Abstract:
A coupling ( 30, 49, 61; 40, 60 ) with a coupling ring ( 1 ) on two coupling parts ( 8, 9 ), wherein the coupling parts ( 8, 9 ) each constitutes a star ( 2, 3 ) with star arms ( 26, 27 ) and star arm end regions ( 4, 5 ) situated thereon, wherein the two stars ( 2, 3 ) are arranged opposite and axialy relative to one another with an angular offset, and the star arm end regions ( 4, 5 ) are provided with in each case at least one threaded bore ( 14 ) for screw connections ( 20 ), wherein the coupling ring ( 1 ) includes plurality of fastening elements ( 10, 11 ).

Description:
BACKGROUND OF THE INVENTION 
     (1) Field of the Invention 
     The invention relates to a coupling with a coupling ring on two coupling parts and also to an associated coupling ring. 
     A description of the specifications concerning the flexible joint coupling with a coupling mounted between two coupling parts, which, in turn, consists of an integrated coupling ring made up of separately vulcanized rubber-wedge metal parts to provide for fastening along the ring and are intermeshed with the coupling parts, is provided in the publication DE 196 39 304 A1. The metal parts of the coupling ring are solely composed of wedges which are evenly arranged along the radial direction of the dimensions and cover the entire shaft-width. Vulcanized rubber blocks, which are already mounted in line with the direction of the dimension, are integrated between the wedges against a pre-tensioned pressure bar. The coupling ring may be composed either of individual segments including at least one rubber block and both-sided vulcanized metal parts to be respectively connected in the form of wedges. 
     The screw connections between the coupling parts and the coupling ring positioned in between it are axially aligned in order to fit with the design of the coupling axis. 
     The fastening of the coupling ring and mounting as well as the dismounting of the coupling parts may involve some difficulties and additional efforts due to the inevitable requirement of an appropriate mounting device and—site in order to carry out implementation of the axial screw connections. 
     (2) Description of Related Art Including Information Disclosed Under 37 CFR 1.97 and 1.98 
     In addition to the above-mentioned, the publication DE 20 2004 003 933 U1 includes a description of the flexible ring coupling with its integrated coupling drive element, which primarily consists of a shaft-shaped coupling part made of flexible material, i.e. rubber in particular, whereas the connection of the shaft-shaped coupling part and its metallic element are vulcanized with bore holes to provide for a reach-through for each one of the coupling parts. However, the shaft-shaped coupling element is split within, at least, one of the metal parts with the gap being formed in doing so ensuring for the secure operation of the coupling with respect to the stability and fastening. 
     This means, that, at least, one fixing device needs to be mounted in line with the split metal part. 
     The shaft-shaped coupling element has vulcanized spring parts coming as fastening elements for mounting with both the radially and axially directed bore holes. The shaft-shaped coupling with its radially aligned bore holes is only fastened to that single coupling part which is radially aligned to the screwing connections. The bore holes are connected with axially aligned screw connections and, in so doing allow for the connection of the shaft-shaped coupling part with the other coupling element. With the radial borehole shape on the one hand, and the axial borehole shape of the shaft-shaped coupling part on the other hand, it is possible to provide for a radial-axial connection between the coupling parts, which are fastened to the coupling part. In cases, where the connection is supposed to be optionally mounted on the basis of a radial shape, the shaft-shaped coupling part needs to be splitted into at least two segments, which are to be assembled into the shaft-shaped coupling part during the mounting process. 
     The fastening of the coupling ring and mounting as well as the dismounting of the coupling parts may involve some difficulties and additional efforts due to the inevitable requirement of an appropriate mounting device and an assembly stand in order to carry out implementation of the axial screwing operation. 
     Please refer to the document GB 377 454 A for a description of a flexible ring coupling with two coupling parts and consisting of flexurally rigid arms providing for a range that allows for the positioning of parent parts which are in-vulcanized on both sides, whereas said parts are crimped between the arms by means of adjustable, radially screw-mountable metal plates, which are fastened to the external side edges of the flexible material wedges. 
     In doing so, the flexible material wedges are mounted between the opposing coupling parts, which would, thus be positioned between the arms with the flexible material wedges are segments with parent parts which are vulcanized on both sides and inserted into the radially guided recesses of the arms. 
     During the mounting process, the opposing parent parts of two adjacently positioned material wedges are supported by the respective coupling part&#39;s arm, whereas the parent parts are radially fastened to and supported by the arm, which is, in turn, made up of a metal plate provided with two holes. The adjustment of the static pressure is made by means of radial screw joints which are mounted vertically to the peripheral end ranges of the arms, as these are, when viewed from their end ranges, provided with two radially aligned threaded holes. 
     The wedge-shaped metal fastening elements usually consist of three parts and become one by the assembly of the both parent parts of the respective adjacent flexible material wedges and the metal plate, which is provided with two holes to allow for the radial screwing with the two radial threaded holes of the arms, so that the parent parts of the flexible material wedges are pressed in a radial way into the recesses (notches), of the respective coupling part&#39;s arms. 
     The flexible material wedges are connected with the parent parts on both sides and are designed in a cuneiform shape in order to fit with the ring axis. The elastic material wedges and their corresponding material wedges are segments, i.e. the material wedges bonded with their parent parts are segments, which are inserted between the notches of the staggered arms of the coupling parts and remain in that position after the completion of the mounting. However, this alone is not sufficient to meet the requirements of a consistent, unsplitted shaft. This is, because the segments are, in a first assembly step, inserted between the arms and, whilst being supported by the parent parts and, in the second step, conveyed in a bridge-like way to one of the coupling rings by means of the screw connection. That way, the bridge-like joining provides for a coupling ring without the need of a separate coupling ring in place. 
     A description of a wedge-integrated coupling with a standard shaft-shaped coupling element can be found in the document DE 20 2009 015 790 U1, whereas the shaft-shaped coupling element consists of many different rubbery-elastic segments. The segments have integrated fastening elements with mounting holes to be aligned with a driven machine assembly part as well as in-vulcanized parts that provide for a reduction of the elasticity. 
     Said segments are adjoined to each other by means of hinged-like connection parts and, in so doing, form a single-parted, radially extendable, shaft-shaped coupling element, which in turn, consists of segment-aligned radial and axial screw joints as well as of a hinge, which is mounted between two segment halves. 
     As is described in the specifications, the self-contained coupling element consists of at least two ring parts/ring segments and an integrated hinge joint, i.e. it is not subjected to the vulcanization process in full and, hence, not formed as a coherent, self-contained coupling ring. Hence, the design of the coupling ring is not intended to serve as a coherent, thus a whole and non-segmented coupling ring solely comprising of radial screw joints. The assembly requires an appropriate mounting device. 
     The document DE 295 22 268 U1 includes a description of a transverse drive integrated into a motor, whose rotor shaft runs in parallel to the drive axis of a rail vehicle which is connected with an axle drive. The axle drive consists of a bevel quill ring enclosed by a wedge-shaped ring, which is, partly, guided through the bevel quill ring. The rotor shaft with its power take-off end is coupled with the wedge-shaped ring by means of a motor-drive coupling, whereas the motor power take-off end is designed as both an angularly elastic and axial coupling. 
     The wedge-shaped ring is coupled with the bevel quill ring by means of a gear drive coupling. The wedge-shaped ring is provided with an axial end-fastening using spiral springs, which make for the wedge-shaped ring&#39;s rebound to its mid-position to the bevel quill ring in the event of a misalignment. 
     The coupling itself does, hence, not comprise of a whole, non-segmented coupling ring. A self-contained, integral coupling ring without any screw joints that may be fastened to the coupling parts is not provided. 
     The document DE 196 39 304 A 1 contains a description of a flexible resp. elastic joint coupling with a spacer shaft which is aligned between two coupling flanges, whereas the spacer shaft consists of separately vulcanized rubber-wedge metal parts to provide for an fastening along the coupling and are intermeshed with the coupling flanges. 
     The metal parts of the spacer shaft consist solely of evenly arranged wedges, covering the entire shaft width in radial direction starting from the peripheral edge. Vulcanized rubber blocks, which are already mounted in line with the direction of the dimension are integrated between the wedges against a pre-tensioned pressure bar. 
     This is the concept serving as the design for a coupling ring consisting of segments whose screw-joint is intermeshed in such a way that it forms coupling ring element, and, by means of the axial screw joint, connect with the intermeshed arrangement of the coupling hubs&#39; arms. The implementation of a self-supporting coupling with an optionally radial screw-joint is not possible. Also in this case, the assembly of the coupling ring element should only take place using appropriate mounting device. 
     Furthermore, the publication 20 2005 015 769 U1 contains a description of a double joint coupling consisting of two joint planes and, thus, two coupling joints which are connected through a shaft, with one of the joint planes is aligned to a gear coupling joint with intermeshing which provides for an angular and axial compensation. The other joint plane is aligned to a torsion-proof, flexile coupling joint. 
     Conventional gear couplings with an integrated intermeshing for the torque transmission are used to connect a driving shaft in order to compensate the axially-parallel, axial, or angular shifts that may occur between the both shafts. 
     Conventional torsion-proof, flexile couplings, such as all-metal couplings are characterized by their capability of compensating possibly occurring misalignments by means of a spring mechanism. This comes along with the advantage that they provide for both a long life fatigue strength and freedom of maintenance. Yet, the elastic-plasticity level is quite low, which, in turn, results in more frequently occurring misalignments, so that the axial shifting clearance is rather restricted. 
     A description of another double joint coupling in the design of a transverse drive with an integrated motor can be found in the publication DE 295 22 268 U1. In this case, the rotor shaft of the motor runs in parallel to the driving axis of a rail vehicle and is connected with an axle drive, which consists of a bevel quill ring that encloses a wedge-shaped ring with parts of it running right within the bevel quill ring. The rotor shaft with its power take-off end is coupled with the wedge-shaped ring. The motor&#39;s power take-off coupling design comes as with both forms of elasticity, i.e. an angular and axial coupling. Using a gear drive coupling and a connection with the bevel quill ring, the wedge-shaped ring has an axial fixture, which is supported by coil springs at its end ranges with the coil springs providing for the wedge-shaped ring&#39;s rebound back into its mid-position, i.e. the bevel quill ring. Difficulties or problems may arise from the direct connection of the wedge-shaped ring with the bevel quill ring, whose intermeshing-mechanism does not allow for any replacement of the coupling joint&#39;s parts in the event of a defect or the like. 
     DETAILED DESCRIPTION OF THE INVENTION 
     The invention is based on the concept to provide for a coupling with an integrated ring to be mounted onto two coupling parts and their corresponding coupling ring with the assembly process of the coupling being simplified by way of the design that is based on a simple, single-parted shaft allowing for the simultaneously implementation of the vulcanization process and, hence, enables the screwing as such part unto the detached end ranges of the front arms. 
     The solution for this task is provided by means of patent claims  1  and  25 . The coupling with its ring on two coupling parts are each fitted with a star unit including star arms in the front, whereas the two star units are arranged in an opposing and axially angular manner, while the star arms in the front are each provided with at least one threaded hole for the screw joints, whereas the following needs to be considered:
         several fastening elements should being radially directed, i.e. towards the axis and arranged around the coupling ring providing at least one solid bores towards the axis whereas the solid bores are supposed to provide for at least one radially aligned screw joint, i.e. towards the fixture of the fastening elements at the threaded bore holes, which are, in turn, radially aligned to the ring axis of the front star arms, which are arranged in an intermeshed manner with respect to the star unit,   at least, one elastic spring element must be provided between the ring-revolving and adjacently arranged fastening elements,   the fastening elements of the coupling rings must provide at least one axial surface which is directed and in line with the front star arms as this is particularly important for the assembly. This is, where the specifications set out in patent claim  1  come into consideration,   as the fastening elements fitted with the coupling ring are part of each of the end ranges belonging to the front star-area of the star unit, which is usually mounted in one of the mid-positions of the gripping arms, whereas the end ranges exhibit a surface aligned towards the fastening elements with a touching connection to the surface at the internal end range of the respective fastening element with the ring-revolving,   alternating arrangement of the fastening elements and the elastic spring parts, which are each fastened to their adjacently arranged fastening elements by means of a simultaneously implemented vulcanization process, form a single coupling ring in the course of a single and simultaneously implemented vulcanization process, and which is, as a whole, screwed onto the two axially shifted star arm units,   the coupling is supposed to provide for an elastic, wholly formed coupling ring and allows for the formation of a consistent, tangential initial tension, whereas the tangential generation of the initial tension is intended to serve the operation of the two angularly aligned, opposing star units of the coupling parts.       

     The fastening elements, which are to be aligned towards the ring axis can be formed in a wedge-shaped manner (which would be the preferable form) and consisting of metal parts. However, the fastening elements can as well consist of other solid materials. Besides, the fastening elements maybe made up of different shapes; this applies also to the spring parts, while the shapes of both parts are always arranged in line with the ring&#39;s circumference. 
     The surfaces of the star arm units may either exhibit an axially aligned surface with an integrated profile which is to be mounted underneath the profiles&#39; surface of the respective fastening element, thus at the narrow wedge-shaped end range before the assembly process takes place with both surfaces contacting each other during the assembly process. 
     The profiles of the fastening elements&#39; surfaces as well as the surfaces belonging to the star arm facing area based on a coherent, positive-locking design. Besides, said profiles may consist either of a notch or spring, while the profiles of the surfaces belonging to the front of the star unit may be either a correspondingly positive-locking spring or a notch. 
     The design profile of the fastening elements may either be composed of a coupling gear system based on wedges or gear with the profiles of the surfaces belonging to the front arm star units providing for an appropriately fitting coupling gear system. 
     The profiles of the fastening elements&#39; surfaces belonging to the front arm units are, thus, available with correspondingly frictional connections. 
     With regard to this, the profiles of the fastening surfaces as well as the profiles of the front arm star units may be designed as a correspondingly matching, thus even, or correspondingly matching, thus bent or topographic shape, which would contact each other during the implementation of the assembly. 
     The fastening elements can be supported by additional means to the front arm star units using pins and fitting bolts. 
     All fastening elements consisting of metallic compounds may exhibit (preferably) external insertions/clearances, which are either composed of a (recess) notch or a counter-bore for the radially aligned screw joints, which are respectively positioned in the external end range of the shaft. 
     The spring parts are composed either of elastic material, in particular rubber or provide a (preferably) evenly designed supporting plate which is aligned to the ring axis. 
     The connection of the bolts with the front arm star unit is either fastened to—depending on the fastening element of the coupling ring—so that one of the star units provides for a connection of the adjacent fastening element&#39;s opposing part with the front arm star unit of one star unit and its opposing star unit, whereas the next one would require another fastening element to be connected to the star unit of another front arm star which, in turns provide for a continuous, thus ring-revolving fastening of the coupling ring on the coupling parts. 
     The coupling with its integrated ring on two coupling parts comes in the form of a double joint coupling with at least one of the coupling parts being fastened to a ring which is connected to a gear coupling with an integrated intermeshing, i.e. gear system, or coming in the form of just one coupling ring of the same kind, which is connected to the shaft of a coupling and compliant to the coupling ring&#39;s specifications of the invention resp. comparable to the gimbal mounting options by means of another coupling which is connected to a shaft. 
     The coupling with its integrated coupling ring on two coupling parts, may as well be used along with a double joint coupling consisting of two joint planes and including two couplings which are connected through a shaft with the joint plane of one spherical gear system, which is aligned to the requirements of an angular and axial compensation clearance. 
     As to that, the spherical gear system is provided with a bushing that comes with an internal gear system, an inter-mountable coupling hub and corresponding external gear system, 
     with the primary shaft being fastened to the inter-mountable coupling hub and the other joint plane of the coupling with its integrated ring being aligned to two coupling parts. 
     The coupling has an integrated coupling ring designed in an unsplitted and non-segmented shape, which is integrated into the fastening- and spring parts, yet, it also serves the purpose of generating a pre-tensioning on two angularly displaced, opposing star units with their front star arm units being axially staggered to the mid-position of the front star arm units that provide for, at least, one threaded bore hole for screw connections. In turn, one of the each coupling ring axes is designed in alignment with the front star arm units and as an axially shaped profile with one of the star units being assigned to a coupling part positioned at the driving end and another star unit being aligned towards the output end with
         said profile being composed of several (preferably) cuneiform fastening elements made of metal, which are arranged around the ring, thus aligned towards the axis of the coupling ring and included in a continuous bore, of which at least one of them is directly aligned in radial direction to the ring axis to provide for the fixture of the fastening elements to the radially aligned threaded bore holes of the front star arm unit&#39;s double-end star units along the fastening elements of the coupling ring,   whose profile is aligned in axial direction towards the ring axis, which is arranged in line with the profile of the front star arm units when locked into position during the assembly process,   the ring-revolving adjacently positioned fastening elements which are each provided with an elastic spring element bonded to said parts during the vulcanization process,   so that a ring-revolving two-sided arrangement of the metallic cuneiform fastening elements and the elastic spring elements provides for the formation of a wedged-shape coupling ring, which can be screwed, as a whole, onto the both axially shifted star front-faced arms of the two-sided star units.       

     The coupling ring can either be a combination of fastening elements and in-vulcanized spring parts, whereas both the fastening elements and the spring parts may exhibit variances with respect to the shape, i.e. with (preferably) wedge-shaped fastening elements aligned to the ring axis, the spring parts are usually designed in a cuboid shape. 
     The elastic coupling with its integrated coupling ring is usually designed in a gimbal shape. 
     Two elastic couplings may be designed in the form of a double-gimbal coupling connected through a corresponding shaft. 
     The intermeshed gear coupling may be replaced by means of a membrane coupling or a ring disk coupling. 
     The arrangement of the two couplings in their joint planes can be mounted as well into the internal as into the external area of the wheelset in rail vehicles. The fields of application with respect to the couplings are not limited to rail vehicles. 
     According to the invention, the coupling ring for the above-mentioned couplings is, in accordance with patent claim  25  hereof, 
     must with respect to the fastening parts, consist of a whole, thus non-segmented coupling ring, whereas 
     
         
         
           
             several, ring-revolving fastening elements, which are axially aligned towards the coupling ring fastening elements with, at least one of them, exhibiting a continuous bore with a straight radial alignment towards the direction of the ring axis. In this case the continuous bore holes must be provided for at least one straight radial alignment going out from the external ring surface and allowing for a screwing connection to fix the fastening elements onto two fitted coupling parts of one coupling, 
             the fastening elements of the coupling ring fixed in the internal ring surface must be provided each with an axial profile running along the direction of the ring axis, 
             one elastic spring element must be provided between each of the ring-revolving, adjacently arranged fastening parts, and is, in turn, fixed to them by means and in the course of a vulcanization process. The latter process must take place in parallel with the fixing procedure, 
             in order to provide for both a connection and the formation of a coupling ring taking place in the course of the ring-revolving, dual arrangement of the fastening elements and the elastic spring parts during the vulcanization process, which is finished in parallel to the above-mentioned process, and is then, as a whole part, ready to be screwed onto the two coupling parts which are fixed on top of the coupling ring. 
           
         
       
    
     The fastening elements can either exhibit a (preferably) wedge-shaped and metal-sealed joints, which, in turn, provides for a coupling ring supported by an arrangement of wedges. 
     Due to the finishing surface of the wedge arrangement around the external ring section, which is fixed with the fastening parts, the screw heads of the corresponding joints may protrude beyond the external ring surface. 
     This can be prevented by providing the fastening elements used for the fixture to the wide wedge-shaped end range with (preferably) external insertions/clearances, which can be done either by means of a countersink notch or a counter bore. These must, however, be suitable for the radially arranged screw-joints so as to ensure for an appropriate countersink. 
     In addition to the wedge-shaped formations, the fastening elements may also be made up of other shapes and forms. The same applies to the elastic spring elements, whose fastening elements may also exhibit various shapes and forms which are in line with their respective shape. 
     The elastic spring elements consist of elastic material, (preferably) rubber. 
     The elastic spring elements exhibit at least one supporting plate, which must be aligned along the direction of the ring axis. The radially aligned supporting plates can each be arranged in the center of the spring element. The supporting plates can either be designed in the shape of parallel surfaces or in the shape of a wedge which is aligned towards the ring axis. Apart from this, the spring elements can exhibit a ring axis with at least, one radially and/or axially concave center mounted in alignment with it. If the latter case applies, one of the supporting plates must be provided with dual a concave center at both the external and internal area of the ring axis belonging to the respective part of the spring element. Moreover, its movement behavior may be oriented towards the radial direction of the ring axis, whereas the spring element must be arranged in line, thus, at the sides of the radially aligned concave center parts. 
     Deviations, improvements, and specific designs of the inventions will be outlined in additional independent claims. 
    
    
     
       BRIEF DESCRIPTION OF THE SEVERAL VIEWS OF THE DRAWINGS 
       The invention is explained and described in detail by means of design examples by means of several drawings: 
         FIG. 1  a depiction of the design in accordance with the invention showing the axial screw joints, thus the coupling along with its coupling ring and solely radially aligned screw joints along the both star&#39;s front facing areas belonging to the coupling parts of the coupling, 
         FIG. 2  a perspective view on the coupling ring in accordance with the invention of the coupling ring&#39;s design, 
         FIG. 3  a depiction of the coupling ring aligned towards the direction of the axis without coupling parts based on the description as set out in  FIG. 2 , 
         FIG. 4   a  a depiction of the cross-sectional view of A-A based on  FIG. 1 , with the star&#39;s front facing arm areas screwed with the coupling ring of said star, 
         FIG. 4 b    a depiction of the cross-sectional view of B-B based on  FIG. 1  with the star&#39;s front facing arm areas screwed with the coupling ring of said star, 
         FIG. 5  a schematic depiction of an fastening element which is, on the basis of spring elements, flanged by a wedge-shaped fastening element provided with a spring in the internal area of the shaft with the design serving the purpose of adjusting the coupling ring to a notch onto one of the star&#39;s front facing arm areas of the external star, 
         FIG. 5 a    a schematic view of a fastening element with a planar surface of the fastening, element adjacent to a planar surface of the star front facing rea, 
         FIG. 6  a schematic depiction of a fastening element, which is on the basis of spring parts, flanged by a wedge-shaped fastening element provided with a notch in the internal area of the shaft, i.e. at its narrow, wedge-shaped end with the design serving the purpose of adjusting the coupling ring onto one of the star&#39;s front facing arm areas of the external star using a spring, 
         FIG. 6 a    a schematic view of a fastening element with a planar surface having dog teeth of the fastening element, 
         FIG. 7  a schematic depiction of a wedge-shaped fastening element exhibiting a narrow, wedge-shaped and even surface to provide for a force-fit contact of the coupling ring to an even, external star front facing area of the external star area, 
         FIG. 7 a    a schematic view of a fastening element with radially aligned screw-joint/ screwing operation, 
         FIG. 8  a schematic depiction of a fastening element exhibiting a narrow, wedge-shaped and bent finish surface to provide for a force-fit contact of the coupling ring to a bent, external star front facing area of the external star. 
         FIG. 9  a perspective depiction of the elastic, unsplitted coupling ring with wedges arranged along it in connection with an unsleeved open gear coupling, 
         FIG. 10  a perspective depiction of a simple gimbal shaft bogie-coupling arranged along it, 
         FIG. 11  a schematic sectioning of an (in accordance with the invention) double-joint coupling—gear coupling/bogie-coupling arranged along it—in idle state, 
         FIG. 12  a schematic sectioning through the double-joint coupling in deflected position based on the description of  FIG. 11 , 
         FIG. 13  a schematic depiction of a gimbal double-joint coupling in accordance with the descriptions of  FIG. 9  and  FIG. 10  designed for rail vehicles with each of them exhibiting one bevel quill ring whose starting point is at the gear coupling and exhibits one bevel, which is, in turn, connected to driving end&#39;s gear and 
         FIG. 14  comes with a double-gimbaled bogie-coupling arranged along it, 
         FIG. 15 a    schematic view of a coupling ring according to the present invention of the coupling ring construction,  FIG. 16 a    schematic side elevational view of a coupling ring. 
     
    
    
     The following section provides an overview of the functionalities described in  FIG. 1 ,  FIG. 2 , and  FIG. 3 . 
       FIG. 15  shows another perspective view of a coupling ring. 
       FIG. 16  shows a side elevational view of a coupling ring. 
     The following section provides an overview of the functionalities described in  FIG. 1 ,  FIG. 2 , and  FIG. 3 . 
     The coupling  30  depicted in  FIG. 1  with the coupling ring  1  mounted on two coupling parts  8 ,  9 —thus exhibiting one coupling component  8  at the driving end&#39;s gear and another one at the output&#39;s gear  9 —, the coupling parts  8  and  9  are each provided with a star  2 ,  3  including star arms  26 ,  27  which are both provided with star front arm facing areas  4 ,  5 , whereas the two stars  2 ,  3  are arranged opposed and axially, resp. angularly shifted to each other in coupling  30 , and with the star front arm facing areas  4 ,  5  which are shifted to the star&#39;s center  28  each exhibiting at least one threaded borehole  14  for the screw-joints  20  provided for coupling ring  1 , whereas
         coupling ring  1  comes (according to  FIG. 2  and  FIG. 3 ) with wedge-shaped, metal fastening elements  10 ,  11 , which are aligned towards axis  23  of coupling ring  1  in a ring-revolving arrangement with each of them providing at least one directly radially aligned continuous bore  12 , 13  towards ring axis  23 . The continuous bores  12 ,  13  provide for at least one of the directly radial aligned screw-joints  20  for the fastening of the fastening elements  10 ,  11  to the threaded boreholes  14 , which are radially aligned to ring axis  23  belonging to the dual star arm facing areas  4 ,  5  as is shown in  FIG. 1 ,   each of the wedge-shaped fastening elements  10 ,  11  must (according to  FIGS. 4 a  and 4 b   ) exhibit one surface  31 , which is axially aligned towards the ring axis  23 , and which, in turn, must be positioned in line with one of the axially directed surfaces  29  of the star&#39;s front facing arm areas  4 ,  5  during the implementation of the assembly process,   each one of the elastic spring elements  17  must be positioned between the ring-revolving adjacently aligned fastening elements  10 ,  11  (according to  FIG. 1 ), which is, by means of a vulcanization process,   it must be considered, that the ring-revolving rotational arrangement of the wedge-shaped fastening elements  10 ,  11  and the elastic spring parts  17  form a bogie-coupling whilst the implementation of a vulcanization process. Said coupling ring must be mountable as a whole onto the both axially shifted star&#39;s front facing areas  4 ,  5  at both ends,   it must be made sure, that the coupling ring  1  constitutes (in accordance with  FIG. 2  and  FIG. 3 ) an elastically whole bogie-coupling, whilst allowing for a consistently tangential pretension, as is shown in  FIG. 1 , whereas said pretension is supposed to operate the two stars  2 ,  3  which are arranged opposed and axially shifted to each other towards the two coupling parts  8 ,  9 .       

     The coupling ring  1  depicted without its components  8 ,  9  in  FIG. 2  and  FIG. 3  is designed as a consistent, whole, and non-segmented coupling ring to be mounted inside of the fastening elements  10 ,  11  and inside of the spring parts, whereas:
         coupling ring  1  comes with several wedge-shaped, metal fastening elements  10 ,  11 , which are aligned towards the radially aligned, continuous bore  12 ,  13  are part of the ring axis  23 . Said continuous bores  12 ,  13  are intended for the sole purpose of providing for a fixing of the fastening elements  10 ,  11  by means of a direct radially aligned screw-joint to be implemented in the external ring section  37  onto the (as is shown in  FIG. 1 ) fitted coupling parts  8 ,  9  of the coupling  30  so as to provide for a connection of the two coupling parts  8 ,  9  via coupling ring ( 1 ) whereas   each of the wedge-shaped fastening elements  10 ,  11  of the coupling ring  1  in the internal ring section  36  must exhibit a profile  31  which is axially aligned towards the ring axis  23 ,   each of the ring-revolving, adjacently arranged fastening elements  10 ,  11  must exhibit one elastic spring element  17 , which is being fixed to the adjacent fastening elements  10 ,  11  during the implementation of a vulcanization process,   with the ring-revolving, alternating arrangement of the metallic, wedge-shaped fastening elements  10 ,  11  and the elastic spring components  17 , which are each fastened to their adjacently arranged fastening elements by means of a simultaneously implemented vulcanization process, forming a single coupling ring  1 , and is, in turn, connected with the two coupling parts  8 ,  9 .       

       FIG. 4 a    depicts a sectioning A-A (which is based on  FIG. 1 ) of coupling ring  1 , which is partly screwed together with the coupling ring  1  of the star&#39;s front facing areas  5  belonging to the star  3 . Another depiction, as is shown in  FIG. 4 b    shows a sectioning B-B (which is based on  FIG. 1  of the same star&#39;s front facing area  4  of star  2  and the star&#39;s front facing area  5  of the other star  3  being screwed together with the coupling ring  1 , whereas both sections A-A (lengthwise aligned section) and B-B (angularly aligned section) show the angular shift between star  2  of the coupling part  8  and the other star  3  of the coupling part  9  as is described in  FIG. 4 b    in contrast to the coupling part  8 , which is connected to a shaft drive  21 , the coupling part  9  exhibits a fastening based on an adjustment screw  34  and a front-end gear shaft  35 , which is fixed to the shaft drive (not included in the drawing). 
     The star front facing areas  4 ,  5  each belonging to a star  2 ,  3  and correspondingly fitted to the fastening elements  10 ,  11  of the coupling ring  1  depict (according to  FIG. 5  and  FIG. 6 ) the star arms  26 ,  27  (as is shown in  FIG. 1 ), with their starting point at the end ranges of the star&#39;s  2 ,  3  mid-position  28 . Said end ranges exhibit a surface  29 , which is aligned towards the fastening elements  10 ,  11 , which enables a connection to surface  31  at the wedge-shaped, narrow end range  32  of the wedge-shaped fastening element  10 ,  11 . 
     The star&#39;s front facing areas  4 ,  5  of the stars  2 ,  3  may each exhibit an axially aligned surface  29  including a profile, which must be, prior to the screwing  20 , positioned underneath the surface  31  with its profile, i.e. at the wedge-shaped, narrow end range  32  of the respectively assigned fastening element  10 ,  11 , which, in turn, leads to a contact between the two surfaces  29 ,  31  during the implementation of the assembly. 
     The profiles of the surfaces  31  belonging to the fastening elements  10 ,  11  as well as the profiles of the surfaces  29  belonging to the star&#39;s front facing arms  4 ,  5  may exhibit a form-fit design at both ends. 
     The profiles of the surfaces  31  belonging to the fastening elements  10 ,  11  may be either provided with a notch  16 , as is shown in  FIG. 6 , or as is shown in  FIG. 5  with a spring  15 , while the profiles of the surfaces  29  belonging to the star&#39;s front facing arms  4 ,  5  may exhibit an accordingly form-fitted spring  6  (see  FIG. 6 ) or a notch (see  FIG. 5 ). 
     (compare  FIGS. 5 a , 6 a   , and  FIG. 7 a   ) 
     The profiles of the surfaces  31  belonging to the fastening elements  10 ,  11  may be composed of a coupling gear system (not included in the drawing), which exhibits a wedge- or gear-shaped design with the profiles of the surfaces  29  belonging to the star&#39;s front facing arm units  4 ,  5  may be provided with an accordingly fitting coupling gear system. 
     The profiles of the surfaces  31  belonging to the fastening elements  10 ,  11 , as well as the profiles of the surfaces  29  belonging to the star&#39;s front facing arm units  4 ,  5  may exhibit a form-fit shape at both ends. 
     The profiles of the surfaces  31  belonging to the fastening elements  10 ,  11  as well as the profiles of the surfaces  29  belonging to the star&#39;s front facing arm units  4 ,  5  may (according to  FIG. 7 ), be designed as correspondingly aligned, even surfaces or (according to  FIG. 8 ) designed as correspondingly aligned, bent surfaces, which, in both cases contact each other during the implementation of the assembly. 
     Regarding the bent surfaces, it must be considered that the surfaces  31 ,  29  aligned towards the internal ring section  36  or the external ring section  37  may exhibit a bent shape. 
     The screw-joints  20  will generally lead to a force fit between the coupling ring  1  and the coupling parts  8 ,  9 , which is usually supported by the form locking connections (spring, notch). As a rule of thumb, the connection area between the coupling ring  1  and the two coupling parts  8 ,  9  assigned to the coupling  30  exhibits a mixed form. 
     All fastening elements  10 ,  11  made of metal compounds may (according to  FIG. 5  and  FIG. 6 , as well as according to  FIG. 7  and  FIG. 8 ) exhibit (preferably) external insertions/clearances  19  at the wedge-shaped, wide end range  33 , which can either be designed in the form of a countersink notch or a counter bore for the radially aligned screw-joints  20 . 
     The spring parts  17  may consist entirely of rubber. The spring parts  17  may, as shown in  FIG. 1 , however also be provided with at least one even supporting plate  18  aligned towards the ring axis  23 . 
     The radially aligned supporting plates  18  may be arranged in a manner that is oriented to the center of the spring element. 
     As is shown by means of a spring element  17  in  FIG. 7 , it is not of necessity that the supporting plates  18  are provided exclusively with parallel consistent, thus even surfaces, but also with surfaces exhibiting a wedged shape  55  (dotted) towards the ring axis  23 . Apart from that, the spring elements  17  with their radial and/or axial alignment towards the ring axis  23  must exhibit at least one concave center, whereas the respective part  56 ,  57  of the spring element belonging to both sides of the supporting plate  18  (as shown in  FIG. 7 ) must be provided with both an axially aligned concave center  39  (dotted) in the internal ring section and a concave center  54  in the external ring section. Concave centers fastened to the sides of the shafts (not included in the drawings) may be radially aligned towards the ring axis  23 . 
     The screw-joints  20  may be, by turns and with the starting point positioned at the primary fastening element  10  belonging to the coupling ring  1 , connected with the star&#39;s front facing arm unit  4  of the primary star  2 , whilst, on the other hand, the screw-joint must be connectable with the fastening element  11  positioned next to the fastening element  11  and the star&#39;s front facing area  4  which is adjacent to the star  2  and the star  3  of the star&#39;s front facing area  5 . This allows, in turn, for the mounting of another fastening element  10  in order to connect another star&#39;s front facing unit  4  with the star  2 , etc. so that, after all, the coupling ring  1  is radially mounted onto the intermeshing coupling parts  8 ,  9  belonging to the internal ring section  36 . 
     The couplings  40  and  30  depicted in  FIG. 9  and  FIG. 10  with their coupling ring  1  mounted onto two coupling parts  8 ,  9  may be part of a double-joint coupling  40 , whereas one of the coupling parts  8  depicted in  FIG. 9  is connected with a spherically geared coupling  22  through the shaft  21 . 
     For explanation purposes,  FIG. 10  depicts a single-gimbal bogie-coupling arranged along it  30  together with the inventive coupling ring  1 , and including the connection of the coupling ring  1  via the coupling component  8  through to the shaft  21 . 
       FIG. 11  shows the gimbal double-joint coupling  40  with two joint planes  41 ,  42  depicted in a non-deflected idle position, while  FIG. 12  shows the gimbal double-joint coupling in a deflected, thus dynamic condition. However, the gimbal double-joint coupling  40  consists of two couplings  22 ,  49 , which are connected through a shaft  21  with one of the joint planes  41  being assigned to a gear coupling  22  which is based on a spherical gear system  45  that provides for both angular and axial compensation. The other joint plane  42  is assigned to the torsion-proof, bending-elastic coupling  49  with its coupling ring  1 . Compared to the coupling  30 , the coupling  49  is provided with a shaft  38 , which is connected with the coupling part  9 . 
     The gear coupling  22 , which is based on a spherical gear shaft system  45  exhibits a replaceable sleeve  46  along with an internal gear shaft system and a replaceable coupling notch  47  including an external gear shaft system, whereas the shaft  21  exhibits an end range-sided connection to the optionally replaceable coupling notch  47  with the torsion-proof, bending-elastic coupling  49  constituting a bogie-coupling arranged along it, and thus, in accordance with the invention, serves the purposes of an elastic, whole wedge-included coupling ring  1 . 
     The gear coupling  22  with its spherical gear shaft system  45  as is shown in  FIG. 11 ,  FIG. 12 , and  FIG. 13  is enclosed by the sleeve  46 , which is provided with a lid  51  that allows for a lubrication covering the full surface, with the lubricant or grease mainly filling the gap  50  between the gear shaft system&#39;s notch  47  and the lid  51  or the sleeve  46 . According to requirements, the sleeve  46  can be a closed sleeve. 
     The double-joint coupling  40  depicted in  FIG. 11  and  FIG. 12  comes with the standard coupling ring  1  as in accordance with the invention being composed of an unsplitted and non-segmented coupling ring with its wedges arranged along it exhibits a consistent, thus coherent shape and is mounted in the inside of the fastening elements  10 ,  11  as well as in the inside of the elastic spring parts  17 . Its purpose is to serve as a basis for screw-joints, which, in turn, leads to the generation of a pretension on two opposing, angularly shifted stars  2 ,  3  with axially shifted star front-facing areas each exhibiting at least one threaded borehole  14  for above-mentioned screw-joints. Each of the star front-facing areas  4 ,  5  exhibits a profile  6 ,  7 , which is axially aligned to the axis  23  of the coupling  1 , whereas the stars  2 ,  3  come with a respectively assigned coupling part  8  at the driving end and a coupling part  9  at the output end, whereas the coupling ring  1 
         is provided with several wedge-shaped, metallic fastening elements  10 ,  11  which are aligned towards the axis  23  and a continuous bore  12 ,  13  which is radially aligned to the ring axis  23 . The continuous boreholes  12 ,  13  are intended for at least one direct radially aligned screw-joint  20  in order to enable for the fastening to the threaded boreholes  14  of the alternatingly arranged star&#39;s front facing are as  4 ,  5 , which are, in turn, aligned in radial direction towards the ring axis  23 ,
           the wedge-shaped fastening elements  10 ,  11  exhibit profile  15 ,  16  running axially along the ring axis  23 , and which must be each adjusted in correspondence with the profile  6 , 7  of the star front facing areas  4 ,  5  during the implementation of the assembly,   each one of the elastic spring elements  17  must be provided between the ring-revolving adjacent fastening elements  10 ,  11  with the respective spring element providing to be bonded to the fastening elements by means of vulcanization, i.e. in the course of this process,   as a result of a vulcanization process, the ring-revolving, alternating arrangement of the metallic fastening elements  10 ,  11  and the elastic spring parts  17  should provide for the formation of a bogie-coupling, in order to be mountable as a whole onto the star-intermeshing, axially shifted star&#39;s front facing areas  4 ,  5 .   
               

     Provided that the fastening elements  10 ,  11  of the coupling ring  1  exhibit a wedge-shaped alignment towards the ring axis  23 , the coupling ring  1  is referred to as a bogie-coupling. 
     Yet, the coupling ring  1  may also exhibit a ring-revolving combination consisting of fastening elements  10 ,  11  and in-vulcanized spring elements  17  which are arranged in an alternate pattern with the fastening elements  10 ,  11  and the spring elements  17  being provided with different, yet, correspondingly aligned shapes. 
     Both the elastic bogie-coupling arranged along it  30  and the bogie-coupling  1  shown in  FIG. 10  depict a single-gimbal bogie-coupling arranged along it. 
     Two elastic couplings with wedges arranged along them  30 ,  61  may (in accordance with  FIG. 14  have the shape of a shaft connection  21  based double-gimbal bogie-coupling arranged along it. 
     Apart from that, the gear coupling  22  with its spherical gear shaft system  45  may be substituted by means of a membrane coupling or ring disk coupling. 
     The arrangement of the two couplings  22 ,  30  mounted in their joint planes  41 ,  42  as is shown in  FIG. 13 , can be mounted as well into the internal as into the external area of the wheelset in rail vehicles. 
     In conclusion, it can be said that the coupling with its coupling ring  1 , as is shown in  FIG. 11, 12, 13 , is at least partly connected with a double-joint coupling  40 , yet, as is shown in  FIG. 11, 12, 13 , a connection must exist at least between one of the coupling parts  8  or  9  and a shaft connection  21  based gear coupling system  22  with its spherical gear shaft system  45  or the connection is formed by a double-joint coupling  60 , as is shown in  FIG. 14 , i.e. through a shaft  21 , that provides for the connection with the coupling  30 ,  61  via a coupling ring which corresponds with the type of assembly of the coupling ring  1  or via another coupling with optional gimbal misalignment and whose connection is formed through a shaft  21 . 
     When it comes to the use of the elastic-unsplitted coupling ring  1  for applications in the field of double-joint couplings  40 , the coupling ring  1  can be connected with a coupling component  8 , as is shown in  FIG. 9 . In this case, the coupling component  8  of the coupling  30  must provide a connection with the shaft connection  21  based gear coupling system  22  that comes along with a spherical gear shaft system. 
     The advantages of the inventive, elastic-unsplitted coupling ring  1  with its consistently tangential pretension in two coupling parts  8 ,  9  within one coupling  30  are shown in the simultaneously conducted vulcanization process, which includes the fastening of all spring parts  17  to the adjacently positioned fastening elements  10 ,  11 , and the consistent compensation resulting from said process, as well as in the non-necessity of an assembly device required for the consistent pretension on the stars  2 ,  3  belonging to the coupling parts  8 ,  9 . 
     The following section provides an overview of the functionalities with respect to the double-joint coupling  40  as is shown in  FIG. 12 : 
       FIG. 12  depicts the gimbal double-joint coupling  40  in a dynamic condition including an axial misalignment  24  and an angular shift  25 . In case of the axial misalignment  24  belonging to the gear coupling system  22 , the latter one is shifted towards the coupling with the wedges arranged along it  49 , with the coupling notch  47  being placed into the clearance  50  in the area of the lid  51  or the sleeve  46 . 
     At the simultaneously occurring angular shift  25 , the shaft  21  tilts out of the clutch coupling axis  48  with the coupling ring with the wedges arranged along it  1  serving as a suspension for the angular shift  25 . 
     The inventive double-joint coupling  40  allows for the effective and efficient use of the advantages—long life fatigue strength and freedom from maintenance. Other advantages include the low space requirements along with a high level of angular and axial compensation and the possibility for lubrication of controllable parts within the wheelset in the two different couplings  22 ,  49 . 
     For instance, it is possible to install the bogie-coupling arranged along it  49  in an externally mounted single-wheel drive, such as is the case with tram systems, i.e. right between the wheel and the transmission gear (as these generally have a narrow space), but also directly above the road (where the surroundings are rather aggressive). Owing to the low maintenance requirements and considering such surroundings, the described arrangement of the coupling  49  turns out to very useful. The inventive double-joint coupling  40  provides the opportunity to align the drives of rail vehicles in a much more diversified and flexible way towards the environmental and technical conditions. 
     On the other hand, the gear coupling  22  with its spherical gear shaft system  45  can be positioned in the protected area of the transmission gear, as this area provides for sufficient space for adjustments and shifts. The gear coupling  22  with its spherical gear shaft system  45  allows for coverage through the lid  51  or the sleeve  46 , which is immovable and, thus, ensures coverage of the external surface. 
     The double-joint coupling  40  allows for a simple replacement of coupling parts applying to both areas the gear coupling  22  with its spherical gear shaft system  45  and the coupling with the wedges arranged along it  49  with the invention providing for an improved damping, an electrical isolation, plus enhanced flexibility in the misalignment resp. shifting areas  24 ,  25 . 
       FIG. 13  is a schematic depiction to explain the way of the application of the double-joint coupling  40  (as is shown in the  FIG. 11  and  FIG. 12 ) for rail vehicles each provided with one bevel quill ring  52 , which is, however, based on the more specific, thus completed drawing of the gear coupling  22 . The latter encloses the shaft  21  and exhibits a bevel  53 , which is connected with the gear shaft (not included in the drawing) at the driving end. If the application is based on dynamic conditions, the angular shift  25  can be applied, too. 
       FIG. 14  depicts a double-gimbal bogie-coupling arranged along it  60  based on the bogie-coupling arranged along it  30  and another bogie-coupling arranged along it  61 , whereas the aforementioned explanations may apply to both the bogie-coupling arranged along it  30  and the bogie-coupling  61  arranged along it. 
     Another field of application of the coupling ring  1  when used with double-joint couplings is the mounting of membrane couplings and ring disk couplings instead of gear couplings into the double-joint couplings. 
     The nature of the invention allows for the fixture of the coupling ring  1  by means of the direct radial screw-joint  20  belonging to the coupling ring  1  onto the axially shifted star&#39;s front facing areas  4 ,  5  of the coupling stars  2 ,  3 , which are positioned below the fastening elements  10 ,  11  and exhibit radially aligned threaded boreholes  14 , which are, in turn, diagonally aligned to the star centers. Furthermore, the distinct corresponding profiles  29 ,  31  serve as a supporting tool when it comes to the adjustment of the coupling ring  1  to the star&#39;s front facing areas  4 ,  5  of the coupling parts  8 ,  9 . 
     Apart from that, the fastening elements  10 ,  11  may consist of rigid material, which may either be formed by means of metal or another rigid substance/agent/material. 
     The fastening elements  10 ,  11  belonging to the coupling ring  1  may, as is the case with the elastic spring elements  17 , consist of various shapes, which correspond to the shapes of the fastening elements  10 ,  11 . 
     In the cross-sectional area, the fastening elements  10 ,  11  may exhibit a profile, which is at least formed on two opposing sides, thus in the direction starting from the external to the internal mid-position of the ring side and/or across the whole ring surface. 
     The fastening elements  10 ,  11  may be aligned towards the ring axis  23  in a wedged shape with the wedge-shaped narrow end range  32  being positioned at the internal side of the shaft and the wedge-shaped wide end range  33  being positioned at the external side of the ring. 
     The spring elements  17  consist of elastic material, i.e. preferably rubber. The elastic spring elements  17  may, however, also contain at least one supporting plate, which is each incorporated by way of a topographic exterior form, e.g. rounded surface and not directly aligned between two spring elements towards the ring axis  23 . 
     The spring elements  17  or parts  56 ,  57  of said elements may be formed with at least one radially and/or axially aligned concave center  39 ,  54  towards the ring axis  23 . 
     INDEX OF REFERENCE SIGNS 
     
         
           1  Coupling ring 
           2  Primary star 
           3  Secondary star 
           4  Primary star front facing area 
           5  Secondary star front facing area 
           6  Spring of the star front facing area 
           7  Notch of the star front facing area 
           8  Primary coupling part 
           9  Secondary coupling part 
           10  Primary fastening element 
           11  Secondary fastening element 
           12  Primary bore 
           13  Secondary bore 
           14  Threaded borehole 
           15  Spring of the fastening element 
           16  Notch of the fastening element 
           17  Spring element 
           18  Radially aligned supporting plate 
           19  Countersink notch/Countersink bore 
           20  Radially aligned screw-joint/screwing operation 
           21  Shaft 
           22  Gear coupling with spherical gear system 
           23  Axis of coupling ring 
           24  Axial misalignment/shift 
           25  Angular misalignment/shift 
           26  Star arm of the (primary) star 
           27  Star arm of the other (secondary) star 
           28  Mid-position of star/center of the star 
           29  Surface of the star front facing area/profile 
           30  Single-gimbal bogie-coupling 
           31  Surface of the fastening element/profile 
           32  Wedge-shaped narrow end-range 
           33  Wedge-shaped wide end-range 
           34  Adjustment screw 
           35  Front end gear shaft 
           36  Internal ring section 
           37  External ring section 
           38  Other (secondary) shaft 
           39  Mid-position of a spring element/part of a spring element 
           40  Double-joint coupling 
           41  Primary joint plane 
           42  Secondary joint plane 
           45  Spherical gear system 
           46  Sleeve 
           47  Coupling hub 
           48  Coupling axis 
           49  Elastic bogie-coupling with shaft connection 
           50  Clearance 
           51  Lid 
           52  Bevel quill ring 
           53  Bevel 
           54  Mid-position of a spring element/part of the spring element 
           55  Wedged shape of a supporting plate 
           56  Part of a spring element 
           57  Part of a spring element 
           60  Double-gimbal bogie coupling 
           61  Elastic-gimbal bogie coupling