Cardanic cross joint with insulation

A universal joint for coupling a drive shaft and a driven shaft comprises a first joint yoke having axially opposite yoke arms; a second joint yoke having axially opposite yoke arms and arranged radially at an angle of 90 in relation to the first joint yoke to form an internal space; first and second connection elements, each connection element having a base web and at least one connection area extending from the base web toward the internal space; and an elastic coupling element configured to fit within the internal space and connected to the at least one connection area of each of the first and second connection elements such that the elastic coupling element is spaced from each of the first and second connection elements over a portion of the respective base webs to create an axial interspace.

The present invention is related to U.S. patent application Ser. No. 11/276,047 entitled “Axial Insulation for a Universal Joint”, U.S. patent application Ser. No. 11/276,049 entitled “Axial Insulation for a Universal Cross Joint”, U.S. patent application Ser. No. 11/276,051 entitled “Insulation for Universal Cross Joint”, and U.S. patent application Ser. No. 11/276,052 entitled “A Universal Cross Joint With Axial Insulation”, filed simultaneously herewith.

FIELD OF THE INVENTION

The invention relates to a cardan joint having two joint yokes, wherein one of the joint yokes is connectable or connected with a driven shaft or a drive shaft, and the other joint yoke is connectable or connected to a shaft to be driven or a drive shaft.

BACKGROUND OF THE INVENTION

Cardan or universal joints, are usually used when two torque-transmitting shafts whose aligned orientation is not always ensured are to be connected with each other. The universal joint then usually consists of two opposing joint yokes that are arranged twisted radially at an angle of 90° in relation to each other that each represent one end of the two shafts that are to be connected in an articulated manner. The cross member, which consists of two pin bearers offset against each other by 90°, is disposed between the joint yokes, the cross member being made of one piece so that the two pin bearers are rigidly connected with each other. The pin bearers are each supported, pivotally about their axes, in the two joint yokes.

With regard to the transmission of driving forces, the skilled person is regularly presented with the task of transmitting the rotational movement on the one hand, but, on the other, of eliminating vibrations and shocks if possible. Such interferences may, for example, be caused by vibrations from the drive unit. This problem is especially noticeable in automobile engineering, in particular in the area of the drive train, for example in the area of the cardan shaft where the vibrations between drive assembly and rear axle are transmitted without hindrance, and in the area of the steering line or in the steering column where, should conventional cardan joints be used, no insulation whatsoever is effected against low-frequency vibrations or shocks imposed by road bumps. Such interferences may, on the one hand, lead to damages in the drive train or the steering column and/or to adverse effects of an acoustic or mechanical nature for the driver.

For the purpose of uncoupling with regard to acoustics or vibration dynamics, in particular in the steering column, it is, for example, known to use a torsional elastic coupling with a so-called Hardy disk as an axially elastic coupling element or a loop disk. The Hardy disk is disposed, for example, in the steering column between the bottom universal joint and a steering housing or steering gear or between the universal joints. The Hardy disk, which is rigid in the direction of rotation, is formed such that it is soft in the direction of the steering column. As required by principle, the bending stiffness of the Hardy disk is relatively small. This effects a distortion of the Hardy disk by the bending moments from the universal joint, if the Hardy disk is arranged in series with the universal joint, as is common. Since a Hardy disk alone (without a cardan joint), at least given appropriate life expectancies, is not suitable for connecting non-aligned shafts, the number of components is disadvantageously increased with the necessary arrangement in series with the cardan joint. Furthermore, the axial constructional space is increased thereby, and the usual compensation of the discontinuities by means of two cardanic joints arranged in anti-phase is disturbed by the additional Hardy disk since it works like an additional joint when placed in series.

The following is a discussion of relevant art pertaining to cardan joints. The discussion is provided only for understanding of the invention that follows. The summary is not an admission that any of the work described below is prior art to the claimed invention.

EP 0 563 940 B1 discloses a universal joint comprising two forks which are situated opposite one another with a 90° offset and which are each a part of each one of two shafts which are to be pivotally interconnected, or which are adapted each to be connected to each one of two shaft ends which are to be pivotally interconnected, and comprising two journal pairs which are offset by 90° from another and which form a journal cross and which are rotatable about their axis in the respective fork ends and, relative to the rotational axis of the shafts, are mounted for torque transmission, the two journal pairs being at least slightly pivotable relatively to one another in the plane formed by the journal cross, each journal being mounted in an anchor bracket and adjacent anchor brackets are interconnected by an elastic coupling element, whereby the elastic coupling element contains reinforcing inlays in loop form, which are disposed to be stationary and which each interconnect two adjacent anchor brackets and in that the reinforcing inlays in loop form are situated along the periphery of the universal joint in a loop plane which is perpendicular to the plane of the journal cross.

It must be regarded as a main disadvantage of the cross joint disclosed in EP 0 563 940 B1 that the two pairs of pins connect the own pins with each other integrally in different ways: The one pair uses a through bolt, the other pair is configured from two short pins that are connected with each other by means of an additional connecting portion. For this reason, a different production tool is required for the production of each pin or pair of pins, which makes the production of the cross joint extremely cost-intensive.

It is a further disadvantage that the cross joint disclosed in EP 0 563 940 B1 takes a lot of constructional effort and is thus very susceptible to malfunction. It must be considered as a further disadvantage that the yokes must be designed small with regard to width and that thus, their yoke bearings must be designed to be bigger (more expensive) in order to transmit a sufficient torque given reasonable construction dimensions. If the flexible ring is damaged in the cross joint of EP 0 563 940 B1, a replacement ring must be supplied via the anchors. In addition, the cross joint is difficult to balance, especially in the case of shafts that rotate quickly.

EP 0 160 599 describes a flexible coupling device comprising first and second yokes which are intended to be fixed, respectively, to a drive member and a driven member, which each have arms arranged so that the arms of the first yoke are interposed with those of the second yoke, whereby to each yoke is fixed a support and these two supports are arranged opposite each other so that the facing surfaces of these supports are substantially perpendicular to the rotation axis of the device, in that an elastomeric linking element is fixed to these facing surfaces of the supports, and in that each support is fixed to the corresponding yoke by means of a spindle engaging in at least one opening in said support and in holes provided in the arms of said yoke.

GB 942,495 discloses a universal coupling for shafts comprising a flexible disc having coupling elements extending one on each side thereof, each for connection to one of the shafts to be coupled, the coupling elements being pivoted to the disc about axes at right angles and lying normally to the axis of the disc whereby, in use of the coupling, angular misalignment of the coupled shafts may be accommodated by pivoting of the coupling elements without flexure of the disc, the disc being composed wholly or mainly of plastic, rubber or the like resilient material which is unrestrained so as to be free to flex during use of the coupling.

It must be considered as a main disadvantage of the connection for shafts disclosed in GB 942,495 that the coupling elements are rotated with clearance towards the disk and with significant friction, the torsion clearance and the friction merely satisfying modest demands.

Therefore, what is needed is an improved universal joint of the type mentioned at the beginning with simple means in such a way that it is cheaper to produce from an economic standpoint, without the elastic coupling element having to convey significant bending moments.

SUMMARY OF THE INVENTION

This invention provides a universal joint for coupling a drive shaft and a driven shaft comprising two joint yokes. Each yoke has bearing elements at axially opposite yoke arms. One joint yoke being connected with the driven shaft and the other joint yoke being connected to the drive shaft. The two joint yokes are arranged radially at an angle of 90° in relation to each other to form an internal space. The invention includes a pair of identical connection elements having pins being pivotally supported in the bearings of the respectively associated joint yoke arms. The universal joint further comprises an elastic coupling element. The connection elements are spatially separated from one another and are connected to each other via the elastic coupling element.

Because of the identical form of the two connection elements, the respective connection elements may be produced or processed in a single production tool. In this manner, a universal joint is provided which can clearly be manufactured cheaper in production for economic reasons, because the respective connection elements can be manufactured or processed with only a single production tool, at the same time making a reduction of logistical and storage costs possible since a separate storage or a provision of different pin bearers, for example, just in time, can be omitted.

Advantageously, a hitherto commonly used elastic uncoupling member arranged in series (additional elastic coupling) can thus be done without in the universal joint according to the invention. The elastic coupling element is advantageously arranged parallel to the universal joint. Within the sense of the invention, a parallel arrangement means that the elastic coupling element is directly associated with the universal joint. Thus, the universal joint as a unit with the elastic coupling element integrated into the joint is easier and cheaper to produce. In addition, a universal joint is provided which satisfies high demands with regard to torsion clearance and to the bearing friction.

It is favorable within the sense of the invention if the pins of each of the connection elements, in relation to an axis of symmetry, each reach, radially counter-directionally, into the associated yoke arms or the bearings disposed therein.

It is expediently provided in a preferred embodiment that the pins reach into the yoke arms or into the bearings disposed therein in a direction oriented from the internal space towards an outer side of the yoke arms opposite to the internal space. Here, pins with their free ends are arranged outside with respect to the middle axis of the joint.

In a further preferred embodiment, it is favorable within the sense of the invention if the pins reach into the yoke arms or into the bearings disposed therein in a direction oriented from the outer side of the yoke arms opposite to the internal space towards the internal space. Here, pins with their free ends are arranged inside with respect to the middle axis of the joint.

However, it may expediently also be provided that the pins of each of the connection elements, in relation to the middle axis of the joint, each reach, oriented equidirectionally, into the yoke arms or into the bearings disposed therein with the connection elements preferably being formed asymmetrically.

Here, it is favorable within the sense of the invention if, in relation to the middle axis of the joint, one of the pins reaches into the associated yoke arm or into the bearing disposed therein in a direction oriented from the outer side of the yoke arms opposite to the internal space towards the internal space, the opposite pin of the same connection element reaching into the yoke arm or into the bearing disposed therein in a direction oriented from the internal space towards the outer side. Here, with respect to the middle axis of the joint, the pins of the respectively same connection element are arranged alternately, one of the pins being arranged on the inside and the other pin being arranged on the outside. This is especially advantageous with regard to the simple radial insertion of the connection elements into the joint yokes when assembling the universal joint.

In the case of the alternate arrangement of the pins, it is expediently provided that that joint yokes with yoke arms have different distances with regard to the middle axis of the joint. In contrast however, when the pins are arranged on the same side, the yoke arms expediently have the same distance with respect to the axis of symmetry.

The elastic coupling element is disposed in the internal space as a torsion-resistant, flexural elastic or axially elastic disk, for example, a Hardy disk. However, the elastic coupling element may also be disposed in the internal space as a torsion-resistant, flexural elastic or axially elastic ring, e.g. annulus, or multi-angular or polygonal ring. Furthermore, the elastic coupling element may also be disposed around the outer sides of the joint yokes or their yoke arms as a torsion-resistant, flexural elastic or axially elastic ring, e.g. annulus, or multi-angular or polygonal ring.

The elastic coupling element may, for example, consist of rubber or the like. A screw joint, rivet joint, vulcanization or the like can, for example, be provided as the connection of the elastic coupling element with the connection elements or the pair of connection elements formed therefrom.

The universal joint according to the invention is particularly suitable for use in a steering column of a motor vehicle, wherein axial shocks can be filtered out as compared to a conventional universal joint. This behavior is especially desirable in structures of steering columns because thus, axial shocks, for example due to stimuli from the road, can be kept away from a steering wheel without having to make sacrifices with regard to torsional stiffness. By integration of the elasticity through the doubly pivotally supported elastic coupling element into or around the universal joint, it is avoided that a bending stiffness must also be provided, in addition to the axial compliance. By means of the universal joint according to the invention, the axial compliance can be made greater so that insulation properties are also improved over conventional elastic couplings in structures of steering columns. The integrated elastic coupling element does not have to convey significant bending moments because the elastic coupling element is kept free of bending by bearings in the axis of the moments. This makes ideal compliance properties in axial direction without bending resistances with optimal stiffness in the direction of rotation possible. The large axial compliance of the joint can favor omitting an otherwise commonly used slip joint from the steering column, which has to compensate fitting tolerances and stimuli from the road. In addition, the universal joint according to the invention, if formed with a disk, can be produced with comparably large yoke widths and, advantageously, with correspondingly small-sized yoke bearings in an appropriate size, with much larger torques being transmittable than in a universal joint with small yoke widths and larger (more expensive) yoke bearings. In addition, the integration of the ring according to the invention permits a simple conveying of the flexible ring in axial direction.

The invention can further include one or more features being subject matter of the dependant claims. Modes for carrying out the present invention are explained below by reference to non limiting embodiments of the present invention shown in the attached drawings. The above-mentioned object, other objects, characteristics and advantages of the present invention will become apparent from the detailed description of the embodiment of the invention presented below in conjunction with the attached drawings.

In the different figures, the same parts are always provided with the same reference numeral so that they are also only described once, as a rule.

DETAILED DESCRIPTION OF THE INVENTION

TheFIGS. 1 to 12show a universal joint1having two joint yokes2. One of the joint yokes2is connected to a driven shaft3or drive shaft3, the other joint yoke2being connected to the shaft4to be driven or drive shaft4. The two joint yokes2are arranged twisted radially at an angle of 90° in relation to each other so that the two joint yokes2form an internal space6. An elastic coupling element7is associated with the universal joint1. A pair8of connection elements formed of two identical, spatially separate connection elements9is associated with the joint yokes2. The connection elements9with their pins11respectively arranged thereon are pivoted in bearings13in the respectively associated joint yokes2or in their yoke arms12. The connection elements9are connected with each other via the elastic coupling element7. Because of the selected side view in theFIGS. 1,5,7,9and11, or because of the selected longitudinal section inFIG. 3, only one joint yoke2, respectively, with its two yoke arms12, or only one connection element9with its two transversal webs18are discernible in their entirety.

The bearings13in the yoke arms12are designed as single-row bearings with a axis of rotation that is radially oriented, for example, as anti-friction bearing, e.g., as needle or ball bearings, but they may also be designed as plain bearings. At least one of the two bearings13per joint yoke2is able to accept radial joint forces in addition to the axial joint forces. The bearings13are fixed in a suitable manner, radially relative to an axis of the joint, in the joint yokes2or their yoke arms12. Possible embodiments are, for example, press fit, bonding or positive fit (abutting at the shoulder, spring ring or the like) of the outer races of the bearing in the joint yokes2or their joint arms12.

In theFIGS. 1 to 6, the connection elements9are formed as additional connection yokes14,29,32. The connection yokes14,29,32have a base web17and transversal arms18arranged on the end thereof. The transversal arms18merge into a pin section19which respectively bears the pin11.

In the embodiment shown inFIGS. 1 and 2, the pins11, in relation to a middle axis22of the joint, each reach counter-directionally into the associated yoke arms12or the bearings13placed therein. With their free ends23, the pins11are oriented from an outer side24opposite the internal space6towards the internal space6. The pin section19and thus, the pin11, is arranged on the outside of the joint yokes2or their yoke arms12in relation to the middle axis22of the joint, the pin section19abutting a side of the bearings13pointing towards the outer side24. Seen in the side view, therefore, the connection yokes14are slightly bigger than the joint yokes2or the symmetrical joint yokes2in order to grasp them with their transversal web18so that the pin11can reach into the bearings13from the outer side24.

For the connection with the elastic coupling element7, the base web17has attached connection areas26that are each offset in relation to the middle axis22of the joint. In relation to the axis of symmetry22, the connection areas26have the same distance, and extend as appendages27axially in the direction towards the internal space6. In this way, an axial interspace is created between the elastic coupling element7and the respective connection element9or the middle of its respective transversal web18, which provides an axial clearance. This axial interspace can be produced by material integration of the connection areas26into the elastic coupling element7(as illustrated, for example, inFIGS. 3 and 4), together with a simplification of the transversal webs18of the connection elements9.

The elastic coupling element7, in the exemplary embodiment shown in theFIGS. 1 and 2, is formed as a disk, preferably as a torsion-resistant, flexural elastic or axially elastic disk, preferably as a Hardy disk, and is connected with the connection areas26or the appendages27in the internal space6. However, it is also conceivable that the elastic coupling element7in the embodiment according to theFIGS. 1 and 2may be formed as a torsion-resistant, flexural elastic or axially elastic ring or annulus. The elastic coupling element7consists of a rubber, for example. A screw joint, rivet joint, vulcanization or the like can, for example, be provided as the connection with the respective elastic coupling element9or the appendages27arranged on the connection yokes14. In theFIGS. 1 and 2, the connection is in principle represented by a chain-dotted line28.

A further embodiment of the universal joint1according to the invention is shown in theFIGS. 3 and 4. In contrast to the exemplary embodiment shown inFIGS. 1 and 2, the pins11with their free end23reach into the joint yokes2or the bearings placed therein13in a direction oriented from the internal space6towards the outer side24opposite the internal space6, but nevertheless counter-directionally in relation to the axis of symmetry22.

In this embodiment, the connection elements9are formed as additional connection yokes29. The connection yokes29have, like the connection yoke14of the embodiment according to theFIGS. 1 and 2, the base web17and transversal arms18arranged on the end thereof. The transversal arms18merge into the pin section19which respectively bears the pin11.

With their base web17, the joint yokes29are designed shorter than in the embodiment according toFIG. 1, because the transversal web18extends into the internal space6. Thus, the pin section19with its pin is also arranged in the internal space6, the pin section19abutting a side of the bearing13that points towards the internal space6.

The connection yokes29, seen in a side view, are formed smaller than a yoke width of the joint yokes12opposite each other, so that the joint yokes29can reach into the bearing13from the inside with their transversal web18or the pin section19with the pin11.

The connection of the elastic coupling element7with the connection element29takes place directly at the base web17. The axial clearance is achieved by round, attached screwed eyes31associated with the elastic coupling element7, which is why, advantageously, a contouring of the joint yokes29corresponding to a contouring of the joint yokes14can be omitted.

In theFIGS. 3 to 4, the connection elements9can also be operated, in principle, rotated by 180° in the bearings13fastened against the elastic coupling element7, which provides for additional adjustment options in the elastic coupling element7with different axial stiffness at tensile and compression stress. In the position shown, advantages with regard to the fail-safe-behavior result from the chained arrangement of the respective joint yoke2with the associated connection yoke29, since the spatial association of the connection yoke29with respect to the associated joint yoke2is maintained in case of a failure of the elastic coupling element7.

In other regards, the embodiment according to theFIGS. 3 and 4corresponds to the embodiment according toFIGS. 1 and 2.

A third advantageous embodiment of the universal joint1according to the invention is shown in theFIGS. 5 and 6.

In this embodiment, the pins11reach, equidirectionally in relation to the middle axis22of the joint, into the associated joint yoke2or into the bearings13placed therein.

The connection elements9are formed as additional connection yoke32in a different way than in the explanations of the examples pertaining toFIGS. 1 to 4.

The joint yoke32has a base web17at each end of which the transversal web18is arranged which is associated with the pin section19with the pin11. The pins11extend with their free end23in the same direction, one of the pins, respectively, being oriented towards the middle axis22of the joint and the other one away from it. One of the pins, namely the pin11, which points with its free end23towards the middle axis22of the joint, with its free end23reaches into the bearing13in a direction from the outer side24towards the internal space6, its opposite pin11, namely the pin11, which points with its free end23away from the middle axis22of the joint, reaches into the bearing13in a direction from the internal space6outer side24towards outer side24. Therefore, the pins11of the same connection yoke29reach in to the bearing13alternately. On the one hand, the pin section19abuts the side of the bearing13pointing towards the outer side24. On the other hand, the pin section19opposite thereto abuts the side of the bearing13pointing towards the internal space6. Therefore, the connection yoke29is supported alternately, namely once abutting the outside of the yoke and once abutting the inside of the yoke.

In order to obtain this alternate bearing, the connection yoke32has a base web17which, in relation to the middle axis22of the joint, has differently distanced transversal webs18so that the transversal webs18that are arranged opposite each other are arranged, on the one hand, on the outside, and on the other, on the inside. In the exemplary embodiment shown inFIG. 5, the base web17has a length corresponding to the length of the base web33of the joint yoke. However, the joint yokes2, relative to the respectively associated connection yokes29, are shifted radially by different degrees in the universal joint1, in relation to the middle axis22of the joint.

As in the exemplary embodiment according toFIGS. 1 and 2, connection areas26or the appendages27are provided for the connection of the connection elements32with the elastic coupling element7.

The elastic coupling element7according to the exemplary embodiments of theFIGS. 3 to 6, is again formed preferably as a torsion-resistant, flexural elastic or axially elastic disk, preferably as a Hardy disk, and is disposed in the internal space6. Of course, the elastic coupling element7may also be formed as a torsion-resistant, flexural elastic or axially elastic ring or annulus and be disposed in the internal space6. Like the joint yokes2with their yoke arms12, the additional joint yokes14,29,32are formed substantially U-shaped, when seen in a side view.

A forth exemplary embodiment of the universal joint1according to the invention is shown in theFIGS. 7 and 8.

In this embodiment, the pins11, in relation to an axis22of symmetry each reach counter-directionally into the associated yoke arms12or the bearings13placed therein, as described in the exemplary embodiment according toFIGS. 1 and 2.

The connection elements9are formed as additional connection yokes34with a base web36, which protrudes over the transversal webs18with one collar37, respectively, which is directed away from the axis of symmetry22. When seen in a side view (FIG. 7), the respective connection yoke34is formed corresponding the Greek letter pi, as it were, the transversal webs18forming parallel pi-arms outside of the joint yokes2or their yoke arms12.

As in the exemplary embodiment according to theFIGS. 1 and 2, the pins11with their free ends23are oriented from an outer side24opposite the internal space6towards the internal space6. The pin section19and thus, the pin11is arranged on the outside on the joint yokes2or their yoke arms12in relation to the axis of symmetry22, the pin section19abutting a side of the bearings13pointing towards the outer side23. The transversal web18grasps the yoke arms12so that the pin11can reach into the bearings13from the outer side24.

The elastic coupling element7is guided around the outer sides24of the joint yokes2or their yoke arms12as a torsion-resistant, flexural elastic or axially elastic ring, or annulus and is connected with the collar37. The elastic coupling element preferably consists of a rubber, which is why a screw joint, a rivet joint or the like can be selected as a connection. Vulcanization is also possible.

A fifth exemplary embodiment of the universal joint1according to the invention is shown in theFIGS. 9 and 10. In contrast to the embodiment shown inFIGS. 7 and 8, the pins11with their free ends23reach into the joint yokes12or the bearings placed therein13in a direction oriented from the internal space6towards the outer side24opposite the internal space6, as described with regard to the exemplary embodiment according to theFIGS. 3 and 4. As in the exemplary embodiment according toFIGS. 7 and 8, the pins11, in relation to an axis symmetry22each reach counter-directionally into the respectively associated bearing13placed therein.

The connection elements9are formed as additional connection yokes38with the base web36. When seen in a side view, the respective connection yoke38is formed corresponding to the Greek letter pi, as it were, the transversal webs18forming parallel pi-arms within the joint yokes2or their yoke arms12.

A sixth exemplary embodiment of the universal joint1according to the invention is shown in theFIGS. 11 and 12. The connection elements9are formed as additional connection yoke39in a different way than in the explanations of the examples pertaining toFIGS. 7 to 10. Also, the joint yokes2are arranged excentrically in relation to the middle axis of the joint22, in contrast to theFIGS. 7 to 10.

The joint yoke39has a base web36on which the transversal web18is respectively arranged, which is associated with the pin section19with the pin11. On the base web36, the collars37are arranged again. The pins11with their free end23oriented in the same direction on the one hand point towards the middle axis22of the joint and on the other, away from it. One of the pins11which points with its free end23towards the middle axis22of the joint, with its free end23reaches into the bearing13in a direction from the outer side24towards the internal space6, its opposite pin11which points with its free end23away from the middle axis22of the joint, reaching into the bearing13in a direction from the internal space6outer side24towards outer side24. Therefore, the pins11of the same connection yoke39reach in to the bearing13alternately. On the one hand, the pin section19abuts the side of the bearing13pointing towards the outer side24. On the other hand, the pin section19opposite thereto abuts the side of the bearing13pointing towards the internal space6. Therefore, the connection yoke39is supported alternately, namely once on the outside and once on the inside.

In order to obtain this alternate bearing, the connection yoke39has the base web36which, in relation to the middle axis22of the joint, has differently distanced transversal webs18so that the transversal webs18that are arranged opposite each other are arranged, on the one hand, on the outside, and on the other, on the inside. In the exemplary embodiment shown inFIG. 11, the base web36has a length corresponding to the length of the base web33of the joint yoke. However, the joint yokes2, with respect to the respectively associated connection yokes39, are shifted axially opposite in relation to the middle axis22of the joint.

In the exemplary embodiments according to theFIGS. 9 to 12, the elastic coupling element7is again formed as a torsion-resistant, flexural elastic or axially elastic ring, or annulus that is guided around the outer sides24of the joint yokes2or their yoke arms12, as described already in the exemplary embodiment according to theFIGS. 7 and 8. The elastic coupling element7is respectively connected with the collar37that is arranged, with respect to the middle axis22of the joint, on both sides. A screw joint, rivet joint, vulcanization or the like can be provided as the connection.

In the universal joint1according to the exemplary embodiments 1 to 12, an input moment (direction of rotation41) is transmitted via the driven shaft3(drive shaft) via the joint yoke2onto the pair of connection elements8pivoted therein or onto the connection elements9,14,29,32,34,38,39respectively supported in the opposite joint arms12, and thence, as tensile/compression stress, onto the elastic coupling means7to the crossing connection elements9,14,29,32,34,38,39and then on to the joint yoke2of the shaft4to be driven or drive shaft. This is represented by means of the output moment (direction of rotation42) that is equidirectional with the input moment (direction of rotation41). With regard to the bending stiffness required to a small degree, the elastic coupling element7is selected such that it is ensured that a rotation of the connection element9,14,29,32,34,38,39or its pin21can take place during an inclination (inclination43) and rotation of the joint yoke2in order to overcome the friction torque according to the selected bearing clearance in the bearings13. In axial direction, the elastic coupling element7thus permits a compliance that can be used for insulation, while the contour of the elastic coupling element7provides a high torsional stiffness.

Advantageously, the universal joint1can be formed smaller if formed according to theFIGS. 7 to 12, with a coupling element7formed as a ring, than if formed according to the example pertaining to theFIGS. 1 to 6, while an axial flexibility can be increased at the same rotational stiffness.

The universal joint1shown in theFIGS. 1 to 12is particularly suitable for use in a steering column of a motor vehicle. The shafts3and4are shown oriented in alignment towards each other. In the vehicle, there usually is an angled position, relative to each other, with the universal joint maintaining the transmission of the rotation. The angled position is shown inFIGS. 1 and 3by means of the angle of inclination43.

Furthermore, a securing element44that can be associated with the respective free end23of the pin11is provided in theFIGS. 5,6,11and12. The securing element44may, for example, be formed as a shaft securing ring. For supporting the securing element44at the pin11, a groove may be placed in the pin11at a suitable location. Of course, such a securing element can be provided in all other exemplary embodiments.