Abstract:
A universal joint comprises first and second joint yokes, each joint yoke having axially opposite yoke arms, and inner and outer sides with respect to an axis of symmetry of the joint; first and second connection elements, each having transverse arms for connecting the connection element to yoke arms of a respective joint yoke and a base web extending beyond the transverse arms in a direction away from the axis of symmetry of the joint; and an elastic coupling element guided around outer sides of the joint yokes and connected to the base web of each connection element at a location beyond the transverse arms in a direction away from the axis of symmetry of the joint.

Description:
This is a division of application Ser. No. 11/276,053 filed on Feb. 10, 2006 U.S. Pat. No. 7,517,283, which claims the benefit of European Patent 05100999.1, filed Feb. 11, 2005, both of which are incorporated herein by reference. 
     The present invention is related to U.S. Pat. No. 7,445,555 entitled “Axial Insulation for a Universal Joint”, U.S. patent application serial number 11/276,049 entitled “Axial Insulation for a Universal Cross Joint”, U.S. Pat. No. 7,445,554 entitled “Insulation for Universal Cross Joint”, and U.S. Pat. No. 7,488,256 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 causes 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 is connected with the driven shaft and the other joint yoke is 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 equi-directionally, 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. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       Further advantageous embodiments of the invention are disclosed in the dependent claims and the following description of the figures. In the figures: 
         FIG. 1  shows a side view of a universal joint, 
         FIG. 2  shows a representation along a section A from  FIG. 1 , 
         FIG. 3  shows a longitudinal section of a universal joint in a second embodiment, 
         FIG. 4  shows a representation along a section A from  FIG. 3 , 
         FIG. 5  shows a side view of a universal joint in a third embodiment, 
         FIG. 6  shows a representation along a section A from  FIG. 5 , 
         FIG. 7  shows a side view of a universal joint in a fourth embodiment, 
         FIG. 8  shows a representation along a section A from  FIG. 7 , 
         FIG. 9  shows a side view of a universal joint in a fifth embodiment, 
         FIG. 10  shows a representation along a section A from  FIG. 9 , 
         FIG. 11  shows a side view of a universal joint in a sixth embodiment, and 
         FIG. 12  shows a representation along a section A from  FIG. 11 . 
     
    
    
     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 
     The  FIGS. 1 to 12  show a universal joint  1  having two joint yokes  2 . In  FIGS. 1 and 2 , one of the joint yokes  2  is connected to a driven shaft  3  or drive shaft  3 , the other joint yoke  2  being connected to the shaft  4  to be driven or drive shaft  4 . The two joint yokes  2  are arranged twisted radially at an angle of 90° in relation to each other so that the two joint yokes  2  form an internal space  6 . An elastic coupling element  7  is associated with the universal joint  1 . A pair  8  of connection elements formed of two identical, spatially separate connection elements  9  is associated with the joint yokes  2 . The connection elements  9  with their pins  11  respectively arranged thereon are pivoted in bearings  13  in the respectively associated joint yokes  2  or in their yoke arms  12 . The connection elements  9  are connected with each other via the elastic coupling element  7 . Because of the selected side view in the  FIGS. 1 ,  5 ,  7 ,  9  and  11 , or because of the selected longitudinal section in  FIG. 3 , only one joint yoke  2 ,  102 ,  202 ,  302 ,  402 ,  502 , respectively, with its two yoke arms  12 ,  112 ,  212 ,  312 ,  412 ,  512 , or only one connection element  9 ,  109 ,  209 ,  309 ,  409 ,  509  with its two transversal webs  18 ,  118 ,  218 ,  318 ,  418 ,  518  are discernible in their entirety. 
     The bearings  13  in the yoke arms  12  are 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 bearings  13  per joint yoke  2  is able to accept radial joint forces in addition to the axial joint forces. The bearings  13  are fixed in a suitable manner, radially relative to an axis of the joint, in the joint yokes  2  or their yoke arms  12 . 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 yokes  2  or their joint arms  12 . 
     In the  FIGS. 1 to 6 , the connection elements  9 ,  109 ,  209  are formed as additional connection yokes  14 ,  29 ,  32 ;  114 ,  129 ,  132 ;  214 ,  229 ,  232 . The connection yokes  14 ,  29 ,  32 ;  114 ,  129 ,  132 ;  214 ,  229 ,  232  each have a base web  17 ,  117 ,  217  and transversal arms  18 ,  118 ,  218  arranged on the end thereof. The transversal arms  18 ,  118 ,  218  merge into a pin section  19 ,  119 , which respectively bears the pin  11 ,  111 ,  211 . 
     In the embodiment shown in  FIGS. 1 and 2 , the pins  11 , in relation to a middle axis  22  of the joint, each reach counter-directionally into the associated yoke arms  12  or the bearings  13  placed therein. With their free ends  23 , the pins  11  are oriented from an outer side  24  opposite the internal space  6  towards the internal space  6 . The pin section  19  and thus, the pin  11 , is arranged on the outside of the joint yokes  2  or their yoke arms  12  in relation to the middle axis  22  of the joint, the pin section  19  abutting a side of the bearings  13  pointing towards the outer side  24 . Seen in the side view, therefore, the connection yokes  14  are slightly bigger than the joint yokes  2  or the symmetrical joint yokes  2  in order to grasp them with their transversal web  18  so that the pin  11  can reach into the bearings  13  from the outer side  24 . 
     For the connection with the elastic coupling element  7 , the base web  17  has attached connection areas  26  that are each offset in relation to the middle axis  22  of the joint. In relation to the axis of symmetry  22 , the connection areas  26  have the same distance, and extend as appendages  27  axially in the direction towards the internal space  6 . In this way, an axial interspace is created between the elastic coupling element  7  and the respective connection element  9  or the middle of its respective transversal web  18 , which provides an axial clearance. This axial interspace can be produced by material integration of the connection areas  26  into the elastic coupling element  7  (as illustrated, for example, in  FIGS. 3 and 4 ), together with a simplification of the transversal webs  18  of the connection elements  9 . 
     The elastic coupling element  7 , in the exemplary embodiment shown in the  FIGS. 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 areas  26  or the appendages  27  in the internal space  6 . However, it is also conceivable that the elastic coupling element  7  in the embodiment according to the  FIGS. 1 and 2  may be formed as a torsion-resistant, flexural elastic or axially elastic ring or annulus. The elastic coupling element  7  consists 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 element  9  or the appendages  27  arranged on the connection yokes  14 . In the  FIGS. 1 and 2 , the connection is in principle represented by a chain-dotted line  28 . 
     A further embodiment of the universal joint according to the invention is shown in the  FIGS. 3 and 4 . In contrast to the exemplary embodiment shown in  FIGS. 1 and 2 , the pins  111  with their free end  123  reach into the joint yokes  102  or the bearings placed therein  113  in a direction oriented from the internal space  106  towards the outer side  124  opposite the internal space  106 , but nevertheless counter-directionally in relation to the axis of symmetry  122 . 
     In this embodiment, the connection elements  109  are formed as additional connection yokes  129 . The connection yokes  129  have, like the connection yoke  14  of the embodiment according to the  FIGS. 1 and 2 , the base web  117  and transversal arms  118  arranged on the end thereof. The transversal arms  118  merge into the pin section  119  which respectively bears the pin  111 . 
     With their base web  117 , the joint yokes  129  are designed shorter than in the embodiment according to  FIG. 1 , because the transversal web  118  extends into the internal space  106 . Thus, the pin section  119  with its pin is also arranged in the internal space  106 , the pin section  119  abutting a side of the bearing  113  that points towards the internal space  106 . 
     The connection yokes  129 , seen in a side view, are formed smaller than a yoke width of the joint yokes  112  opposite each other, so that the joint yokes  129  can reach into the bearing  113  from the inside with their transversal web  118  or the pin section  119  with the pin  111 . 
     The connection of the elastic coupling element  107  with the connection element  129  takes place directly at the base web  117 . The axial clearance is achieved by round, attached screwed eyes  131  associated with the elastic coupling element  107 , which is why, advantageously, a contouring of the connection yokes  129  corresponding to a contouring of the joint yokes  114  can be omitted. 
     In the  FIGS. 3 to 4 , the connection elements  109  can also be operated, in principle, rotated by 180° in the bearings  113  fastened against the elastic coupling element  107 , which provides for additional adjustment options in the elastic coupling element  107  with 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 yoke  102  with the associated connection yoke  129 , since the spatial association of the connection yoke  129  with respect to the associated joint yoke  102  is maintained in case of a failure of the elastic coupling element  107 . 
     In other regards, the embodiment according to the  FIGS. 3 and 4  corresponds to the embodiment according to  FIGS. 1 and 2 . 
     A third advantageous embodiment of the universal joint according to the invention is shown in the  FIGS. 5 and 6 . 
     In this embodiment, the pins  211  reach, equidirectionally in relation to the middle axis  222  of the joint, into the associated joint yoke  202  or into the bearings  213  placed therein. 
     The connection elements  209  are formed as additional connection yoke  232  in a different way than in the explanations of the examples pertaining to  FIGS. 1 to 4 . 
     The joint yoke  232  has a base web  217  at each end of which the transversal web  218  is arranged which is associated with the pin section with the pin  211 . The pins  211  extend with their free end  223  in the same direction, one of the pins, respectively, being oriented towards the middle axis  222  of the joint and the other one away from it. One of the pins, namely the pin  211 , which points with its free end  223  towards the middle axis  222  of the joint, with its free end  223  reaches into the bearing  213  in a direction from the outer side  224  towards the internal space  206 , its opposite pin  211 , namely the pin  211 , which points with its free end  223  away from the middle axis  222  of the joint, reaches into the bearing  213  in a direction from the internal space  206  outer side  224  towards outer side  224 . Therefore, the pins  211  of the same connection yoke  229  reach in to the bearing  213  alternately. On the one hand, the pin section abuts the side of the bearing  213  pointing towards the outer side  224 . On the other hand, the pin section opposite thereto abuts the side of the bearing  213  pointing towards the internal space  206 . Therefore, the connection yoke  229  is 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 yoke  232  has a base web  217  which, in relation to the middle axis  222  of the joint, has differently distanced transversal webs  218  so that the transversal webs  218  that 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 in  FIG. 5 , the base web  217  has a length corresponding to the length of the base web  233  of the joint yoke. However, the joint yokes  202 , relative to the respectively associated connection yokes  229 , are shifted radially by different degrees in the universal joint, in relation to the middle axis  222  of the joint. 
     As in the exemplary embodiment according to  FIGS. 1 and 2 , connection areas  226  or the appendages  227  are provided for the connection of the connection elements  232  with the elastic coupling element  207 . 
     The elastic coupling element  107 ,  207  according to the exemplary embodiments of the  FIGS. 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 space  106 ,  206 . Of course, the elastic coupling element  107 ,  207  may also be formed as a torsion-resistant, flexural elastic or axially elastic ring or annulus and be disposed in the internal space  106 ,  206 . Like the joint yokes  102 ,  202  with their yoke arms  112 ,  212 , the additional joint yokes  129 ,  232  are formed substantially U-shaped, when seen in a side view. 
     A fourth exemplary embodiment of the universal joint according to the invention is shown in the  FIGS. 7 and 8 . 
     In this embodiment, the pins  311 , in relation to an axis  322  of symmetry each reach counter-directionally into the associated yoke arms  312  or the bearings  313  placed therein, as described in the exemplary embodiment according to  FIGS. 1 and 2 . 
     The connection elements  309  are formed as additional connection yokes  334  with a base web  336 , which protrudes over the transversal webs  318  with one collar  337 , respectively, which is directed away from the axis of symmetry  322 . When seen in a side view ( FIG. 7 ), the respective connection yoke  334  is formed corresponding the Greek letter pi, as it were, the transversal webs  318  forming parallel pi-arms outside of the joint yokes  302  or their yoke arms  312 . 
     As in the exemplary embodiment according to the  FIGS. 1 and 2 , the pins  311  of  FIGS. 7 and 8  have free ends  323  that are oriented from an outer side  324  opposite the internal space  306  towards the internal space  306 . The pin section  319  and the pin  311  are arranged on the outside of the joint yokes  302  or their yoke arms  312  in relation to the axis of symmetry  322 , the pin section  319  abutting a side of the bearings  313  pointing towards the outer side  323 . The transversal web  318  grasps the yoke arms  312  so that the pin  311  can reach into the bearings  313  from the outer side  324 . 
     The elastic coupling element  307  is guided around the outer sides  324  of the joint yokes  302  or their yoke arms  312  as a torsion-resistant, flexural elastic or axially elastic ring, or annulus and is connected with the collar  337 . 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 joint according to the invention is shown in the  FIGS. 9 and 10 . In contrast to the embodiment shown in  FIGS. 7 and 8 , the pins  411  with their free ends  423  reach into the joint yokes  412  or the bearings placed therein  413  in a direction oriented from the internal space  406  towards the outer side  424  opposite the internal space  406 , as described with regard to the exemplary embodiment according to the  FIGS. 3 and 4 . As in the exemplary embodiment according to  FIGS. 7 and 8 , the pins  411  of  FIGS. 9 and 10 , in relation to an axis of symmetry  422 , each reach counter-directionally into the respectively associated bearing  413  placed therein. 
     The connection elements  409  are formed as additional connection yokes  438  with the base web  436 . When seen in a side view, the respective connection yoke  438  is formed corresponding to the Greek letter pi, as it were, the transversal webs  418  forming parallel pi-arms within the joint yokes  402  or their yoke arms  412 . 
     A sixth exemplary embodiment of the universal joint according to the invention is shown in the  FIGS. 11 and 12 . The connection elements  509  are formed as additional connection yoke  539  in a different way than in the explanations of the examples pertaining to  FIGS. 7 to 10 . Also, the joint yokes  502  are arranged eccentrically in relation to the middle axis of the joint  522 , in contrast to the  FIGS. 7 to 10 . 
     The joint yoke  539  has a base web  536  on which the transversal web  518  is respectively arranged, which is associated with the pin section  519  with the pin  511 . On the base web  536 , the collars  537  are arranged again. The pins  511  have their free ends  523  oriented in the same direction, and on one side point towards the middle axis  522  of the joint and on the other side point away from it. One of the pins  511  which points with its free end  523  towards the middle axis  522  of the joint, with its free end  523  reaches into the bearing  513  in a direction from the outer side  524  towards the internal space  506 , its opposite pin  511  points with its free end  523  away from the middle axis  522  of the joint, reaching into the bearing  513  in a direction from the internal space  506  towards outer side  524 . Therefore, the pins  511  of the same connection yoke  539  reach in to the bearing  513  alternately. On one yoke arm, the pin section  519  abuts the side of the bearing  513  pointing towards the outer side  524 . On the other yoke arm, the pin section  519  abuts the side of the bearing  513  pointing towards the internal space  506 . Therefore, the connection yoke  539  is supported alternately, namely once on the outside and once on the inside. 
     In order to obtain this alternate bearing, the connection yoke  539  has the base web  536  which, in relation to the middle axis  522  of the joint, has differently distanced transversal webs  518  so that the transversal webs  518  that 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 in  FIG. 11 , the base web  536  has a length corresponding to the length of the base web  533  of the joint yoke. However, the joint yokes  502 , with respect to the respectively associated connection yokes  539 , are shifted axially oppositely in relation to the middle axis  522  of the joint. 
     In the exemplary embodiments according to the  FIGS. 9 to 12 , the elastic coupling element  407 ,  507  is again formed as a torsion-resistant, flexural elastic or axially elastic ring, or annulus that is guided around the outer sides  424 ,  524  of the joint yokes  402 ,  502  or their yoke arms  412 ,  512 , as described already in the exemplary embodiment according to the  FIGS. 7 and 8 . The elastic coupling element  407 ,  507  is respectively connected with the collar  437 ,  537  that is arranged on both sides of the middle axis  422 ,  522  of the joint. A screw joint, rivet joint, vulcanization or the like can be provided as the connection. 
     In the universal joint according to the exemplary embodiments of  FIGS. 1 to 12 , an input moment (direction of rotation  41 ) is transmitted via the driven shaft  3  (drive shaft) via the joint yoke  2 ,  102 ,  202 ,  302 ,  402 ,  502  onto the pair of connection elements pivoted therein or onto the connection elements respectively supported in the opposite joint arms  12 ,  102 ,  202 ,  302 ,  402 ,  502 , and thence, as tensile/compression stress, onto the elastic coupling means  7 ,  107 ,  207 ,  307 ,  407 ,  507  to the crossing connection elements and then on to the joint yoke  2 ,  102 ,  202 ,  302 ,  402 ,  502  of the shaft  4  to be driven or drive shaft. This is represented by means of the output moment (direction of rotation  42 ) that is equidirectional with the input moment (direction of rotation  41 ). With regard to the bending stiffness required to a small degree, the elastic coupling element  7 ,  107 ,  207 ,  307 ,  407 ,  507  is selected such that it is ensured that a rotation of the connection element or its pin can take place during an inclination (inclination  43 ) and rotation of the joint yoke  2 ,  102 ,  202 ,  302 ,  402 ,  502 , in order to overcome the friction torque according to the selected bearing clearance in the bearings  13 ,  113 ,  213 ,  313 ,  413 ,  513 . In an axial direction, the elastic coupling element  7 ,  107 ,  207 ,  307 ,  407 ,  507  thus permits a compliance that can be used for insulation, while the contour of the elastic coupling element  7 ,  107 ,  207 ,  307 ,  407 ,  507  provides a high torsional stiffness. 
     Advantageously, the universal joint can be formed smaller if formed according to  FIGS. 7 to 12 , with a coupling element  307 ,  407 ,  507  formed as a ring, than if formed according to the example pertaining to the  FIGS. 1 to 6 , while an axial flexibility can be increased at the same rotational stiffness. 
     The universal joint shown in the  FIGS. 1 to 12  is particularly suitable for use in a steering column of a motor vehicle. The shafts  3  and  4  are 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 in  FIGS. 1 and 3  by means of the angle of inclination  43 . 
     Furthermore, a securing element  244 ,  544  that can be associated with the respective free end  23 ,  123 ,  223 ,  323 ,  423 ,  523  of the pin  11 ,  111 ,  211 ,  311 ,  411 ,  511  is provided in the  FIGS. 5 ,  6 ,  11  and  12 . The securing element  244 ,  544  may, for example, be formed as a shaft securing ring. For supporting the securing element  244 ,  544  at the pin  11 ,  111 ,  211 ,  311 ,  411 ,  511 , a groove may be placed in the pin  11 ,  111 ,  211 ,  311 ,  411 ,  511  at a suitable location. Of course, such a securing element can be provided in all other exemplary embodiments.