardan axis (the momentary center 22), thus enabling the rolling body 13 or the outer ring 39 to pivot.

[0159] However, in the second section 16, exactly one third contact point 21 is provided on which the rolling body 13 is supported, so that a rotation (pivoting) around the momentary center 22 is exactly not possible.

[0160] At any time, the instantaneous center 22 is formed only by the contact points 19, 20 in the first section 15. The first section 15 and the second section 16 of the respective raceway 17, 18 are defined, i.e. not changeable. That is, the instantaneous center 22 is always formed only by the contact points 19, 20 in the first section 15, and the support of the rotation around the instantaneous center 22 is always achieved by the third contact point 21 in the second section 16.

[0161] In this way, the positions of the contact points 19, 20, 21 are always defined or determined by the special design of the raceways 17, 18.

[0162] The contact points 19, 20, 21 are arranged along the trunnion axis 12 or along a radial direction 37, so that on the driving side, the rotation of the rolling body 13 or outer ring 39 around the instantaneous center 22 can always be supported by the third contact point 21 arranged in the second section 16, at least during the intended operation of the three-ball-pin type universal joint 1.

[0163] Therefore, the position of the rolling body 13 or outer ring 39 along the radial direction 37 (relative to the recess 7 or raceway 17, 18, i.e. relative to the outer joint part 2) is defined or stabilized by the contact points 19, 20 of the first section 15. Stabilized means that the rolling body 13 automatically returns to this position (due to the shape of the first section 15, the respective areas 44, 45 and the prevailing torque transmitted between the outer joint part 2 and the inner joint part 8).

[0164] The contact points 19, 20 of the first section 15 also control the pivoting of the rolling body 13 (or outer ring 39) around a first pivot axis 42 extending transversely to the rotation axis 14 and transversely to the raceways 17, 18, i.e. in particular reduce or prevent such pivoting. This avoids a (in the recess 7, between the raceways 17, 18 along the circumferential direction 6) face contact of the rolling body 13 or outer ring 39 with the outer joint part 2.

[0165] The third contact point 21 of the second section 16 controls the pivoting of the rolling body 13 (or outer ring 39) around a second pivot axis 43 extending transversely to the rotation axis 14 and parallel to the raceways 17, 18, i.e. in particular reduces or prevents such pivoting. This avoids a contact of the rolling body 13 or outer ring 39 with the raceways 17, 18 on the driven side. Figure 25 and Figure 26

[0166] By the special design of the raceways 17, 18 and the rolling body 13 or outer ring 39, a contact of the rolling body 13 with the outer joint part 2 at other (not provided) contact points (on the usual face or on the driven side) can be avoided. In this way, an undesired noise can also be reduced or avoided by the ACFG value. ​

[0167] The rolling body 13 is supported by exactly three contact points 19, 20, 21 of the respective contact rolling track 17, 18 (that is, only on the driving side) through which a momentary center 22 is formed only by the first contact point 19 and the second contact point 20 arranged in the first section 15, while the third contact point 21 arranged in the second section 16 only supports the rolling body 13 in its rotation around the momentary center 22, when the cardan joint 1 is functioning as intended.

[0168] Each rolling body 13 is in contact with the respective recess 7 at any time only by a plurality of contact points 19, 20, 21 on the respective rolling track 17, 18, that is, only by the first contact point 19, the second contact point 20 and the third contact point 21, when the three-pin cardan joint 1 is functioning as intended.

[0169] The rolling tracks 17, 18 and the rolling bodies 13 are designed in such a way that, when the three-pin cardan joint 1 is in the stretched arrangement (see Figure 2 , Figure 3 , Figure 26 ), that is, when the longitudinal axes 3, 9 are coaxially aligned with each other (at which the bending angle 52 is 0°), the contact points 19, 20, 21 are arranged at a respective distance (first distance 23, second distance 24, third distance 25) from the trunnion axis 12, wherein the distances 23, 24, 25 deviate from each other by at most 1% of the maximum distance 23, 24, 25.

[0170] If the distances 23, 24, 25 are of equal size, the sliding friction of the rolling bodies 13 with the rolling tracks 17, 18 at the contact points 19, 20, 21 can be minimized (when the rolling bodies 13 roll on the rolling tracks 17, 18).

[0171] The rolling tracks 17, 18 and the rolling bodies 13 are designed in such a way that, when the three-pin cardan joint 1 is in the stretched arrangement, that is, when the longitudinal axes 3, 9 are coaxially aligned with each other, and in a cross section extending transversely to the longitudinal axes 3, 9, at each contact point 19, 20, 21 the surface normal 26 of the rolling body 13 surface has a contact angle (first contact angle 27, second contact angle 28, third contact angle 29) with a tangent direction 30 extending transversely to the trunnion axis 12 and transversely to the longitudinal axes 3, 9. The contact angles 27, 28 of the contact points forming the momentary center 22 are each approximately 10°.

[0172] The absolute values of the contact angles 27, 28 of the contact points forming the momentary center 22 are equal (see Figure 1 and Figure 2 ) or different (see, for example, Figure 19 and Figure 20 ).

[0173] The third contact angle 29 of the third contact point 21, which only supports the rotation of the rolling body 13 about the instantaneous center 22, is smaller than the contact angles 27, 28 of the contact points 19, 20 forming the instantaneous center 22. The third contact angle 29 of this third contact point 21 is 0 degrees (see Figures 1 to 7 ). But it can also be approximately 5 degrees (see Figure 19 , Figure 21 , Figure 22 ).

[0174] The raceways 17, 18 have a Gothic shape (i.e. a pointed arch shape composed of two circular arcs, see for example Figures 3 to 7 ) in a cross section extending transversely to the first longitudinal axis 3 in the first section 15, which is in contact with or has the contact points 19, 20 forming the instantaneous center 22 of the rolling body 13. At this point, the radii of the circular arcs can also be large, possibly even infinite, so that a conical shape is formed (see for example Figure 1 and Figure 2 ).

[0175] The circular arcs can have the same or different radii from one another. The contact points 19, 20 between the rolling body 13 and the raceways 17, 18 are located on the circular arcs, i.e. on the side flanks of the pointed arch. Depending on the contact angles 27, 28 or the shape of the pointed arch or the shape of the circular arcs, the contact points 19, 20 are arranged at the same distance 23, 24 from the trunnion axis 12 or at different distances 23, 24 from the trunnion axis 12.

[0176] The raceways 17, 18 have a straight line shape (see Figures 3 to 7 ), a concave shape (i.e. curved away from the rolling body 13, see Figure 1 and Figure 2 ) or a convex shape (i.e. curved towards the rolling body 13, see Figure 13 ) in a cross section extending transversely to the first longitudinal axis 3 in the second section 16, which is in contact with the third contact point 21, which only supports the rotation of the rolling body 13 about the instantaneous center 22. If the second section 16 is designed to be straight, these shapes are particularly parallel to one another in the cross section (see Figures 3 to 7 and Figure 22 , or can also be inclined to one another and open (see Figure 19 ) or closed (see Figure 21 ) towards the second longitudinal axis 9.

[0177] The rolling body 13 has a first profile 31 of the outer peripheral surface containing the contact points 19, 20 in a cross section containing the axis of rotation 14 in a first region 44 and a second profile 32 of the outer peripheral surface containing at least one third contact point 21 in a second region 45. The first profile 31 is formed by a first radius 33 (i.e. spherical), the second profile 32 is formed by a second radius 34 (i.e. spherical, for exampleFigures 1 to 7 or elliptical, for example Figures 3 to 7 and Figure 20 ) are formed. In particular, these radii 33, 34 are different from one another or equal in size.

[0178] If the radii 33, 34 are different, the second radius 34 is greater than the first radius 33 (see Figure 3 , Figure 7 and Figure 20 ).

[0179] As an alternative, the radii 33, 34 are equal in size ( Figure 1 and Figure 2 ).

[0180] If the radii 33, 34 are equal in size, the two raceways 17, 18 of the recess 7 contacted by the rolling body 13 can be designed differently from one another, such that the arrangement of the first section 15 and the second section 16 in the raceways 17, 18 is different (see, for example, Figure 17 ).

[0181] The PCR 135 of the joint inner part 8 and the PCR 236 of the joint outer part 2 are arranged along the radial direction 37 between the instant center 22 and the at least one third contact point 21.

[0182] Figure 8 A cross-sectional detail of a third embodiment variant of a three-ball pin joint 1 is shown. Reference is made to the description of Figures 1 to 7 .

[0183] Here, the trunnion 11 is designed to be spherical and the inner ring 40 is embodied as cylindrical. The inner ring 40 is fixed relative to the outer ring 39 in both directions along the rotational axis 14 by means of a fixing ring 46 arranged in the outer ring 39.

[0184] The rolling body 13 has, in a cross section containing the rotational axis 14, in a first region 44 a first profile 31 of the outer circumference containing the contact points 19, 20 and, in a second region 45, a second profile 32 of the outer circumference containing the at least one third contact point 21. The first profile 31 is formed by a first radius 33, i.e. a spherical shape, and the second profile 32 is formed by a second radius 34, i.e. a spherical shape, wherein the radii 33, 34 are equal in size.

[0185] The raceways 17, 18 have a Gothic shape in a cross section extending transversely to the first longitudinal axis 3 at the first section 15 contacting or having the contact points 19, 20 forming the instant center 22 of the rolling body 13. The circular arcs have equal radii 33, 34. The contact points 19, 20 between the rolling body 13 and the raceways 17, 18 lie on the circular arcs, i.e. on the sides of the pointed arches.

[0186] The raceways 17, 18 have a straight-line shape in a cross section extending transversely to the first longitudinal axis 3 in the second section 16, which is in contact with the third contact point 21, which supports only the rolling body 13 in its rotation about the instantaneous center 22, and these shapes extend parallel to one another in the cross section.

[0187] Figure 9 A cross-sectional detail of a fourth embodiment variant of the three-ball pin joint 1 is shown. Reference is made to the description of Figure 8 .

[0188] Unlike the third embodiment variant, the inner ring 40 has a concave spherical sliding surface facing the trunnion 11. The inner ring 40 is freely movable relative to the outer ring 39 along the rotational axis 14.

[0189] Figure 10 A cross-sectional detail of a fifth embodiment variant of the three-ball pin joint 1 is shown. Reference is made to the description of Figure 8 .

[0190] Unlike the third embodiment variant, the inner ring 40 has a convex sliding surface facing the trunnion 11, wherein the trunnion is embodied as a cylindrical shape.

[0191] The movement of the inner ring 40 relative to the outer ring 39 away from and toward the second longitudinal axis 9 is limited by one fixed ring 46, respectively. A first stop 47 formed by the fixed ring 46 is arranged on the second side of the bearing body 41 away from the second longitudinal axis 9 along the rotational axis 14.

[0192] Figure 11 Details of the first embodiment variant of the three-ball pin joint 1 shown in Figure 1 and Figure 2 are shown. Reference is made to the description of Figures 1 to 7 .

[0193] Figure 12 A cross-sectional detail of a sixth embodiment variant of the three-ball pin joint 1 is shown. Reference is made to the description of Figure 11 .

[0194] Unlike the first embodiment variant, the rolling body 13 has a second profile 32 of the outer peripheral surface comprising at least one third contact point 21 in a cross section containing the rotational axis 14 in the second region 45, wherein the second profile is elliptical.

[0195] Figure 13 A cross-sectional detail of a seventh embodiment variant of the three-ball pin joint 1 is shown. Reference is made to the description of Figure 12 .

[0196] Unlike the sixth variant, the raceways 17, 18 in the second section 16, which is in contact with the third contact point 21, which supports only the rotation of the rolling elements 13 about the instantaneous center 22, have a convex shape (i.e. curved towards the rolling elements 13) in a cross section extending transversely to the first longitudinal axis 3.

[0197] Figure 14 A cross-sectional detail of an eighth variant of the three-ball-bearing type universal joint 1 is shown. Reference is made to the description of Figures 1 to 7 .

[0198] Unlike the first variant, the raceways 17, 18 in the second section 16, which is in contact with the third contact point 21, which supports only the rotation of the rolling elements 13 about the instantaneous center 22, have a straight shape in a cross section extending transversely to the first longitudinal axis 3. These shapes are mutually inclined in the cross section and open towards the second longitudinal axis 9.

[0199] Unlike the first variant, the inner ring 40 has a stepped shape in a cross section extending transversely to the second longitudinal axis 9, so that the contact faces of the inner ring 40 interacting with the support body 41 are arranged offset outwards (i.e. away from the second longitudinal axis 9) along the rotation axis 14 with respect to one end face of the inner ring 40. This end face of the inner ring 40 is the innermost surface of the inner ring 40 (inward along the rotation axis 14, i.e. towards the second longitudinal axis 9). The stepped shape comprises sections at right angles to each other. Furthermore, the inner ring 40 is fixed with respect to both directions along the rotation axis 14 on the outer ring 39 by means of a fixing ring 46 arranged in the outer ring 39.

[0200] Thanks to this stepped shape, the inner ring 40 can be moved further along the rotation axis 14 towards the second longitudinal axis 9.

[0201] Figure 15 A cross-sectional detail of a ninth variant of the three-ball-bearing type universal joint 1 is shown. Reference is made to the description of Figures 3 to 7 .

[0202] Unlike the second variant, the two raceways 17, 18 of the recess 7, which are contacted by the rolling elements 13, are designed differently from each other, so that the arrangement of the first section 15 and the second section 16 in the raceways 17, 18 is different or mutually exchanged.

[0203] Figure 16 A cross-sectional detail of a tenth variant of the three-ball-bearing type universal joint 1 is shown. Reference is made to the description of Figure 14 .

[0204] In contrast to the eighth embodiment variant, the raceways 17, 18 have a straight shape in the cross section extending transversely to the first longitudinal axis 3, in the second section 16 which is in contact with the third contact point 21 which supports only the rolling movement of the rolling body 13 about the instantaneous center 22, wherein these shapes extend parallel to one another.

[0205] Figure 17 A cross-sectional detail of an eleventh embodiment variant of the three-ball joint 1 is shown. Reference is made to the description of Figure 16 .

[0206] In contrast to the tenth embodiment variant, the raceways 17, 18 have a concave shape, i.e. curved away from the rolling body 13, in the cross section extending transversely to the first longitudinal axis 3, in the second section 16 which is in contact with the third contact point 21 which supports only the rolling movement of the rolling body 13 about the instantaneous center 22.

[0207] In contrast to the tenth embodiment variant, the rolling body 13 has a second profile 32 of the outer circumference surface comprising at least one third contact point 21 in the cross section containing the rotational axis 14, wherein this second profile is elliptical in the second region 45.

[0208] Figure 18 A cross-sectional detail of a twelfth embodiment variant of the three-ball joint 1 is shown. Reference is made to the description of Figure 17 .

[0209] In contrast to the eleventh embodiment variant, the raceways 17, 18 have a straight shape in the cross section extending transversely to the first longitudinal axis 3, in the second section 16 which is in contact with the third contact point 21 which supports only the rolling movement of the rolling body 13 about the instantaneous center 22, wherein these shapes of the raceways 17, 18 extend parallel to one another.

[0210] Figure 19 A cross-sectional detail of a thirteenth embodiment variant of the three-ball joint 1 is shown. Reference is made to the description of Figure 16 .

[0211] In contrast to the tenth embodiment variant, the raceways 17, 18 have a straight shape in the cross section extending transversely to the first longitudinal axis 3, in the second section 16 which is in contact with the third contact point 21 which supports only the rolling movement of the rolling body 13 about the instantaneous center 22. These shapes extend obliquely to one another in the cross section and open up towards the second longitudinal axis 9.

[0212] Furthermore, the absolute values of the contact angles 27, 28 of the contact points forming the instantaneous center 22 are different.

[0213] The third contact angle 29 of the third contact point 21, which only supports the rotation of the rolling body 13 about the instantaneous center 22, is smaller than the contact angles 27, 28 of the contact points 19, 20 forming the instantaneous center 22. The third contact angle 29 of the third contact point 21 is approximately 5 degrees.

[0214] Figure 20 A cross-sectional detail of a fourteenth embodiment variant of a three-ball joint 1 is shown. Reference is made to the description of Figure 12 .

[0215] Unlike the sixth embodiment variant, the absolute values of the contact angles 27, 28 of the contact points 19, 20 forming the instantaneous center 22 are different.

[0216] Like the sixth embodiment variant, but unlike, for example, the thirteenth embodiment variant, the third contact angle 29 of the third contact point 21 is 0 degrees.

[0217] Figure 21 A cross-sectional detail of a fifteenth embodiment variant of a three-ball joint 1 is shown. Reference is made to the description of Figure 19 .

[0218] Unlike the thirteenth embodiment variant, the second sections 16 of the raceways 17, 18 have a linear shape in the cross-section and extend obliquely to one another and are closed toward the second longitudinal axis 9.

[0219] Figure 22 A cross-sectional detail of a sixteenth embodiment variant of a three-ball joint 1 is shown. Reference is made to the description of Figure 19 and Figure 21 .

[0220] Unlike the thirteenth and fifteenth embodiment variants, the second sections 16 of the raceways 17, 18 have a linear shape in the cross-section and extend parallel to one another and are inclined relative to the rotation axis 14 or the trunnion axis 12 when the three-ball joint is in the extended state.

[0221] Figure 23 A cross-sectional detail of a seventeenth embodiment variant of a three-ball joint 1 is shown. Reference is made to the description of Figures 1 to 7 .

[0222] The first sections 15 of the raceways 17, 18, which are in contact with or have the contact points 19, 20, 49, have a Gothic shape, i.e. a pointed arch shape composed of two circular arcs, in a cross-section extending transversely to the first longitudinal axis 3. Between the circular arcs, the raceways 17, 18 have a linear shape which is different from the Gothic shape.

[0223] More than two contact points 19, 20 are provided in the first section 15. A further fourth contact point 49 is arranged along the radial direction 37 between the first contact point 19 and the second contact point 20. The face normal 26 of the fourth contact point 49 extends through the instantaneous center 22.

[0224] When the multi-ball-pin gimbal 1 is functioning as intended, each rolling body 13 is in contact with the respective recess 7 at any time only via a plurality of contact points 19, 20, 21, 50 on the respective raceway 17, 18, i.e. only via the first, second, third and fourth contact points 19, 20, 21, 50.

[0225] The raceways 17, 18 and the rolling bodies 13 are designed such that, when the three-ball-pin gimbal 1 is in the stretched arrangement, i.e. when the longitudinal axes 3, 9 are coaxially aligned with each other (at which time the bending angle 52 is 0 degrees), the contact points 19, 20, 21 are arranged at respective distances 23, 24, 25 from the trunnion axis 12, wherein the distances 23, 24, 25 deviate from each other by at most 1% of the smallest (first, second, third) distance. The fourth distance 50 of the fourth contact point 49 deviates more than the other distances 23, 24, 25. The fourth distance 50 of the fourth contact point 49 is greater than the distances 23, 24, 25 of the other contact points 19, 20, 21.

[0226] The fourth contact angle 51 of the fourth contact point 49 is smaller than the contact angles 27, 28 of the first contact point 19 and the second contact point 20. The fourth contact angle 51 is 0 degrees.

[0227] The raceways 17, 18 have a straight and mutually parallel shape in a cross section extending transversely to the first longitudinal axis 3 in the second section 16, which is in contact with the third contact point 21, which only supports the rolling bodies 13 in their rotation about the instantaneous center 22.

[0228] The rolling bodies 13 have, in a cross section containing the rotation axis 14, in the first region 44 a first profile 31 of the outer circumference surface containing the contact points 19, 20, 49, and in the second region 45 a second profile 32 of the outer circumference surface containing the third contact point 21. The first profile 31 is formed by a first radius 33 (i.e. spherical), and the second profile 32 is formed by a second radius 34 (i.e. elliptical). The radii 33, 34 are designed differently from each other, wherein the second radius 34 is greater than the first radius 33.

[0229] The shape of the first profile 31 and the raceway 17 is designed such that a specific proportional relationship exists between the distance 53 and the difference 54 between the distances 23, 24, 50. The proportional relationship is constituted by the distance 53 (or its absolute value without a sign) parallel to the rotational axis 14 between the first contact point 19 and the second contact point 20, and the difference 54 (or its absolute value) between the smaller of the first distance 23 and the second distance 24 and the fourth distance 50, i.e. the proportional relationship = distance 53 / difference 54. The proportional relationship is greater than 1.5.

[0230] Figure 24 A cross-sectional detail of a multi-ball pin type universal joint 1 is shown, which is designed as a double-ball pin type universal joint 1. Reference is made to the description of Figures 1 to 23 . Here, the trunnions 11 with spherical sliding surfaces are arranged in an inner ring 40 with spherical contact surfaces. The inner ring 40 is freely movable relative to the outer ring 39 along the rotational axis 14.

[0231] Unlike all other embodiments, the rolling body 13 only comprises the outer ring 39 and the inner ring 40. The bearing body 41 provided in the other embodiments is not present, so that the inner ring 40 is directly rotatably supported on the outer ring 39. However, this embodiment without the bearing body 41 can also be implemented in other multi-ball pin type universal joints 1, for example in a triple-ball pin type universal joint.

[0232] Figure 25 A cross-sectional side view of a triple-ball pin type universal joint 1 according to a second embodiment variant in a motor vehicle 38 (schematically represented) is shown. Figure 26 A triple-ball pin type universal joint 1 in a bent state is shown in Figure 26 .

[0233] The triple-ball pin type universal joint 1 comprises a universal joint outer part 2 having a first longitudinal axis 3 and a cavity 4 extending parallel to the first longitudinal axis 3 and having an open end 5, wherein in the universal joint outer part 2 three recesses 7 extending parallel to the first longitudinal axis 3 are formed distributed along a circumferential direction 6 extending around the first longitudinal axis 3. The triple-ball pin type universal joint 1 further comprises a universal joint inner part 8 having a second longitudinal axis 9. The universal joint inner part 8 comprises a central body 10 on which three trunnions 11 are molded, which have a trunnion axis 12 extending radially from the second longitudinal axis 9, and on each trunnion 11 at least one rolling body 13 is arranged, which is rotatable around the trunnion axis 12.

[0234] Each rolling body 13 extends annularly around a rotational axis 14 of the rolling body 13.

[0235] Each rolling body 13 is movably accommodated in a recess 7 along the first longitudinal axis 3, respectively. Each recess 7 has two raceways 17, 18 opposite each other in the circumferential direction 6.

[0236] The rolling body 13 comprises an outer ring 39 and an inner ring 40, which are rotatable relative to one another. For this purpose, between the inner ring 40 and the outer ring 39, support bodies 41 (rolling elements, here needle-shaped rolling elements) are arranged. These support bodies 41 are arranged in a mounting space of the outer ring 39, wherein the mounting space is limited with respect to the direction of the rotational axis 14 by a fixing ring 46. A large number of such support bodies 41 are arranged along a circumferential direction 6 around the rotational axis 14. The support bodies 41 are prevented from displacement along the rotational axis 14 by the fixing ring 46 arranged in a corresponding recess of the outer ring 39.

[0237] The joint inner part 8 is displaceable along the first longitudinal axis 3 relative to the joint outer part 2 and is bendable relative to the joint outer part 2 by a bending angle 52 (see Figure 26 ) between the first longitudinal axis 3 and the second longitudinal axis 9. In the extended state of the joint 1, the bending angle 52 is 0 degrees (see Figure 25 ). In the bent state of the joint 1, the bending angle 52 is greater than 0 degrees (see Figure 26 ).

[0238] List of reference signs

[0239] 1 tri- ball joint

[0240] 2 joint outer part

[0241] 3 first longitudinal axis

[0242] 4 cavity

[0243] 5 end

[0244] 6 circumferential direction

[0245] 7 recess

[0246] 8 joint inner part

[0247] 9 second longitudinal axis

[0248] 10 central body

[0249] 11 trunnion

[0250] 12 trunnion axis

[0251] 13 rolling body

[0252] 14 rotational axis

[0253] 15 first section

[0254] 16 second section

[0255] 17 first raceway

[0256] 18 second raceway

[0257] 19 first contact point

[0258] 20 second contact point

[0259] 21 third contact point

[0260] 22 instantaneous center

[0261] 23 first distance

[0262] 24 second distance

[0263] 25 third distance

[0264] 26 face normal

[0265] 27 first contact angle

[0266] 28 second contact angle

[0267] 29 third contact angle

[0268] 30 tangent direction

[0269] 31 first profile

[0270] 32 second profile

[0271] 33 first radius

[0272] 34 second radius

[0273] 35 pitch circle radius PCR1 (of the inner part of the universal joint)

[0274] 36 pitch circle radius PCR2 (of the outer part of the universal joint)

[0275] 37 radial direction

[0276] 38 motor vehicle

[0277] 39 outer ring

[0278] 40 inner ring

[0279] 41 bearing body

[0280] 42 first pivot axis (tilt / pan axis)

[0281] 43 second pivot axis (roll axis)

[0282] 44 first region

[0283] 45 second region

[0284] 46 fixed ring

[0285] 47 first stop

[0286] 48 second stop

[0287] 49 fourth contact point

[0288] 50 fourth distance

[0289] 51 fourth contact angle

[0290] 52 bending angle

[0291] 53 distance

[0292] 54 difference

Claims

1. Multi-globe-pin universal joint (1) having a universal joint outer part (2) having a first longitudinal axis (3) and a cavity (4) extending parallel to the first longitudinal axis (3) and having an open end (5), wherein In the joint outer part (2), at least two recesses (7) extending parallel to the first longitudinal axis (3) are formed distributed along a circumferential direction (6) extending around the first longitudinal axis (3); and a joint inner part (8) having a second longitudinal axis (9), the joint inner part comprising at least one central body (10) on which at least two trunnions (11) are molded, the trunnions having trunnion axes (12) extending radially from the second longitudinal axis (9), wherein on each trunnion (11) at least one rolling body (13) is arranged which is rotatable around the trunnion axis (12), respectively, wherein each rolling body (13) extends annularly around an axis of rotation (14) of the rolling body (13), wherein each rolling body (13) is movably accommodated in the recess (7) along the first longitudinal axis (3), respectively, wherein each recess (7) has two raceways (17, 18) opposite to each other in the circumferential direction (6), and each raceway (17, 18) has a first section (15) and a second section (16) along a radial direction (37) extending transversely to the first longitudinal axis (3), wherein when a torque directed in the circumferential direction (6) is transmitted, the rolling body (13) is supported on one of the two raceways (17, 18) with respect to the circumferential direction (6) by a plurality of contact points (19, 20, 21, 49), wherein only the contact points (19, 20, 49) in the first section (15) form a center of instantaneous motion (22) for the rolling body (13), and at least one contact point (21) in the second section (16) only supports the rotation of the rolling body (13) around the center of instantaneous motion (22).

2. The multi-spherical-pin universal joint (1) according to claim 1, wherein The rolling body (13) is supported on the raceway (17, 18) by exactly three contact points (19, 20, 21), wherein only the first contact point (19) and the second contact point (20) arranged in the first section (15) form the center of instantaneous motion (22), and the third contact point (21) arranged in the second section (16) only supports the rotation of the rolling body (13) around the center of instantaneous motion (22).

3. The multi-spherical-pin universal joint (1) according to any one of the preceding claims, wherein When the multi-ball pin joint (1) is operating as intended, each rolling body (13) is in contact with the respective recess (7) at any time only by a plurality of contact points (19, 20, 21) on the respective raceway (17, 18).

4. The multi-spherical-pin universal joint (1) according to any one of the preceding claims, wherein The raceways (17, 18) and the rolling bodies (13) are embodied such that, when the multi-ball pin joint (1) is in the stretched arrangement, that is, when the longitudinal axes (3, 9) are coaxially aligned with one another, the contact points (19, 20, 21, 49) are arranged at a respective distance (23, 24, 25, 50) from the gimbaling axis (12), wherein the distances (23, 24, 25, 50) deviate from one another by at most 10% of the smallest distance (23, 24, 25, 50).

5. The multi-spherical-pin universal joint (1) according to any one of the preceding claims, wherein The raceways (17, 18) and the rolling bodies (13) are embodied such that, when the multi-ball pin joint (1) is in the stretched arrangement, that is, when the longitudinal axes (3, 9) are coaxially aligned with one another, and in a cross section extending transversely to the longitudinal axes (3, 9), at each contact point (19, 20, 21, 50) a surface normal (26) of the surface of the rolling body (13) has a contact angle (27, 28, 29, 51) between the surface normal (26) and a tangent direction (30) extending transversely to the gimbaling axis (12) and transversely to the longitudinal axes (3, 9), wherein the contact angles (27, 28) of the contact points (19, 20) forming the instantaneous center (22) are each at least 5 degrees.

6. The multi-spherical pin type universal joint (1) according to claim 5, wherein The absolute values of the contact angles (27, 28) of the contact points (19, 20) forming the instantaneous center (22) are equal or different.

7. The multi-spherical-pin universal joint (1) according to any one of the preceding claims 5 and 6, wherein The contact angle (29) of the contact point (21) supporting only the rotation of the rolling body (13) about the instantaneous center (22) is smaller than the contact angles (27, 28) of the contact points (19, 20) forming the instantaneous center (22).

8. The multi-spherical-pin universal joint (1) according to any one of the preceding claims 5 to 7, wherein The absolute value of the contact angle (29) of the contact point (21) supporting only the rotation of the rolling body (13) about the instantaneous center (22) is smaller than 10 degrees.

9. The multi-spherical-pin universal joint (1) according to any one of the preceding claims, wherein A first section (15) of the raceway (17, 18) in contact with the contact points (19, 20) forming the instantaneous center (22) of the rolling body (13) has a Gothic shape in a cross section extending transversely to the first longitudinal axis (3).

10. The multi-spherical-pin universal joint (1) according to any one of the preceding claims, wherein A second section (16) of the recess (7) in contact with the contact point (21) supporting only the rotation of the rolling body (13) about the instantaneous center (22) has a linear, concave or convex shape in a cross section extending transversely to the first longitudinal axis (3).

11. The multi-spherical-pin universal joint (1) according to any one of the preceding claims, wherein The rolling body (13) has, in a cross section containing the axis of rotation (14), in a first region (44) a first profile (31) of the outer circumference containing the contact points (19, 20, 49) and, in a second region (45), a second profile (32) of the outer circumference containing at least one contact point (21), wherein the first profile (31) is formed by at least one first radius (33) and the second profile (32) is formed by at least one second radius (34), wherein the radii (33, 34) are different or equal in size.

12. The multi-spherical pin universal joint (1) according to claim 11, wherein The second radius (34) is greater than the first radius (33).

13. The multi-spherical pin universal joint (1) according to claim 11, wherein, The radii (33, 34) are of equal size and the raceways (17, 18) of the recess (7) contacted by the rolling bodies (13) are embodied differently from one another such that the arrangement of the first section (15) and the second section (16) in the raceways (17, 18) is different.

14. The multi-spherical-pin universal joint (1) according to any one of the preceding claims, wherein The PCR1 (35) of the cardan inner part (8) and the PCR2 (36) of the cardan outer part (2) are arranged along the radial direction (37) between the instant center (22) and the third contact point (21), wherein the PCRs (35, 36) are pitch circle radii.

15. Motor vehicle (38) with at least one multi-pin cardan joint (1) according to any one of claims 1 to 14.

Images