Cardan double joint arrangement

Abstract

Cardan double joint arrangement with angular, radial and axial compensation behavior, comprising a first joint arrangement (1), a second joint arrangement (2) and an intermediate shaft (6) connecting the first and second joint arrangements (1, 2), wherein the first and / or the second joint arrangement (1, 2) each has a toothed part with circumferential broad crowned external teeth (4) which is in contact with a corresponding toothed part with circumferential internal teeth (3), wherein the ends of the connecting intermediate shaft (6) each have a toothed part with circumferential internal teeth (3) or a toothed part with circumferential broad crowned external teeth (4) or one end of the connecting intermediate shaft has a toothed part with circumferential internal teeth (3) and the other end has a toothed part with circumferential broad crowned external teeth (4),wherein the toothed part with circumferential broad crowned external teeth (4) engages with the toothed part with circumferential internal teeth (3) of the intermediate shaft or with a joint sleeve (3), and wherein in all operating modes there is a torsional backlash between the internal teeth and the broad crowned external teeth of ≤ 1.5°.

Description

[0001] The present invention relates to the technical field of mechanical engineering and drive technology and concerns a cardanic double joint arrangement which can be used, for example, in motor vehicles, rail vehicles, machines or aircraft.

[0002] Cardan shaft assemblies fulfill, among other functions, the task of transmitting torque and rotational motion between two misaligned shaft sections. In doing so, they provide a positive-locking connection and can compensate for angular, axial, or radial misalignment.

[0003] EP 0 878 368 A1 discloses a drive unit for railway vehicles, comprising an electric motor suspended from the vehicle frame or running gear, a gearbox, and a coupling, wherein the axle of the two driving wheels is guided through a hollow shaft, and wherein the coupling, which incorporates the hollow shaft, is provided between the wheelset formed from the axle and the driving wheels and the gearbox. A first part of a curved-tooth coupling is provided between the gearbox and the hollow shaft, and the output-side second part of the curved-tooth coupling is provided between the hollow shaft and the wheelset.

[0004] A drive unit for rail vehicles is known from DE 100 50 757 A1, in which the drive unit is equipped with an electric motor suspended from the vehicle frame or running gear, a gearbox, and a gimbal-acting coupling system. The coupling system is arranged between a wheelset axle and the gearbox, wherein a first part of the coupling system, in the form of a crowned-tooth coupling, is integrated into the output gear of the gearbox and into its lubricating oil circuit, and wherein a second, output-side part of the coupling system is provided between the gearbox and the wheelset. The second part of the coupling system is a rubber-elastic coupling.

[0005] Furthermore, EP 1 940 667 A1 discloses a cardanic double-joint coupling for rail vehicles with two joint planes, comprising two coupling joints connected to each other for torque transmission via a hollow pinion shaft and a shaft enclosed by the hollow pinion shaft. One joint plane is associated with a coupling joint featuring crowned teeth with angular and axial compensation capability, and the other joint plane is associated with a torsionally rigid, flexurally elastic coupling joint.

[0006] A double-jointed coupling in the form of a transverse drive with a motor is described in DE 295 22 268 U1, wherein the rotor shaft of the motor lies parallel to the drive axle of a rail vehicle and is connected to an axle drive comprising a hollow pinion shaft that surrounds a toothed shaft. The toothed shaft runs at least partially inside the hollow pinion shaft, with the rotor shaft being coupled to the toothed shaft at its output end via a motor output coupling, and the motor output coupling being designed as an angularly and axially flexible coupling. The toothed shaft is coupled to the hollow pinion shaft via a transmission drive coupling and axially fixed at its ends by coil springs, the coil springs returning the toothed shaft to its central position relative to the hollow pinion shaft after any deflection.

[0007] A disadvantage is that conventional joint designs have significant limitations in their range of motion, thus restricting both torque transmission and displacement capability. Another disadvantage is that known cardan joint designs are complex and expensive to maintain and repair.

[0008] The object of the invention is to provide a joint arrangement that enables improved angular displacements and high torque transmissions, provides improved radial and axial displacement capability, and is simple and cost-effective to assemble, maintain, and repair.

[0009] The problem is solved by the invention specified in the patent claims. Advantageous embodiments are the subject of the dependent claims, and the invention also includes combinations of the individual dependent patent claims in the sense of an AND conjunction, as long as they are not mutually exclusive.

[0010] The problem according to the invention is solved by a cardan double-joint arrangement with angular, radial and axial compensation behavior, comprising a first joint arrangement, a second joint arrangement and an intermediate shaft connecting the first and second joint arrangements, wherein the first and / or the second joint arrangement each has a toothed part with circumferential broad crowned external teeth, which is in contact with a corresponding toothed part with circumferential internal teeth, wherein the ends of the connecting intermediate shaft each have a toothed part with circumferential internal teeth or a toothed part with circumferential broad crowned external teeth, or one end of the connecting intermediate shaft has a toothed part with circumferential internal teeth and the other end has a toothed part with circumferential broad crowned external teeth.wherein the toothed part with circumferential broad crowned external teeth engages with the toothed part with circumferential internal teeth of the intermediate shaft or with a joint sleeve, and wherein in all operating modes there is a torsional backlash between the internal teeth and the broad crowned external teeth of ≤ 1.5°.

[0011] In an advantageous embodiment of the cardan double joint arrangement, the toothed parts with broad crowned external teeth are designed as a joint hub and / or as broad crowned external teeth in the end area of ​​the intermediate shaft.

[0012] It is also advantageous if the backlash is ≤ 0.5° in all operating modes.

[0013] It may be advantageous to provide that the intermediate shaft is designed as a solid shaft or at least partially as a hollow shaft.

[0014] Particularly advantageous is the intermediate shaft in the area of ​​the first joint arrangement, which is positively connected to the joint hub with broad crowned external teeth and engages with the internal teeth of a joint sleeve, and in the area of ​​the second joint arrangement, the intermediate shaft has internal teeth that engage with the broad crowned external teeth of a joint hub.

[0015] It is advantageous if the intermediate shaft is made of a metallic material, a polymeric material, a rubber-elastic material and / or a composite material.

[0016] It may be advantageous to provide that the intermediate shaft is at least partially made of an electrically insulating material.

[0017] In a further advantageous embodiment, it can be provided that the intermediate shaft is made of two or more pieces and / or is designed in two or more parts.

[0018] It is also advantageous if the first and second joint arrangement each have a sealing element in the formed free space.

[0019] Furthermore, it may be advantageous to provide that at least one joint arrangement has a closable opening.

[0020] Advantageously, the first and / or second joint arrangement can each have at least one coupling element at the end area, wherein the coupling element formed at the end area is particularly advantageously connected to a drive shaft, output shaft, motor, gearbox and / or a wheelset or wheelset axle in a torque-transmitting manner.

[0021] In the case of a cardan double joint arrangement, it can be advantageous if the connection of the first and / or the second joint arrangement with a drive shaft, output shaft, motor, gearbox and / or a wheelset or wheelset axle is realized by means of circumferential toothing, press fit, tapered connection, splined connection and / or screw connection.

[0022] Advantageously, the deflection angle of the first and second joint arrangement can be realized in the range of > 0° to 20° for each joint arrangement.

[0023] Advantageously, it can be provided that in the cardan double joint arrangement a combination with at least one arc tooth coupling, lamellar coupling, tab coupling, spring coupling, link coupling, ring disc coupling, a wedge pack and / or a wedge pack ring is implemented.

[0024] Furthermore, it is advantageous if the intermediate shaft has a cylindrical shape.

[0025] It is also advantageous if the gearing component is connected to the intermediate shaft by means of a press fit, face gearing or welded connection.

[0026] The cardanic double-joint arrangement according to the invention, with angular, radial, and axial compensation behavior, comprises a first joint arrangement, a second joint arrangement, and an intermediate shaft connecting the first and second joint arrangements. The two ends of the connecting intermediate shaft can be configured differently with respect to the provided toothing.

[0027] It is possible that both ends have the same tooth configuration, namely as a toothed section with circumferential internal teeth or as a toothed section with circumferential broad crowned external teeth. Alternatively, it is possible that the two ends of the connecting intermediate shaft have different tooth configurations, such that one end of the intermediate shaft is a toothed section with circumferential internal teeth, while the other end of the intermediate shaft is a toothed section with circumferential broad crowned external teeth.

[0028] The joint arrangement according to the invention therefore offers a high degree of variability in design and construction and enables flexible adaptation to the desired areas of application.

[0029] Furthermore, it may be provided that the toothed part with circumferential broad crowned external teeth or the toothed part with circumferential internal teeth engages with a joint sleeve.

[0030] In an advantageous embodiment, the toothed part with broad, convex external teeth can be designed as a joint hub.

[0031] In one embodiment of the cardan double-joint arrangement according to the invention, the intermediate shaft can be connected at its end end to a joint hub by means of a force-fit, material-fit, and / or positive-fit connection in the first and / or second joint arrangement. In this case, the intermediate shaft itself does not have internal teeth but is connected to a joint hub by at least a force-fit connection. The joint hub can be designed such that it has a toothed portion with broad, crowned external teeth, which in this case engages with the internal teeth of an additional joint sleeve.

[0032] In a further embodiment of the cardan double-joint assembly according to the invention, the intermediate shaft, which can be designed as a hollow shaft, has a toothed section with circumferential internal teeth at one or both ends, which engages with the broad crowned external teeth of the toothed section. This embodiment has the technical advantage that an additional joint sleeve is not required, thereby reducing material and manufacturing costs for the cardan double-joint assembly.

[0033] The essential aspect of the invention is that the interaction of the gearing element according to the invention, with its broad crowned external teeth, and the meshing gearing element with internal teeth of the intermediate shaft or a joint sleeve, results in a significantly improved axial, angular, and radial displacement capability of the joint assembly. This makes it possible to achieve a deflection angle of the first and second joint assembly in the range of > 0° to 20° for each joint assembly, and, moreover, only very low restoring forces occur during torque transmission.

[0034] Several technical advantages are achieved due to the interaction of the broad crowned external toothing of the toothed part and the low torsional backlash generated in the joint arrangements between the internal toothing and the broad crowned external toothing ≤ 1.5°.

[0035] The minimal backlash present in all operating modes, which can advantageously be ≤ 0.5°, enables very smooth running of the double-jointed cardan joint assembly, thus preventing unwanted rolling movements when stationary, knocking noises, or rattling, especially when changing the direction of load. Furthermore, higher accuracy in power transmission is achieved, providing optimized operating modes without unwanted idling during direct torque transmission.

[0036] By using two joint assemblies connected by an intermediate shaft, each featuring a toothed section with broad crowned external teeth and an intermediate shaft and / or joint sleeve with internal teeth, improved compensation for bending of the intermediate shaft is achieved. Due to the uniform surface pressure across the width of the meshing teeth, improved radial, axial, and angular displacement capability is enabled at high power density between the drive and driven sides.

[0037] The intermediate shaft can be connected at its end end, either on both sides or on one side, to the joint hubs of the first and second joint arrangement by means of force-fit, material-fit and / or form-fit connections, and in conjunction with the broad crowned external toothing of the joint hub enables a high axial and radial compensation behavior between the drive and driven unit or between a drive shaft and driven shaft, as well as improved compensation of any angular misalignment that occurs.

[0038] In an advantageous embodiment, a sealing element can be provided that protects the free space of the engaging internal teeth and broadly convex external teeth against the ingress of dirt.

[0039] To achieve weight savings through a lighter design and lower manufacturing costs, it can be advantageous to design the intermediate shaft at least partially as a hollow shaft and / or cylindrical. It is conceivable that the intermediate shaft is designed as a solid shaft in the area of ​​the joint hubs, while the exposed area between the first and second joint arrangements is designed as a hollow shaft.

[0040] In an advantageous embodiment of the cardan double joint arrangement, it can be provided that in the area of ​​the first joint arrangement the intermediate shaft has a toothed part with circumferential internal teeth at one end and is connected at least positively to the toothed part with circumferential broad crowned external teeth, wherein the circumferential broad crowned external teeth of the toothed part engage with the circumferential internal teeth of the intermediate shaft or a joint sleeve.

[0041] It is also conceivable that the intermediate shaft is designed as a solid shaft in one end section and as a hollow shaft in the other. This makes it possible to combine two different designs in a single cardan joint assembly. For example, the first joint assembly could have internal splines on the hollow shaft and broad, crowned external splines on a joint hub, while in the second joint assembly, the intermediate shaft is connected to a joint hub by force-fit, material-fit, and / or positive locking, where the internal splines of a joint sleeve and the broad, crowned external splines of the joint hub engage. This allows for variable adaptation of the design to the specific requirements of each application and increases the flexibility of the cardan double joint assembly.

[0042] Depending on the stress profile and technical application, it may be advantageous for the intermediate shaft to be made of various materials, such as a metallic material, a polymeric material, a rubber-elastic material, and / or a composite material. For example, in an advantageous embodiment of the intermediate shaft, it is conceivable that, for electrical insulation between the drive and driven units, the intermediate shaft is made at least partially of an electrically insulating material, thereby effectively preventing electrical flashover. It is also conceivable that the electrical insulation is implemented in the area of ​​the shaft-hub connection between the intermediate shaft and the gear teeth.

[0043] In addition, it can be advantageously provided that the intermediate shaft is made of an elastic material, which enables, for example, a damped transmission of the torque between the first and second joint arrangement and a variably adjustable torsional stiffness.

[0044] For a flexible design as well as time- and cost-saving repair and maintenance of the cardan double joint arrangement, it can be advantageously provided that the intermediate shaft is designed in two or more parts and / or in two or more sections.

[0045] The special design of the joint arrangement, and in particular the design of the intermediate shaft with a toothed section featuring internal teeth and / or a toothed section with broad, crowned external teeth, or in a further special design of the joint arrangement in conjunction with the internal teeth of a sleeve, has the technical advantage that only low restoring forces occur with low friction, thus achieving long maintenance intervals. The cardan double-joint arrangement, by providing the first and second joint arrangements according to the invention in conjunction with the flexibly designed and arranged intermediate shaft, can also be used in permanently vibration-free operation even when an ideal W- or Z-arrangement of the drive and output sides cannot be achieved.This is achieved, among other things, by an improved displacement capability of the first and second joint arrangement, which allows a deflection angle of up to 20° per joint arrangement while simultaneously minimizing vibration excitation, due to the homokinetic force and torque transmission and the constant angular velocity.

[0046] The cardan double-joint arrangement according to the invention can advantageously have at least one closable opening through which time-saving lubrication of at least the meshing gear teeth can be achieved, thereby enabling extended maintenance and repair intervals. A closable opening can, for example, be a cover provided on the end face, a plug, a screw connection, or a lubrication device.

[0047] In an advantageous embodiment of the cardan double-joint arrangement, the force-fit and / or positive-locking connection of the intermediate shaft, in the case of a toothed component acting as the joint hub of the first and / or the second joint arrangement, can be achieved by means of circumferential toothing, press fit, tapered connection, splined connection, and / or bolting. This enables a reliable shaft-hub connection with high torque and force transmission.

[0048] It is conceivable that the cardan double joint arrangement with the coupling elements formed at the ends is connected to a drive shaft, output shaft, motor, gearbox, single wheel and / or a wheelset or wheelset axle in a torque-transmitting manner.

[0049] The technical characteristics of high axial, radial, and angular displacement capacity, combined with low maintenance requirements, make it possible to expediently install the double-joint arrangement at points in the drive and driven components of, for example, a vehicle, a machine, or a power unit where lubrication and sealing are easily managed and where limited installation space is required. The cardanic double-joint arrangement according to the invention enables high fatigue strength, maintenance-free operation, a small footprint, and high displacement capacity.

[0050] The technical advantages and effects of the novel double-jointed gimbal arrangement are that - by combining two joint arrangements with an intermediate shaft, improved axial, radial and angular displacement capability of the joint arrangement is achieved, - The circumferential, wide-crowned external toothing of the joint hubs improves the fit and functionality of the double-joint arrangement, especially under high loads or unfavorable installation conditions, and prevents overloading in the center of the toothing, thereby significantly reducing wear despite the low backlash of ≤1.5° occurring in all operating modes. - a high power density is provided and - low restoring forces are achieved, which in particular allow for smaller dimensions of the bearings in the connected components of the input and output shafts.

[0051] The invention is explained in more detail below with reference to four exemplary embodiments. The associated Fig. Figures 1 to 5 show schematic representations of possible embodiments of the cardan double joint arrangement according to the invention. Example 1

[0052] In Fig. Figure 1 is a schematic representation of a cardan-type double-joint arrangement for rail vehicles with two articulation planes, comprising two joint assemblies. The first joint assembly 1 is frictionally connected to a drive shaft 5 of a motor via a flange connection of the first joint sleeve 3. The second joint assembly 2 is frictionally connected to an output shaft of a gearbox via a flange connection of the second joint sleeve 3. The first and second joint assemblies 1, 2 are connected for torque transmission by a cylindrical intermediate shaft 6, which is designed as a solid metallic shaft in the area of ​​the joint hubs and as a hollow shaft with an enlarged circumference in a central region. In the central region, the cylindrical intermediate shaft 6 consists of an electrically insulated composite material.The first and second joint arrangements 1, 2 each have an interchangeable joint sleeve 3 with internal teeth and a joint hub with corresponding broad, crowned external teeth, wherein the cylindrical intermediate shaft 6 is connected to the joint hub at its end by means of an interference fit. The backlash between the internal teeth of the cylindrical intermediate shaft 6 and the broad, crowned external teeth of the joint hub is a maximum of 0.5° in all operating modes. The first and second joint arrangements 1, 2 each have a sealing element between the joint hub and the joint sleeve 3, which hermetically seals the space between the meshing internal teeth of the joint sleeve 3 and the external teeth of the joint hub. The cardanic double joint arrangement can be configured and used in any configuration with joint planes in the area of ​​drives or wheelsets, with joint planes differing from Z or W arrangements.The second joint assembly 2 with broad crowned external teeth is arranged in the protected area of ​​a gearbox, where sufficient space is available for displacement. The first and second joint assemblies 1, 2 have a cover for sealing the interior from the outside and for possible lubrication of the meshing internal teeth of the cylindrical intermediate shaft 6 and the broad crowned external teeth of the joint hubs. Example 2

[0053] In Fig. Figure 2 is a schematic representation of a cardan joint for rail vehicles with two articulation planes, comprising two joint arrangements. The first and second joint arrangements 1, 2 are connected for torque transmission by a cylindrical intermediate shaft 6, which is designed as a continuous hollow shaft. The first and second joint arrangements feature joint hubs 4 with broad crowned teeth, which are positively connected to a drive shaft 5 and an output shaft by means of an interference fit. At its end, on the drive side, the cylindrical intermediate shaft 6 has a joint sleeve 3 with internal teeth that engages with the broad crowned external teeth of the corresponding joint hubs 4. On the output side, the intermediate shaft 6 has a toothed section with broad crowned external teeth 4 that engages with the internal teeth of the joint sleeve 3.The backlash between the internal teeth of the cylindrical intermediate shaft 6 and the crowned external teeth of the joint hubs 4 is a maximum of 0.45° in all operating modes. The first and second joint arrangements 1, 2 each have a sealing element between the joint hub 4 and the joint sleeve 3, which hermetically seals the space between the meshing internal teeth of the joint sleeve 3 and the external teeth of the joint hub 4. The double-jointed cardan joint arrangement can be configured with joint planes in either a Z or W arrangement in the area of ​​drives or gear sets. The second joint arrangement 2, with crowned external teeth on the joint hub 4 and internal teeth on the cylindrical intermediate shaft 6, is located in the protected area of ​​a gearbox where sufficient space is available for displacement.The first and second joint arrangements 1, 2 have a cover for sealing the interior to the outside and for possible lubrication of the meshing internal teeth of the cylindrical intermediate shaft 6 and broad crowned external teeth of the joint hubs 4. Example 3

[0054] Figure 3 schematically shows a double-jointed cardan joint for rail vehicles with two articulation planes, comprising two differently designed joint assemblies 1 and 2. The first joint assembly 1 is frictionally connected to a drive shaft 5 of a motor via a flange connection of the joint sleeve 3. The first and second joint assemblies 1, 2 are connected by a cylindrical intermediate shaft 6 for torque transmission. In the region of the joint hub 4 of the first joint assembly, the intermediate shaft 6 is designed as a solid metallic shaft, and at least in the region of the second joint assembly, it is designed as a hollow shaft. The first joint assembly 1 has a joint sleeve 3 with internal teeth and a joint hub 4 with corresponding broad crowned external teeth, wherein the cylindrical intermediate shaft 6 is connected to the joint hub 4 at its end by means of an interference fit in the first joint assembly.The cylindrical intermediate shaft 6 is designed as a hollow shaft at its other end and has internal teeth at the end end in the area of ​​the second joint assembly. These teeth mesh with the broad, crowned external teeth of the corresponding joint hubs 4. The backlash between the internal teeth of the cylindrical intermediate shaft 6 and the broad, crowned external teeth of the joint hub 4 is a maximum of 0.5° in all operating modes. The first and second joint assemblies 1, 2 each have a sealing element between the joint hub 4 and the joint sleeve 3, which hermetically seals the space between the meshing internal teeth of the joint sleeve 3 and the external teeth of the joint hub 4. The double-jointed cardan joint assembly can be configured with joint planes in either a Z or W arrangement in the area of ​​drives or wheelsets.The second joint assembly 2 with broad crowned external teeth is arranged in the protected area of ​​a gearbox, where sufficient space is available for displacement. The first and second joint assemblies 1, 2 have a cover for sealing the interior from the outside and for possible lubrication of the meshing internal teeth of the cylindrical intermediate shaft 6 and the broad crowned external teeth of the joint hubs 4. Example 4

[0055] The Fig. 4 and Fig. Figure 5 schematically shows a double-jointed gimbal arrangement for rail vehicles with two articulation planes, each featuring two differently designed joint arrangements 1, 2. According to Fig. 4 The first joint assembly 1 is positively connected to a drive shaft 5 of a motor via a flange connection of the first joint sleeve 3. The second joint assembly 2 is connected according to Fig. 4 a curved tooth coupling 8 and according to Fig. 5 a wedge pack coupling 9 which is positively connected to the output shaft of a gearbox. The first and second joint arrangements 1, 2 are connected by an intermediate shaft 6 for torque transmission. In the embodiment according to Fig. 4 The first joint arrangement 1 is designed such that the internal teeth of the intermediate shaft 6, which is designed as a hollow shaft in the area of ​​the first joint arrangement 1, engage with the joint hub 4 with its associated broad crowned external teeth. The backlash between the internal teeth of the cylindrical intermediate shaft 6 and the broad crowned external teeth of the joint hub 4 is a maximum of 0.30° in all operating modes. In the embodiment according to Fig.In the first joint arrangement 1, the intermediate shaft 6 is designed such that it is a solid shaft and is positively connected to the joint hub 4 with a circumferential, broadly crowned external toothing. The backlash between the internal toothing of the intermediate shaft 6 and the broadly crowned external toothing of the joint hub 4 is a maximum of 0.45° in all operating modes. Reference symbol list 1 First joint arrangement 2 Second joint arrangement 3 Toothed part with circumferential internal toothing / Joint sleeve 4 Toothed part with circumferential wide crowned external toothing / joint hub 5 Drive shaft 6 Intermediate shaft 7 Output shaft 8 curved tooth coupling 9 wedge pack coupling QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] EP 0 878 368 A1

[0003] DE 100 50 757 A1

[0004] EP 1 940 667 A1

[0005] DE 295 22 268 U1

[0006]

Claims

[1] Cardan double joint arrangement with angular, radial and axial compensation behavior, comprising a first joint arrangement (1), a second joint arrangement (2) and an intermediate shaft (6) connecting the first and second joint arrangements (1, 2), wherein the first and / or the second joint arrangement (1, 2) each has a toothed part with circumferential broad crowned external teeth (4) which is in contact with a corresponding toothed part with circumferential internal teeth (3), wherein the ends of the connecting intermediate shaft (6) each have a toothed part with circumferential internal teeth (3) or a toothed part with circumferential broad crowned external teeth (4) or one end of the connecting intermediate shaft has a toothed part with circumferential internal teeth (3) and the other end has a toothed part with circumferential broad crowned external teeth (4),wherein the toothed part with circumferential broad crowned external teeth (4) engages with the toothed part with circumferential internal teeth (3) of the intermediate shaft or with a joint sleeve (3), and wherein in all operating modes there is a torsional backlash between the internal teeth and the broad crowned external teeth of ≤ 1.5°. [2] Cardan double joint arrangement according to claim 1, wherein the toothed parts with broad crowned external teeth (4) are designed as a joint hub and / or as broad crowned external teeth in the end region of the intermediate shaft (6). [3] Cardan double joint coupling according to claim 1, wherein the torsional backlash is ≤ 0.5° in all operating modes. [4] Cardan double joint arrangement according to claim 1, wherein the intermediate shaft (6) is designed as a solid shaft or at least partially as a hollow shaft. [5] Cardan double joint arrangement according to claim 2, wherein the intermediate shaft (6) in the area of ​​the first joint arrangement is force-fit connected to the joint hub with broad crowned external teeth (4) and engages with the internal teeth of a joint sleeve (3), and wherein in the area of ​​the second joint arrangement the intermediate shaft has internal teeth which engage with the broad crowned external teeth of a joint hub (4). [6] Cardan double joint arrangement according to claim 1, wherein the intermediate shaft (6) is made of a metallic material, a polymeric material, a rubber-elastic material and / or a composite material. [7] Cardan double joint arrangement according to claim 1, wherein the intermediate shaft (6) is made at least partially of an electrically insulating material. [8] Cardan double joint arrangement according to claim 1, wherein the intermediate shaft (6) is made of two or more pieces and / or is made of two or more parts. [9] Cardan double joint arrangement according to claim 1, wherein the first and second joint arrangement (1,2) each have a sealing element in the formed free space. [10] Cardan double joint arrangement according to claim 1, wherein at least one joint arrangement (1,2) has a closable opening. [11] Cardan double joint arrangement according to claim 1, wherein the first and / or second joint arrangement (1,2) each has at least one coupling element at its end region. [12] Cardan double joint arrangement according to claim 11, wherein the coupling element formed at the end area is connected to a drive shaft (5), a motor, a gearbox and / or a wheelset or a wheelset shaft in a torque-transmitting manner. [13] Cardan double joint arrangement according to claim 1, wherein the connection of the first and / or the second joint arrangement (1,2) to a drive shaft, a motor, a gearbox and / or a wheelset or a wheelset axle is realized by means of circumferential toothing, press fit, tapered connection, splined connection and / or screw connection. [14] Cardan double joint arrangement according to claim 1, wherein the deflection angle of the first and second joint arrangement (1,2) is achievable in the range of > 0° to 20° for each joint arrangement. [15] Cardan double joint arrangement according to claim 1, wherein a combination with at least one arc tooth coupling (8), lamellar coupling, tab coupling, spring coupling, link coupling, ring disc coupling, a wedge pack coupling (9) and / or a wedge pack ring is realized. [16] Cardan double joint arrangement according to claim 1, wherein the intermediate shaft (6) has a cylindrical shape. [17] Cardan double joint arrangement according to claim 1, wherein the toothed part (3,4) is connected to the intermediate shaft (6) by means of a press fit, face toothing or welded connection.

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