TECHNICAL FIELD 
       [0001]    The present invention relates to a device for the vibration-reduced transmission of torques between two shaft sections running along a longitudinal axis. 
       BACKGROUND 
       [0002]    Such devices are known from the prior art and are used, for example, to transmit torques in a steering column or in a drive train of a motor vehicle. Precisely in these applications it is necessary to use torque transmission devices which are constructed as compactly as possible on account of the ever-decreasing installation spaces and increasing torque requirements and which couple the shaft sections to one another with damping of torsional oscillations. In particular, such torque transmission devices are required to transmit the torques in as loss-free a manner as possible from one shaft section to the other shaft section, but sufficiently damp vibrations and torsional oscillations which occur, so as not to transmit, for example, structure-borne noise arising at the drive axle through the vehicle. For this reason, torque transmission devices are provided with damping elements which can compensate for such vibrations or torsional oscillations. 
         [0003]    It is the object of the present invention to provide a device for the vibration-reduced transmission of torques of the type referred to at the outset which meets the increased requirements placed on the torque transmission with a compact construction. 
       SUMMARY 
       [0004]    This object is achieved by a device for the vibration-reduced transmission of torques between two shaft sections in a shaft arrangement comprising two transmission parts that interact in a torque-transmitting manner in a coupling area, wherein each of the transmission parts has a protruding claw formation, which is received in a receiving area for the transmission of torque from the respectively other transmission part, wherein a damping device is provided between the transmission parts, wherein each of the transmission parts also has a closed bearing ring with a bearing opening, which receives and supports an axial positioning pin, and wherein the bearing ring is integrally connected to the associated claw formation of the respective transmission part and extends axially into the receiving area. Owing to the use of transmission parts with claw formations protruding in the axial direction, it is possible to transmit even high torques between the shaft sections in a largely loss-free manner, while providing sufficient constructional possibilities for accommodating the vibration-reducing damping device. Furthermore, the transmission parts can each be supported or be mutually guided on a positioning pin, whereby undesired deflections or diffractions of the transmission parts relative to one another can be prevented in the entire rotational speed range and thus also at high centrifugal forces. 
         [0005]    In order to achieve radial guidance of the two transmission parts over the entire length of the torque transmission device, a development of the invention provides that the claws of the claw formation of the one transmission part are received in corresponding receiving openings of the other transmission part. Thus, the claws of the claw formations of the one transmission part are received in the receiving openings, arranged around the closed bearing ring, of the respectively other transmission part, whereby the transmission parts are mutually guided and owing to the closed bearing rings a continuous support of the transmission parts on the positioning pin is possible. In other words, owing to the closed bearing rings and their bearing openings, the bearings are adapted to the length of the torque transmission device, whereby an inexpedient double-joint formations is avoided. 
         [0006]    According to a preferred embodiment of the invention, it is provided that the shape of the radially inner section of the claw formation of the one transmission part is adapted to the shape of the closed bearing ring of the respectively other transmission part. In other words, the claws of the claw formation of the one transmission part are formed in such a way that they correspond to the shape of the bearing ring of the other transmission part, whereby mutual guidance of the transmission parts over the entire length of the torque transmission device is possible. 
         [0007]    In order to achieve an as far as possible play-free and low-friction guidance of the two transmission parts, according to a preferred embodiment, between the bearing rings of the transmission parts there is provided on the positioning pin a positioning sleeve, and at the outer circumference of the torque transmission device between the transmission parts a slide bush is arranged. In the context of a play-free and low-friction support of the transmission parts by the bearing rings on the positioning pin it should be mentioned that the transmission parts are supported on the positioning pin by means of bearing bushes which are adapted to the length of the bearing rings. According to a preferred embodiment of the invention, the transmission parts are axially braceable by means of the positioning pin. 
         [0008]    For the damping of torsional oscillations, a development of the invention provides that the damping device has at least two damping material coatings, in particular rubber coatings, in each case one damping material coating surrounding the claw formation and the receiving area of one of the transmission parts. These damping material coatings may have a progressive characteristic, i.e. on increasing pressing display decreasing damping behaviour with increasing rigidity. 
         [0009]    In order to achieve as progressive a characteristic of the damping material coatings of the damping device as possible, a development of the invention provides that the claw formations and the receiving areas have indentations at their end running in the direction of the centre axis and that the damping material coating has a bulging thickening in the region of the indentations of the claws. The bulging thickenings of the damping material coatings in the region of the indentations act as an integrated predamper inside the compression-loaded damping device, i.e. in the region in which the claws are applied against the corresponding receiving openings in the event of loading. In other words, firstly the material coatings in the region of these thickenings are deformed, whereby a stepped damping behaviour of the damping device results. 
         [0010]    According to a preferred embodiment of the invention, the claw formation of at least one of the transmission parts is at least partially covered with a first material, the vibration-reducing damping device between the claw formations of the two transmission parts being made of a second material. Owing to the use of transmission parts with claw formations protruding in the axial direction, it is possible to transmit even torques of large magnitude in a largely loss-free manner between the shaft sections. There are a variety of constructional possibilities here for accommodating a coating made of a first material on the metal components and a vibration-reducing damping device made of a second material. By applying a first material coating between the claw formations of the transmission parts and the vibration-reducing damping device made of a second material, possibilities of adapting the torque transmission device are obtained. In other words, the torque transmission device can be adapted by the first material coating to its area of application, i.e. drive train or steering column, and the particular type of vehicle or the rotational-speed and torque requirements. 
         [0011]    Furthermore, a simply producible basic shape can be chosen for the claws made of metal. If the claw shape is to be specially configured for the torque transmission and the damping of torsional oscillations, this can be achieved more simply with the first material, e.g. plastic, covering the claws. Moreover, it is thus possible to avoid costly pretreatment of the metallic claw base body for subsequent vulcanising-on of rubber, since the rubber material is vulcanised onto the first material which constitutes the covering. 
         [0012]    Thus, a preferred embodiment of the invention provides that the claw formations of the transmission parts are at least partially covered with plastic, in particular with a high-strength polyamide material, as the first material. The plastic which covers the claw formations of the transmission parts can be easily brought into a preferred shape for the torque transmission and for the mounting of the damping device made of a second material. In other words, for the basic shape of the claw formations made of metal, geometric shapes which are simple to produce are chosen and, specifically for the torque transmission and damping of torsional oscillations, advantageous formations of the claws are subsequently formed from plastic. The latter is injection-moulded directly onto the metal components and can be brought into the desired shape simply and inexpensively. 
         [0013]    In this context, a particularly simple and inexpensively producible embodiment of the invention provides that the two transmission parts are substantially uniformly designed in the coupling area. The use of substantially identical transmission parts results in a less complicated and thus less expensive production of the device according to the invention. 
         [0014]    With regard to the damping device, it is provided that the latter has a damping coating made of a second material, in particular rubber, between the claw formations of the transmission parts, which claw formations can be brought into engagement with one another and are covered with the first material. This damping coating may have a progressive characteristic, i.e. on increasing pressing display decreasing damping behaviour with increasing rigidity. A preferred embodiment of the invention provides that each of the claw formations of the transmission parts covered with the first material has in each case a damping material coating, in particular a rubber coating. In this context, it should further be mentioned that the at least one damping coating made of the second material may be further provided with additional insert parts, in particular made of plastic. Owing to these insert parts, the damping coating made of the second material is further stiffened, whereby a progressive damping characteristic is achieved. In other words, on increasing pressing, the insert parts move closer to the plastic coating covering the claw formation, whereby the rigidity of the torque transmission device rapidly increases at the end of the compression of the rubber coatings. 
         [0015]    In order to achieve an as progressive a characteristic in the damping device as possible, a development of the invention provides that the coverings of the claw formations made of the first material have indentations at their end running in the direction of the centre axis and that the damping coating made of the second material has a bulging thickening in the region of the indentations of the covering of the claw formations made of the first material. The bulging thickenings of the damping material coating in the region of the indentations act as an integrated predamper inside the compression-loaded damping device. In other words, in the event of loading, firstly the material coatings in the region of these thickenings are substantially deformed, whereby a stepped damping behaviour of the damping device results. 
         [0016]    According to the invention, it may further be provided that between the transmission parts there is provided a positioning pin, by means of which the device is axially braceable. The two transmission parts of the torque transmission device are supported on this positioning pin. Furthermore, between the transmission parts a central positioning sleeve may be arranged on the positioning pin. 
         [0017]    For the radial play-free support of the transmission parts on the positioning pin, a preferred embodiment of the invention provides that each of the transmission parts has a closed bearing ring with a bearing opening, which receives and supports the axial positioning pin, wherein the bearing ring is integrally connected to the associated claw formation of the respective transmission part and extends axially into a receiving area of the transmission parts. In this connection, it should further be mentioned that the claws of the claw formation of the one transmission part are received in corresponding receiving openings in the receiving area of the respectively other transmission part. Owing to the closed bearing ring and the simultaneous reception of the claws of the claw formation of the one transmission part in the corresponding receiving openings of the other transmission part, guidance over the entire length of the torque transmission device is achieved, whereby undesired radial deflections or diffractions on account of the centrifugal force at high rotational speeds, e.g. in a drive train, can be avoided. In addition, owing to the bearing rings with the associated bearing openings, the bearings are adapted to the length of the torque transmission device, whereby inexpedient formation of double joints can be avoided. 
         [0018]    The present invention further relates to a device for the vibration-reduced transmission of torques between two shaft sections in a shaft arrangement comprising two transmission parts that interact in a torque-transmitting manner in a coupling area, wherein each of the transmission parts has a receiving area, in which at least one protruding claw formations of an intermediate element engages for the transmission of torque, wherein a damping device is provided between the transmission parts and the intermediate element, wherein each of the transmission parts also has a closed bearing ring with a bearing opening, which receives and supports an axial positioning pin, and wherein the bearing ring is integrally connected to the associated claw formation of the respective transmission part and extends axially into the receiving area. 
         [0019]    A development of the invention provides that the intermediate element has a disc-shaped base element, from which claw formations protrude on both sides in the axial direction. 
         [0020]    According to the invention, the claw formation of the intermediate element is at least partially filled with an elastomer. 
         [0021]    A preferred embodiment of the invention provides that the claws of the claw formation of the intermediate element are received in corresponding receiving openings in the receiving area of one of the transmission parts. 
         [0022]    The invention further relates to a shaft arrangement having a device described above. 
     
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         [0023]    The invention is explained below by way of example with the aid of the accompanying figures, in which: 
           [0024]      FIGS. 1A and 1B  illustrate sectional views of a first embodiment of the invention; 
           [0025]      FIGS. 2A and 2B  illustrate sectional views of a second embodiment of the invention; 
           [0026]      FIGS. 3A and 3B  illustrate sectional views of a third embodiment of the invention; 
           [0027]      FIGS. 4 and 5  illustrate perspective views of a fourth embodiment; and 
           [0028]      FIGS. 6A and 6B  illustrate sectional views of the fourth embodiment of the invention. 
       
    
    
     DETAILED DESCRIPTION 
       [0029]    In  FIGS. 1A and 1B  a torque transmission device according to the invention is shown in each case in sectional views and denoted generally by  10 .  FIG. 1A  shows an axis-containing longitudinal section along the longitudinal axis A, whereas  FIG. 1B  shows an axially orthogonal section through the arrangement along the section line I-I from  FIG. 1A . 
         [0030]    As can be seen in  FIGS. 1A and 1B , the torque transmission device according to the invention has a first transmission part  12  and a second transmission part  14 . The two transmission parts  12  and  14  overlap in a coupling area  16 , said parts having in this coupling area  16  claw formations approximately circular sector-shaped in cross-section. The transmission part  12  has in total three claws  18 ,  20 ,  22  in each case offset by 120° with respect to one another. These claws  18 ,  20  and  22  project in the axial direction, as shown in  FIG. 1A  representatively for the claw  18 . Similarly, the transmission part  14  has a corresponding claw formation  24 ,  26 ,  28 , only the claw  28  being shown in  FIG. 1A . The claw formation  24 ,  26  and  28  is, in the same way, arranged in an axially protruding manner on the second transmission part  14  and approximately circular sector-shaped in cross-section. 
         [0031]    In  FIG. 1A  it can be seen that the transmission parts  12 ,  14  each have a receiving area  30 ,  32 , in which the claw formation of the respectively other transmission part  12 ,  14  is received, in  FIG. 1A  only the claw  18  in the receiving area  32  of the transmission part  14  and correspondingly the claw  28  in the receiving area  30  of the transmission part  12 .  FIG. 1A  additionally shows the bearing rings  34  and  36  of the transmission parts  12 ,  14 , i.e. the bearing ring  34  of the transmission part  12  and the bearing ring  36  of the transmission part  14 . The bearing rings  34 ,  36  each have a bearing opening  38  and  40 , respectively, formed in them. In these bearing openings  38 ,  40  of the transmission parts  12 ,  14 , an axial positioning pin  42  is received in a supporting manner. The bearing rings  38 ,  40  are integrally connected to the claw formation associated with them, in  FIG. 1A  again only to the claws  18 ,  28  shown, of the respective transmission part  12 ,  14  and extend, as can be seen in  FIG. 1A , axially into the receiving areas  30 ,  32  of the transmission parts  12 ,  14 . 
         [0032]    It is thus also evident from  FIG. 1A  how deflections and diffractions of the transmission parts  12 ,  14  relative to one another can be avoided by the bearing rings  34 ,  36  and the bearing openings  38 ,  40 , since there is mutual guidance between the claw formations  18 ,  20 ,  22  or  24 ,  26 ,  28  and the bearing rings  34 ,  36  extending into the receiving areas  30 ,  32 , over the entire length of the torque transmission device. In other words, the claw formations  18 ,  20 ,  22  or  24 ,  26 ,  28  of the transmission parts  12 ,  14  are guided by the bearing rings  34 ,  36  in the receiving areas  30 ,  32 . Owing to the bearing openings  38 ,  40  in the bearing rings  34 ,  36 , a continuous support of the transmission parts  12 ,  14  on the positioning pin is achieved. A “continuous support” is to be understood in this context such that a formation of double joints is not possible and concomitant angular offsets between the transmission parts are effectively avoided. 
         [0033]    In addition,  FIG. 1B , which illustrates a sectional view along the section line I-I running through the receiving area  30  of the transmission part  12 , shows how the claws  24 ,  26 ,  28  of the transmission part  14  are received in corresponding receiving openings  44 ,  46 ,  48  in the receiving area  30  of the transmission part  12 . Owing to the bearing ring  34 , the receiving openings  44 ,  46 ,  48  are closed off radially inwards, whereby only the bearing ring  34  with its bearing opening  38  is responsible for the support of the transmission part  12  on the positioning pin. At the same time, mutual guidance of the transmission parts  12 ,  14  with their claw formations  18 ,  20 ,  22  and  24 ,  26 ,  28  is achieved by the receiving openings  44 ,  46 ,  48  and the bearing ring  34 , since no relative deflections of the transmission parts with respect to one another are possible on account of the reception of the claws  24 ,  26 ,  28  in the receiving openings  44 ,  46 ,  48  and of the bearing ring  34 . The fact that the claws  24 ,  26 ,  28  are adapted to the shape of the receiving openings  44 ,  46 ,  48  and radially inwards to the shape of the bearing ring  34  also contributes to this guidance. At their radially inner end, the claws  24 ,  26 ,  28  therefore have cylindrical segment-shaped indentations which are adapted to the shape of the bearing ring  34  of the transmission part  12 . 
         [0034]    Thus, on the one hand, deflections of the transmission parts  12 ,  14  relative to one another can be avoided owing to the receiving openings  44 ,  46 ,  48  and the bearing rings  34 ,  36  closing off these receiving openings  44 ,  46 ,  48  and, on the other hand, double-joint formations and concomitant angular offsets between the transmission parts  12 ,  14  can be avoided owing to the bearings formed by the closed bearing rings  34 ,  36  and their bearing openings  38 ,  40 , which bearings are adapted to the length of the torque transmission device  10 . 
         [0035]    In  FIG. 1A  there can further be seen bearing bushes  50 ,  52 , by means of which the transmission parts  12  and  14  are supported on the positioning pin  42 . The length of the bearing bushes  50 ,  52  is adapted to the length of the bearing rings  34 ,  36  associated with them. The bearing bushes  50 ,  52  contribute to an as far as possible frictionless support of the transmission parts  12 ,  14  on the positioning pin  42 . 
         [0036]    In the coupling area  16 , the two transmission parts  12  and  14  are each covered with a rubber coating  54 ,  56 . Specifically, a corresponding rubber coating  54  can be seen on the transmission part  12  and a corresponding rubber coating  56  can be seen on the claws  24 ,  26 ,  28  of the transmission part  14 . The two rubber coatings  54  and  56  are vulcanised directly onto the lateral surfaces of the claw formations  18 ,  20 ,  22  and  24 ,  26 ,  28 . The two corresponding rubber coatings constitute  54 ,  56  constitute a compression-loaded main damper device D. 
         [0037]    It can further be seen in  FIG. 1B  that the claw formations  18 ,  20 ,  22  and  24 ,  26 ,  28  have indentations  58  at their end leading up to the centre axis M. Provided on the rubber coatings  54 ,  56  in the region of the indentations  58  are bulging thickenings  60  which fill the indentations  58  and project in the direction of the next claw of one of the claw formation  18 ,  20 ,  22  or  24 ,  26 ,  28  in the circumferential direction. The indentations  58  and the bulging thickenings  60  act as a predamper integrated into the compression-loaded damping device D. 
         [0038]    Besides the compression-loaded damping device D, the torque transmission device  10  according to the invention further provides a torsion-loadable predamper device V. For the transmission of torques to the predamper device V, receiving dishes  62  and  64  which correspond to the claws  18 ,  28  and receive them in a form-fitting manner are provided. The number of receiving dishes  62 ,  64  corresponds to the number of claws of the claw formations  18 ,  20 ,  22  and  24 ,  26 ,  28 , only the receiving dishes  62  and  64  are shown here representatively. The receiving dishes  62  and  64  are each connected to one of the transmission parts  12  and  14  by a rubber coating  66 ,  68 , i.e. are vulcanised on. 
         [0039]    Arranged between the transmission parts  12  and  14  or between their bearing rings  38 ,  40  is a central spacing and positioning sleeve  70  which is intended to enable an as far as possible low-friction and play-free support of the transmission parts  12  and  14  on the positioning pin. For the guidance of the transmission parts  12  and  14 , a slide bush  71  is provided in their circumferential region. 
         [0040]    The transmission parts  12  and  14  further have a tubular section  72  and  74  in their end regions. The torque transmission device  10  according to the invention can be connected to, for example welded or pressed onto, a shaft section via these tubular sections  72  and  74 . However, other detachable connection possibilities are also conceivable, for example using a Hirth serration which can be formed on one of the transmission parts  12 ,  14  instead of the tubular section  72 ,  74 . 
         [0041]    Further embodiments of the invention are explained below with reference to  FIGS. 2A to 3B . To avoid repetition and to simplify the description, components acting in the same way or of the same kind use the same reference symbols as in the first exemplary embodiment, but preceded by a consecutive number. 
         [0042]    In  FIGS. 2A and 2B  show sectional views of the torque transmission device  110 . Thus,  FIG. 2A  shows an axis-containing longitudinal section along the longitudinal axis A, whereas  FIG. 2B  shows an axially orthogonal section through the arrangement.  FIG. 2B  has the section along the section line I-I from  FIG. 2A . 
         [0043]    As can be seen in  FIGS. 2A and 2B , the torque transmission device according to the invention has a first transmission part  112  and a second transmission part  114 . The two transmission parts  112  and  114  overlap in a coupling area  116 , said parts having in this coupling area  116  claw formations approximately circular sector-shaped in cross-section. The transmission part  112  has in total three claws  118 ,  120 ,  122  in each case offset by 120° with respect to one another. This claw formation  118 ,  120  and  22  projects in the axial direction, as shown in  FIG. 1  representatively for the claw  118 . Similarly, the transmission part  114  has a corresponding claw formation  124 ,  126 ,  128 , only the claw  128  being shown in  FIG. 2A . The claw formation  124 ,  126  and  128  is, in the same way, arranged in an axially protruding manner on the second transmission part  114  and approximately circular sector-shaped in cross-section. 
         [0044]    It can further be seen from  FIGS. 2A and 2B  that the claw formations  118 ,  120 ,  122  and  124 ,  126 ,  128  of the transmission parts  112  and  114  are covered with a coating of a first material  130  and  132 . Specifically, there can be seen a corresponding material coating  130  of plastic on the transmission part  12  and a corresponding material coating  132  of plastic on the transmission part  114 . The plastic is directly injection-moulded around the claws of the claw formations  118 ,  120 ,  122  and  124 ,  126 ,  128  to form the first material coatings  130 ,  132 . 
         [0045]    In this connection, it should be mentioned that besides the covering with plastic it is also possible to use other materials for covering the claw formations  118 ,  120 ,  122  and  124 ,  126 ,  128 . Owing to these options regarding the choice of material, the torque transmission device  110  can be adapted to its different areas of application in the steering column or the drive train but also to different vehicle types with different requirements for the torque transmission. Thus, for example, the damping behaviour of the torque transmission device  110  can be influenced in a desired manner already by the first material coatings  130 ,  132 . 
         [0046]      FIGS. 2A and 2B  additionally show that the claw formations  118 ,  120 ,  122  and  124 ,  126 ,  128  or their plastic coatings  130  and  132  are each covered with a rubber coating  134 ,  136  in the coupling area  116 . Thus, the rubber coating  134  can be seen on the claw formation  118 ,  120 ,  122  of the transmission part  112  and a corresponding rubber coating  136  can be seen on the claw formation  124 ,  126 ,  128  of the transmission part  114 . The two corresponding rubber coatings  134 ,  136  constitute a compression-loadable damping device D. 
         [0047]    The coverings  130 ,  132  of plastic of the claw formations  118 ,  120 ,  122  and  124 ,  126 ,  128  have indentations  138  at their end leading up to the centre axis M. Provided on the rubber coatings  134 ,  136  in the region of the indentations  138  are bulging thickenings  140  which fill the indentations  138  and project in the direction of the next claws of a claw formation  118 ,  120 ,  122  or  124 ,  126 ,  128  in the circumferential direction. The indentations  138  and the bulging thickenings  140  act as a predamper integrated into the compression-loaded damping device D. In the event of loading, i.e. in the operation of the torque transmission device  110 , firstly the material coatings in the region of the bulging thickenings  140  are deformed until a large-area contact of the coated claw formations occurs. This results in a stepped damping behaviour in the damping device D. 
         [0048]    As can be clearly seen in particular from  FIG. 2B , the claws of the claw formations  118 ,  120 ,  122  and  124 ,  126 ,  128  made of metal have a simple substantially regular shape which is simple to produce by various metal machining processes. The indentations  140 , which are more difficult to produce, are integrally provided in the coatings  130 ,  132  of plastic. Since the material for the coatings  130 ,  132  is plastic, shapings of this kind, such as, for example, the indentations  138 , can be simply produced during the injection-moulding around the claw formations  118 ,  120 ,  122  and  124 ,  126 ,  128 . Furthermore, the plastic for the first material coatings  130 ,  132  can be chosen in such a way that the rubber coatings  134 ,  136  directly bond to the plastic without additional adhesion promoters being required, whereby the production costs can be reduced. 
         [0049]    It can further be seen from  FIGS. 2A and 2B  that the transmission parts  112  and  114  each have a closed bearing ring  142  and  144  each with a bearing opening  146 ,  148  which receive an axial positioning pin  150  in a supporting manner, the bearing rings  142 ,  144  being integrally connected to the associated claw formation  118 ,  120 ,  122  or  124 ,  126 ,  128  of the respective transmission part  112  and  114  and extending axially into a receiving area  152  and  154  of the transmission parts  112  and  114 . In addition, owing to the bearing rings  142 ,  144  with the associated bearing openings  146 ,  148 , the bearings are adapted to the length of the torque transmission device  110 , whereby inexpedient formation of double joints can be avoided and resulting angular offsets of the transmission parts  112 ,  114  can be prevented. Formed in the receiving areas  152  and  154  of the transmission parts  112  and  114  are in each case receiving openings  156 ,  158 ,  160  ( FIG. 2B ) for receiving the claw formations  118 ,  120 ,  122  or  124 ,  126 ,  128  covered with the first material coating  130 ,  132 . Reference is made in this regard to  FIG. 2B  which shows a sectional view along the section line I-I running through the receiving area  152  of the transmission part  112 . 
         [0050]    In  FIG. 2B  the receiving openings  156 ,  158  and  160  in the receiving area  152  of the transmission part  112  can be seen. In addition, it is evident from  FIG. 2B  that the bearing ring  142  closes off the receiving openings  156 ,  158  and  160  radially inwards. Owing to the closed bearing rings  142 ,  144  of the transmission parts  112  and  114  and also the receiving openings  156 ,  158 ,  160 , mutual guidance of the transmission parts  112  and  114  over the entire length of the torque transmission device  110  is achieved. The transmission parts  112  and  114  are supported on the positioning pin  150  in a manner low in friction and substantially free of radial play via the bearing openings  146 ,  148  of the closed bearing rings  142 ,  144  via bearing bushes  164 ,  166 . In other words, owing to the closed bearing ring  134  and the simultaneous reception of the claws of the claw formation  124 ,  126 ,  128  of the transmission part  114  in the corresponding receiving openings  156 ,  158  and  160  of the transmission part  112 , guidance over the entire length of torque transmission device  110  is achieved, whereby undesired deflections or diffractions on account of the centrifugal force at high rotational speeds, for example on use in a drive train, can be avoided. 
         [0051]    Furthermore, between the closed bearing rings  142 ,  144  there is provided a central spacing and positioning sleeve  168  which is intended to enable an as far as possible axial play-free support of the transmission parts  112  and  114  on the positioning pin  150 . 
         [0052]    The transmission parts  112  and  114  have a tubular section  170 ,  172  in their end region. The torque transmission device  110  according to the invention can be connected to, for example welded or pressed onto, a shaft section via this tubular section  170 ,  172 . However, other, detachable connection possibilities are also conceivable, for example using a Hirt serration which can be formed on the transmission part  112 ,  114  instead of the tubular section  170 ,  172 . 
         [0053]    A third exemplary embodiment of the invention is explained below with reference to  FIGS. 3A and 3B  (section II-II from  FIG. 3A ). 
         [0054]    The essential difference from the first embodiment according to the invention lies in the fact that the damping material coatings  234 ,  236  which are applied to the first material coatings  230 ,  232  have insert parts  274 . These insert parts are preferably produced from the same material as the material coatings  230 ,  232  covering the claw formations  218 ,  220 ,  222  or  224 ,  226 ,  228 . Owing to the insert parts  274  of plastic, further stiffening of the damping rubber coatings  234 ,  236  or of the torque transmission device  210  can be achieved. 
         [0055]    In the event of loading, the covered claws  218 ,  220 ,  222  and  224 ,  226 ,  228  are partially compression-loaded. During this compression loading, the insert parts  274  are applied against one another in the rubber coatings  234 ,  236  and owing to the increasing loading the rubber coatings  234 ,  236  are compressed. The insert parts  274  thus move closer to the plastic coatings  230 ,  232 , whereby the rigidity of the damping device D greatly increases at the end of the compression and overall a progressive damping characteristic can be achieved. 
         [0056]    It can further be seen in particular from  FIG. 3B  that the indentations  238  in the plastic coatings  230 ,  232  are not as pronounced as in the first exemplary embodiment. However, the bulging thickenings  240  reach as far as the insert parts  274 . 
         [0057]    A fourth embodiment is described below with reference to  FIGS. 4 and 5 . 
         [0058]      FIG. 4  shows a perspective view of the torque transmission device  310  according to a fourth embodiment of the invention. From  FIG. 4  the two transmission parts  312  and  314  and also a section of an intermediate element  376  arranged between these transmission parts  312 ,  314  can be seen.  FIG. 4  further shows the two tubular sections  372  and  374  on the transmission parts  312 ,  314 , by which the transmission parts  312 ,  314  can be attached to shaft sections (not shown). 
         [0059]      FIG. 5  shows a perspective view of the intermediate element  376  with the claw formations  318 ,  320  and  324 ,  326  and  328  protruding from a disc-shaped base element  376   a.    
         [0060]    In addition, it is shown by way of indication in  FIG. 5  that the claw formations  318 ,  320  and  324 ,  326 ,  328  are each covered with a rubber coating  354  and  356 . In the base element  376   a  there can be seen between the claws  324  and  328  a through-bore  378  which is provided, for example, in order, on assembly of the torque transmission device  310  or on insertion of the intermediate part  376  into one of the transmission parts  312 ,  314 , to allow air enclosed between the transmission parts  312 ,  314  and the intermediate element  376  to escape and thus bring the intermediate element  376  into contact with the associated transmission part  312 ,  314 . 
         [0061]    In  FIGS. 6A and 6B  the torque transmission device  310  is shown in each case in sectional views.  FIG. 6A  shows an axis-containing longitudinal section along the longitudinal axis A, whereas  FIG. 6B  shows an axially orthogonal section through the torque transmission device  310  along the section line VI-VI from  FIG. 6   a.    
         [0062]    From  FIG. 6A  the intermediate element  376  and also the claws  320  and  324  protruding from the base element  376   a  can be seen. The claw  320  is received in the receiving opening  343  of the transmission part  314  and the claw  324  is received in the receiving opening  344  of the transmission part  312 . In other words, the claw formations  318 ,  320  and  324 ,  328  are each received in the receiving areas  330  of the transmission part  312  and in the receiving area  332  of the transmission part  314 . This is evident in particular from comparative viewing of the two  FIGS. 6A and 6B . 
         [0063]    It can further be seen from  FIG. 6A  that the disc-shaped base element  376   a  of the intermediate element  376  is covered with a rubber coating  380  and also serves for guidance of the transmission parts  312  and  314  in their circumferential region. The base element  376   a  further limits a tilting angle of the two transmission parts relative to one another in the operation of the torque transmission device  310 . 
         [0064]    The claws  324 ,  326 ,  328  are each covered with a rubber coating  354 , having indentations  358  at the end thereof leading up to the centre axis M ( FIG. 6B ). Provided on the rubber coating  354  in the region of the indentations  358  are bulging thickenings  360  which fill the indentations  558  and project in the direction of the side walls of the receiving opening  344 ,  346  and  348 . 
         [0065]    Besides the above-described intermediate element  376 , there is a further difference from the above embodiments according to  FIGS. 1 to 3  in that elastomer bodies  380 ,  382  are provided both in the claws  318 ,  320  and  324 ,  326 ,  328  and in the transmission parts. Owing to the elastomer bodies  380 ,  382 , the behaviour of the torque transmission device  310  can be better adjusted to specific frequencies of vibrations and oscillations which arise in a drive train of a motor vehicle. 
         [0066]    The functioning of the torque transmission device  310  according to the fourth embodiment corresponds more or less to the functioning of the embodiments described with reference to  FIGS. 1 to 3 , with the difference that the torque to be transmitted is not transmitted directly via the transmission parts  312  and  314 , but via an interposed intermediate element  376 . A torque is introduced into the torque transmission device  310 , for example, via the transmission part  312 , whereupon the transmission part  312  is displaced with compression of the damping coating  354  in the direction of the intermediate element  376  relatively about axis M, i.e. the torque is transmitted with compression of the damping coating  354  by interaction of the claws  324 ,  326 ,  328  with the receiving openings  344 ,  346 ,  348  to the intermediate element  376 . The intermediate element  376  is displaced relatively with its claw formation  318  and  320  in the direction of the receiving openings  343  of the transmission part  314 , whereby the torque is transmitted to the transmission part  314 . The transmission part  314  thus driven now in turn drives the shaft section (not shown) connected to it in a rotationally fixed manner.
The present invention relates to a device for the vibration-reducing transmission of torques between two shaft sections in a shaft arrangement comprising two transmission parts that interact in a torque-transmitting manner in a coupling area, wherein each of the transmission parts has a protruding claw formation, which is received in a receiving area for the transmission of torque from the respectively other transmission part, wherein a damping device is provided between the transmission parts, wherein each of the transmission parts also has a closed bearing ring with a bearing opening, which receives and supports an axial positioning pin, and wherein the bearing ring is integrally connected to the associated claw formation of the respective transmission part and extends axially into the receiving area.