Double-joint coupling, bogie, railway vehicle, industrial applications and computer program product

Abstract

The invention relates to a double joint coupling (10) comprising a hollow pinion shaft (20) connected to an internal toothing (52) and an intermediate shaft (30) connected to a clutch toothing (34) to mesh with the internal toothing (52), wherein the clutch toothing (34) on the intermediate shaft is designed to be able to pass through the hollow pinion shaft (20).

Description

TECHNICAL FIELD

[0001] The invention relates to a double-joint coupling and a method of assembling a double-joint coupling. The invention further relates to a bogie of a rail vehicle having such a double-joint coupling and to a corresponding rail vehicle itself. The invention further relates to a computer program product for simulating the operating behavior of such a double-joint coupling and to an industrial application provided with a double-joint coupling according to the invention. BACKGROUND

[0002] The publication EP 2 457 795 A1 discloses a coupling device for connecting a driving machine part to a driven machine part. The coupling device comprises a toothed coupling and an articulated lever coupling. The toothed coupling is connected with a hollow shaft, which in the assembled state extends through the hollow shaft with an outer toothing of the toothed coupling and a shaft of a connecting flange for a plate. In order to assemble the coupling device, the shaft is configured to be separable between the toothed coupling and the articulated lever coupling.

[0003] The international patent application WO 2007 / 036219 A1 discloses a cardan double-joint coupling for a rail vehicle, which comprises a hollow pinion shaft, through which a middle shaft extends. The middle shaft is releasably connected at one end to an outer toothing coupling hub of a toothed coupling.

[0004] The utility model DE 295 22 268 U1 discloses a transverse drive for a rail vehicle, in which a large wheel engages with a hollow pinion shaft. In the hollow pinion shaft a toothed shaft is provided. The toothed shaft has at both ends an outer toothing, wherein one of the outer toothings engages with an inner toothing structure formed thereon of the hollow pinion shaft. The other outer toothing end engages in an inner toothing structure of a coupling flange. SUMMARY

[0005] Double-joint couplings are used in various applications and are subjected to stresses, which makes it necessary to check the coupling. There is also a need to produce a coupling which is simple and cost-effective, while at the same time having a high compensation capacity for deflections. This applies in particular to industrial applications or rail vehicles. It is an object of the invention to provide a double-joint coupling which provides an improvement with respect to at least one of the points mentioned.

[0006] The object is achieved by the double joint coupling according to the present invention. The double joint coupling comprises a hollow pinion shaft which is connected with an internal tooth structure such that a rotation of the hollow pinion shaft can be transmitted to the internal tooth structure. The double joint coupling further comprises an intermediate shaft which is connected with a coupling tooth structure such that a rotation of the intermediate shaft can be transmitted to the coupling tooth structure. The coupling tooth structure is configured to mesh with the internal tooth structure on the hollow pinion shaft, thereby configuring a toothed coupling at one end of the hollow pinion shaft. Accordingly, a rotation of the hollow pinion shaft can be transmitted to the intermediate shaft by the toothed coupling. According to the present invention, the coupling tooth structure which is connected with the intermediate shaft is configured to be realized by the hollow pinion shaft. To this end, the coupling tooth structure has an outer diameter which is smaller than the inner diameter of the hollow pinion shaft. This makes it possible that the intermediate shaft can be provided separately from other components and that the intermediate shaft can be handled as one complete subassembly. Furthermore, the additional assembly of the double joint coupling requires a reduced number of components and assembly steps. Moreover, the double joint coupling according to the present invention can be quickly disassembled into its largest subassembly by pulling apart the intermediate shaft and the hollow pinion shaft. Thereby, the maintenance or repair of the double joint coupling is simplified.

[0007] In one embodiment of the claimed double joint coupling, the coupling tooth structure is integrally configured with the intermediate shaft, that is to say, cannot be separated from each other without being destroyed. The coupling tooth structure can be made from the same workpiece as the intermediate shaft, thereby further reducing the number of components in the claimed double joint coupling. Alternatively, the coupling tooth structure and the intermediate shaft can also be connected to each other by form locking, for example by welding. Due to the integrality of the coupling tooth structure with the intermediate shaft, an improved cost efficiency and a high degree of modularity is achieved, the machining complexity is minimized and the ease of maintenance of the double joint coupling is further improved.

[0008] Furthermore, the thrust ring can be arranged in the region of the coupling toothing on the intermediate shaft. In this case, the thrust ring has an outer diameter which is smaller than the inner diameter of the hollow pinion shaft. Thereby, the thrust ring can be introduced together with the intermediate shaft through the hollow pinion shaft. The thrust ring allows to provide a seal between the toothed coupling and the hollow pinion shaft in the assembled state, thereby reducing the loss of working medium, for example lubricant. In order to provide the seal, at least one sealing element, for example an O-ring, can be arranged on the outer surface of the thrust ring. For this purpose, for example, a circumferential groove can be configured in the outer surface of the thrust ring. Depending on the axial position of the at least one sealing element, the thrust ring is configured to create a seal between the intermediate shaft and the hollow pinion shaft or the carrier ring. For this purpose, the inner diameter of the hollow pinion shaft and the outer diameter of the thrust ring are selected such that between them an annular space can be configured having an assembly gap width which is smaller than the radial dimension of the at least one sealing element in the unloaded state. Such an assembly gap width can be adjusted in a simple manner by determining the dimensions of the outer diameter of the coupling toothing and the inner diameter of the hollow pinion shaft accordingly. In particular, alternatively or additionally, a retaining ring can be provided on the outer surface, by which the axial movement of the intermediate shaft can be supported, i.e. limited. Thereby, an end stop for the coupling toothing is provided. The retaining ring also allows a reliable assembly. In this case, the term "axial movement" or "axial position" is to be understood as a movement or position along the rotational axis of the intermediate shaft and the hollow pinion shaft.

[0009] Furthermore, at least one sealing element can be arranged on the inner surface of the thrust ring. Thereby, a seal can be created between the intermediate shaft and the thrust ring. For this purpose, the sealing element can be configured as an O-ring, for example, which is accommodated in a circumferential groove on the inner surface of the thrust ring. Thereby, the loss of working medium, for example the discharge of lubricant from the toothed coupling, can also be reduced. In a further embodiment of the claimed double-joint coupling, the sealing element has two sealing lips. Such a sealing element is also referred to as double sealing ring and provides an enhanced sealing effect.

[0010] In a further embodiment of the claimed double-joint coupling, the thrust ring is configured to be axially supported on the hollow pinion shaft. For this purpose, the thrust ring has an outer diameter which is greater than the inner diameter of the hollow pinion shaft. Thereby, the axial movement of the intermediate shaft can be supported and for this purpose no additional retaining ring is required. Thus, the claimed double-joint coupling has a reduced number of components.

[0011] Furthermore, the carrier ring, on which the inner tooth structure is arranged, can be releasably connected to the hollow pinion shaft. To this end, the carrier ring is essentially configured as a frame, wherein the inner tooth structure is releasably arranged in the carrier ring or is integrally configured therewith. The inner tooth structure can be separated from the double joint coupling claimed by the carrier ring and can be individually inspected and repaired. Likewise, the carrier ring can be produced individually. Thereby, the production complexity of the double joint coupling claimed is reduced. Upon disassembly of the double joint coupling claimed, the torque transmission from the hollow pinion shaft to the intermediate shaft can be interrupted by loosening the carrier ring from the hollow pinion shaft. The components of the double joint coupling itself, such as the intermediate shaft, or the components of the drive train to which the double joint coupling belongs, become free-floating due to this interruption of the torque transmission. The carrier ring can be loosened from the hollow pinion shaft at an early stage of the disassembly in order to simplify the disassembly as a whole at an early stage. Thus, the double joint coupling claimed provides a high degree of maintenance friendliness. Alternatively, the carrier ring can be integrally configured with the hollow pinion shaft and have the inner tooth structure. Due to the integral configuration of the carrier ring with the hollow pinion shaft, the modular concept is further implemented and the assembly complexity is reduced by reducing the number of components.

[0012] Furthermore, the intermediate shaft in the double joint coupling claimed can be configured with a flange-like web. In this case, the flange-like web is arranged at the end of the intermediate shaft facing away from the gear coupling. The flange-like web can be connected to a flange-like bundle, so that a second articulation plane can be generated at this location in addition to the gear coupling as a first articulation plane. To this end, the flange-like web can be made of the same workpiece as the intermediate shaft. Alternatively, the flange-like web can also be connected to the intermediate shaft by material bonding, for example by welding. Due to the integrity between the flange-like web and the intermediate shaft, they cannot be separated from each other without being destroyed. Thereby, the flange-like web can be manufactured as a whole in a simple, fast and economical manner. Furthermore, the flange-like web is provided with a mounting hole, which allows the intermediate shaft to be fixed to the hollow pinion shaft during mounting. Thus, the assembly of the double joint coupling claimed can be selectively interrupted. Alternatively, the intermediate shaft can also be provided integrally with an additional coupling tooth structure, by which an additional gear coupling is generated.

[0013] In another embodiment of the double joint coupling claimed, the intermediate shaft is configured as a hollow shaft. This allows a weight-reducing construction type and a reduction of the moment of inertia of the intermediate shaft. Likewise, the free space in the hollow shaft can also be used to introduce a tool, for example for a center screw.

[0014] The basic object is also achieved by a method for assembling a double joint coupling according to the application. The double joint coupling comprises a hollow pinion shaft, an intermediate shaft with a coupling toothing, a thrust ring and a carrier ring, which are assembled by the method according to the application. In a first step, the hollow pinion shaft is provided, which is held or fixed in the appropriate form. In a subsequent second step, the intermediate shaft is introduced through the hollow pinion shaft. In this case, the intermediate shaft is pushed from one end of the hollow pinion shaft to the other end in the direction of the coupling toothing constructed thereon. After the intermediate shaft has been introduced, the coupling toothing protrudes at least partially in the axial direction from the hollow pinion shaft. In a subsequent third step, at least one sealing element and / or a fixing element are mounted to the outer surface of the thrust ring arranged on the intermediate shaft. The at least one sealing element can be configured as an O-ring and creates a seal between the thrust ring and thus the intermediate shaft and the hollow pinion shaft. The fixing element can be configured, for example, as a fixing ring suitable for supporting the axial movement of the intermediate shaft. In a further fourth step, the carrier ring is fixed to the hollow pinion shaft. The carrier ring has an inner toothing configured to engage with the coupling toothing. By fixing the carrier ring to the hollow pinion shaft, an engagement is created between the coupling toothing and the inner toothing, thus creating a toothed coupling. Thus, the torque transmission from the hollow pinion shaft to the intermediate shaft is achieved, thus providing the main function of the double joint coupling.

[0015] The hollow pinion shaft and the intermediate shaft constitute the heaviest components of the double joint coupling according to the application. In the method according to the application, the number of assembly steps in which these components have to be handled is correspondingly minimized. As soon as the intermediate shaft is passed through the hollow pinion shaft, the assembly of at least one sealing element and / or a fixing element can be easily carried out. Furthermore, relatively light components have to be handled in order to provide torque transmission between the hollow pinion shaft and the intermediate shaft with the carrier ring. The inner toothing and / or the carrier ring can be adjusted by corresponding tolerances to ensure simple assembly in the third step. In general, the assembly of the proposed double joint coupling is thereby accelerated and simplified, thus also achieving a greater degree of maintenance convenience. The method according to the application can also be developed to form a method for disassembling the corresponding double joint coupling in the order of the steps shown in reverse order.

[0016] In one embodiment of the claimed method, in a first step, a thrust ring is mounted to the intermediate shaft. The thrust ring can be configured as an open ring, which engages when mounted to the intermediate shaft. In this case, the thrust ring is fixed to the intermediate shaft in the region of the coupling toothing, that is to say, essentially adjacent to the coupling toothing, and in a second step, together with the coupling toothing, is passed through the hollow pinion shaft. Alternatively, the thrust ring can be mounted to the intermediate shaft directly after the second step, that is to say, when the coupling toothing is passed through the hollow pinion shaft. To this end, the thrust ring can also be configured as an open ring, which engages when fitted to the intermediate shaft.

[0017] Similarly, this object is achieved by a bogie for a rail vehicle according to the invention. The bogie comprises a traction motor, which is connected to a double-joint coupling in order to transmit torque. The double-joint coupling is in turn connected to an axle or a wheel of the rail vehicle by means of a gear mechanism in order to transmit torque. According to the invention, the double-joint coupling is configured according to one of the above-mentioned embodiments. Due to the double-joint coupling according to the invention, the production, maintenance and repair of the bogie is simplified. In particular, the double-joint coupling can be assembled and / or disassembled according to one of the above-mentioned methods.

[0018] Similarly, the object is achieved by a rail vehicle according to the invention, which comprises a vehicle body, at least one bogie being mounted on the vehicle body. Here, the term "rail vehicle" is to be understood as any motor vehicle which moves by means of a wheel / rail system. For example, the rail vehicle can be configured as a locomotive, a tram, a railcar, a monorail train, a maglev train, an underground train, a suburban train or a tramway. In this case, the bogie is configured according to one of the above-mentioned embodiments. By using a bogie according to the invention, the operation of such a rail vehicle becomes more efficient, since by the increased ease of maintenance of the bogie, the downtime can be reduced.

[0019] Furthermore, the basic object is achieved by an industrial application according to the invention, which comprises a drive unit connected to an output unit in order to transmit torque. The drive unit can be in the form of an electric motor, a combustion engine or a hydraulic motor, for example. By means of the drive unit, a drive power to be transmitted to the output unit is provided via an output shaft. The drive unit can be configured as a mill, a vertical mill, a sugar mill, a cement mill, a rock crusher, a conveyor belt, a pump, a roller press, a belt conveyor, a drilling machine, a rotary furnace, a slewing mechanism, a mixer, a hoisting device, a milling machine or a scrap press, for example. To this end, the output unit has an input shaft, which is connected to the output shaft of the drive unit by means of a coupling. The coupling is configured according to one of the above-mentioned embodiments according to the invention.

[0020] Similarly, the objects proposed are achieved by a computer program product according to the application, which is configured to simulate the operating behavior of a double-joint coupling. The term "operating behavior" is to be understood as, for example, the bending behavior or the wear behavior of the individual components. The kinematic setup and / or the vibration behavior of the double-joint coupling can also be simulated by the computer program product. Thus, the operating behavior of the double-joint coupling can be simulated in the assembled state in a rail vehicle. This can include driving operation and maintenance operation. The double-joint coupling thus maps its physical behavior in the computer program product according to the application and can be provided with a data interface by means of which an additional computer program product for simulation can transmit input values to the computer program product according to the application. In the same way, the computer program product can also be provided with a data interface for transmitting output values of the computer program product according to the application to an additional computer program product for simulation. By means of the computer program product, for example, the plausibility of the measurement data of sensors installed on the double-joint coupling and / or on the bogie can be checked. By means of the computer program product, in particular, defective sensors on the double-joint coupling and / or on the bogie can be detected. The computer program product can be configured as a so-called digital twin. Such a digital twin is proposed, for example, in the patent publication US 2017 / 286572 A1. The disclosure of US 2017 / 286572 A1 is also included by reference in this application. According to the application, the double-joint coupling that can be simulated by the computer program product claimed is configured according to one of the above-mentioned embodiments. BRIEF DESCRIPTION OF DRAWINGS

[0021] The application is explained in more detail below with reference to the individual embodiments in the figures. The figures are intended to be complementary to one another, since the same reference signs in different figures have the same technical meaning. The features of the individual embodiments can also be combined with one another. Furthermore, the embodiments shown in the figures can be combined with the above-mentioned features. In the figures, the following is shown in detail:

[0022] Figure 1 A first embodiment of the double-joint coupling claimed is shown schematically during a phase of the production method claimed;

[0023] Figure 2 A first embodiment of the double-joint coupling claimed is shown schematically during an additional phase of the production method claimed;

[0024] Figure 3 A first embodiment of the double-joint coupling claimed is shown schematically during an additional phase of the production method claimed;

[0025] Figure 4A longitudinal section of the first embodiment of the double-joint coupling claimed is schematically shown during an additional phase of the production method claimed;

[0026] Figure 5 A longitudinal section of the first embodiment of the double-joint coupling claimed is shown in the assembled state;

[0027] Figure 6 A longitudinal section of the second embodiment of the double-joint coupling claimed is shown in the assembled state;

[0028] Figure 7 The structure of an embodiment of the railway vehicle claimed is schematically shown;

[0029] Figure 8 The structure of an embodiment of the industrial application claimed is schematically shown. DETAILED DESCRIPTION

[0030] Figure 1 A longitudinal section of the first embodiment of the double-joint coupling claimed is schematically shown during a phase of the method 100 claimed. Figure 1 On the basis of the fact that the first step 110, in which the hollow pinion shaft 20 is provided, has already been completed, and the thrust ring 40 is fixed on the intermediate shaft 30. According to Figure 1 , the second step 120 is performed, in which the intermediate shaft 30 is introduced through the hollow pinion shaft 20. To this end, the hollow pinion shaft 20 has a clear internal space 21. The introduction movement is in the direction of the arrow F2. Figure 1The hollow pinion shaft 20 has a pinion toothing 22 via which a torque 25 can be introduced into the hollow pinion shaft 20 and as a result of which the hollow pinion shaft 20 and the intermediate shaft 30 can be rotated about the axis of rotation 15. The intermediate shaft 30 has a shaft portion 32 which has a first end 31 at which a coupling toothing 34 is configured. The coupling toothing 34 is a helical toothing 36 and is configured integrally with the shaft portion 32. As a result of the helical toothing 34, an inclination movement 13 can be carried out between the hollow pinion shaft 20 and the intermediate shaft 30 at the first end 31 of the intermediate shaft 30 in the first articulation plane 11. The outer diameter 38 of the coupling toothing 34 is smaller than the inner diameter 24 of the hollow pinion shaft 20. A wall spacing 27 is therefore provided between the coupling toothing 34 and the hollow pinion shaft 20 which allows the intermediate shaft 30 to be introduced 37 through the hollow pinion shaft 20 in the direction of the mounting flange 26. A thrust ring 40 which is arranged on the shaft portion 32 on the intermediate shaft 30 in the region of the coupling toothing 34 when viewed along the axis of rotation 15 has an outer diameter 42 which is smaller than the inner diameter 24 of the hollow pinion shaft 20. The thrust ring 40 is in the form of an open ring, the components of which engage in the radial direction and can be introduced through the hollow pinion shaft 20 in the assembled state. In order to introduce 37, an axial force 17 can be applied to the sheet flange 35 at the second end 33 of the intermediate shaft. The sheet flange 35 belongs to a sheet coupling which is not shown in more detail and by means of which an inclination movement 13 can be carried out in the second articulation plane 12 in the region of the second end 33 of the intermediate shaft.

[0031] Figure 2 A first embodiment of the double-joint coupling 10 claimed is shown schematically in a longitudinal sectional detail view in a further stage after the stage according to Figure 1 of the method 100 claimed. The intermediate shaft 30 is introduced through the hollow pinion shaft 20 so far that the coupling toothing 34 protrudes out of the hollow pinion shaft 20. The thrust ring 40 which is arranged in the region of the coupling toothing 34 on the intermediate shaft 30 projects at least partially beyond the mounting plane 29 on the mounting flange 26 along the axis of rotation 15. The thrust ring 40 has a circumferential groove 46 on the inner side 43 in which a sealing element 44 is accommodated which is elastically deformable in the radial direction, i.e. substantially perpendicular to the axis of rotation 15, and is therefore suitable for centring the thrust ring 40 on the intermediate shaft 30. The sealing element 44 on the inner surface 43 has already been positioned in this position in the first method step 110 when the thrust ring 30 is mounted to the intermediate shaft 40. Figure 2A third step 130 of the claimed method 100 is shown, in which two sealing elements 44 are mounted on the outer surface 41 of the thrust ring 40. The sealing elements 44 are each accommodated in a circumferential groove 46 on the outer surface 41 of the thrust ring 40. The fixing ring 45, which is also mounted there in the third step 130, is accommodated in an additional circumferential groove 46 between the sealing elements 44 on the outer surface 41. Due to the fixing ring 45, axial movement of the intermediate shaft 30 in the assembled state can be limited. The fixing ring 45 is configured to be supported on the hollow pinion shaft 20, by which the axial movement of the intermediate shaft 30, i.e. the axial movement along the axis of rotation 15, is limited. As Figure 2 is shown, in the unloaded state, the outer diameter 47 of the sealing elements 44 is greater than the inner diameter 34 of the hollow pinion shaft 20. The sealing elements 44 at the outer surface 41 of the thrust ring 40 are configured in an elastically deformable manner.

[0032] Figure 3 A first embodiment of the claimed double-joint coupling 10 is shown in a longitudinal cross-section in a phase of the claimed method 100 after the phase according to Figure 2 The first embodiment of the claimed double-joint coupling 10 is shown in a longitudinal cross-section in a phase of the claimed method 100 after the phase according to Figure 3 On the basis of the fact that the third step 130 is carried out, so that the sealing elements 44 and the fixing element 45 are arranged at the outer surface 41 of the thrust ring 40. Furthermore, in the third step 130, an axial force 39 is applied to the intermediate shaft 30 in order to press one of the sealing elements 44 into the hollow pinion shaft 20. In this case, the axial force 39 can be applied as a pressure to the first end 31 of the intermediate shaft 30 or as a tension to the second end 33 of the intermediate body 30. The thrust ring 40 is pressed by the coupling toothing 34, so that the sealing element 44 to be pressed in is compressed by the hollow pinion shaft 20, i.e. by its wall. The sealing element 44 is in a loaded state, in which the outer diameter 49 of the sealing element 44 is the same as the inner diameter 24 of the hollow pinion shaft 20, so that a sealing action is achieved, which prevents the working medium from escaping from the region of the coupling toothing into the hollow pinion shaft 20. The third step 130 of the claimed method 100 is thereby ended.

[0033] Figure 4 A first embodiment of the claimed double-joint coupling 10 is shown in a longitudinal cross-section in a phase of the claimed method 100 after the phase according to Figure 3 The first embodiment of the claimed double-joint coupling 10 is shown in a longitudinal cross-section in a phase of the claimed method 100 after the phase according to Figure 4In a fourth step 140, the carrier ring 50 is mounted on the hollow pinion shaft 20 in the region of the first end 31 of the intermediate shaft 30. The carrier ring 50 has an inner toothing 52 which is configured to mesh with the coupling toothing 34 on the intermediate shaft 30. The coupling toothing 34 is in the form of a helical toothing 36, such that during meshing into the inner toothing 52 when viewed along the rotational axis 15, the first articulation plane 11 lies within the carrier ring 50. In particular, the helical toothing 36 is adapted to perform the tilting movement 13 in the inner toothing 52. In order to bring about the meshing of the coupling toothing 34 with the inner toothing 52, an axial force 17 needs to be applied to the intermediate shaft 30 in the axial direction, i.e. along the rotational axis 15, thereby causing a positional movement 55 of the intermediate shaft 30. By forming the meshing, it is possible to transmit a torque 25 from the hollow pinion shaft 20 to the intermediate shaft 30. The transmission path of the torque 25 is illustrated by the arrow in the drawing. Figure 4 When the carrier ring 50 is fixed, the sealing element 44 on the thrust ring 40 facing the first end 31 of the intermediate shaft 30 is compressed by the carrier ring 50. As a result, there is also a seal between the thrust ring 40 and the carrier ring 50. With the execution of the fourth step 140, the double-joint coupling 10 is substantially installed, that is to say, it is adapted to transmit a torque 25 from the hollow pinion shaft 20 to the intermediate shaft 30. Thus, Figures 1 to 4 The method 100 illustrated has a small number of necessary steps 110, 120, 130, 140, which can be carried out quickly. The steps 110, 120, 130, 140 illustrated can easily be exchanged in order, thereby providing a complementary disassembly method.

[0034] Figure 5 A first embodiment of the double-joint coupling 10 claimed is illustrated in a longitudinal sectional view in the installed state. In this case, the carrier ring 50 is mounted to the hollow pinion shaft 20 using a fastener 56 configured as a screw. By means of the coupling toothing 34 which meshes with the inner toothing 52 of the carrier ring 50, it is ensured that a torque 35 is transmitted from the hollow pinion shaft 20 to the intermediate shaft 30.

[0035] Since the coupling toothing 34 is configured as a helical toothing 36, a first articulation plane 11 of the double-joint coupling 10 is achieved. A second articulation plane 12 is achieved by the flange-like flange 35 and the flange-like web connected thereto. An inclined movement 13 with respect to the first articulation plane 11 and the second articulation plane 12 at least partially defines a kinematic setup 85 of the double-joint coupling 10. The kinematic setup 85 is also influenced by the bending behavior of the flange-like web 48. Likewise, the kinematic setup 85 of the double-joint coupling 10 is influenced by the deformation behavior of its components, for example the torsional stiffness of the intermediate shaft 30 with respect to the rotational axis 15. Based on at least a portion of these data, the static and dynamic behavior of the double-joint coupling 10 can be mapped and simulated. The double-joint coupling 10 and its kinematic setup 85 are stored in the computer program product 80, so that a reaction 88 of the double-joint coupling 10 to a predetermined stress 86 can be established. Both the stress 86 and the reaction 88 can comprise forces and torques which can be determined in a time-resolved manner. For example, the stress 86 can be predetermined as an input of the computer program product 80 by which a driving operation of the rail vehicle 70, not shown in more detail, is mapped. Thus, the operating behavior of the double-joint coupling 10 can be simulated with the computer program product 80.

[0036] Figure 6 The structure of a second embodiment of the claimed double-joint coupling 10 is shown schematically in a longitudinal section. The double-joint coupling 10 has a hollow pinion shaft 20 through which an intermediate shaft 30 is introduced. The intermediate shaft 30 has a coupling toothing 34 in the form of a helical toothing 36 at a first end 31 facing a carrier ring 50 having an inner toothing 52. In this case, the coupling toothing 34 is configured integrally with the intermediate shaft 30. The carrier ring 50 is releasably connected to the hollow pinion shaft 20 by means of fastening elements 56 in the form of screws. An outer diameter 38 of the coupling toothing 34 is smaller than an inner diameter 24 of an inner space 21 of the hollow pinion shaft 20. The helical toothing 36 meshes with the inner toothing 52 and is configured in such a way that it can be inclined with respect to a rotational axis 15 of the double-joint coupling 10. A corresponding inclined movement 13 of the first end 31 of the intermediate shaft 30 defines a first articulation plane 11 of the double-joint coupling 10. Furthermore, a thrust ring 40 is arranged between the hollow pinion shaft 20 and the carrier ring 50, which thrust ring 40 is provided at its outer surface 41 and inner surface 43 with at least one recess 46 in which a sealing element 44 is accommodated. The thrust ring 40 is firmly clamped between the carrier ring 50 and the hollow pinion shaft 20 in the assembled state. Since the releasable connection between the carrier ring 50 and the hollow pinion shaft 20 and the meshing between the coupling toothing 34 at the first end 31 of the intermediate shaft 30 and the inner toothing 52, a torque 25 can be transmitted onto the intermediate shaft 30. The transmission of the torque 25 is indicated in Figure 6 ​

[0037] The intermediate shaft 30 is in the form of a hollow shaft and has a shaft portion 32 between a first end 31 and an opposite second end 33. At the second end 33 a coupling toothing 34 is configured, which meshes with an inner toothing 52 of an additional coupling part 57. Thereby at the second end 33 of the intermediate shaft 30 a tilting movement 13 is allowed, by which the second articulation plane 12 of the double-joint coupling 10 is realized. The tilting movement 13 at the first articulation plane 11 and the second articulation plane 12 belong to the kinematic setup 85 of the double-joint coupling 10, which can be simulated by the respective computer program product 80. Also deformations of the shown parts, for example a torsional behavior of the intermediate shaft 30, belong to the kinematic setup 85 of the double-joint coupling 10. According to Figure 6 The double-joint coupling 10 according to the application is described in the not more detailed computer program product 80. By inputting stresses 86 referring to forces and torques, the computer program product 80 is configured to simulate for example a driving behavior of the rail vehicle 70 and to simulate a reaction 88 of the double-joint coupling 10. In this case the reaction 88 can also include forces and torques.

[0038] Figure 7 The structure of an embodiment of the claimed rail vehicle 70 is schematically shown, which is driven on a track 79 by means of wheels 76. The rail vehicle 70 comprises a car body 71, on which a bogie 75 is fixed. The bogie 75 comprises a traction motor 72, which is connected to the double-joint coupling 10 to transmit a torque. The double-joint coupling is in turn connected to a gear mechanism 74 to transmit a torque, which is in turn connected via a shaft 77 to the wheels 76 to transmit a torque. The double-joint coupling 10 is configured according to one of the above described embodiments.

[0039] Furthermore, Figure 8 A schematic structure of an embodiment of the claimed industrial application 90 is shown, which comprises a drive unit 92, which is configured as an electric motor, a combustion engine or a hydraulic motor. The drive power, which is provided by the drive unit 92, is transmitted via an output shaft 93 to an output unit 94. The output unit 94 can be in the form of a mill, a vertical mill, a sugar mill, a cement mill, a rock crusher, a conveyor belt, a pump, a roller press, a plate belt conveyor, a drilling machine, a rotary furnace, a rotary mechanism, a mixer, a hoisting device, a milling machine or a scrap press, for example. For this purpose, the output unit 94 has an input shaft 97, which is connected by means of a coupling 96 to the output shaft 93 of the drive unit 92. The coupling 96 is in the form of the double-joint coupling 10 according to one of the above described embodiments.

Claims

1. A double jointed coupling (10) comprising a hollow pinion shaft (20) connected with an internal tooth structure (52) and an intermediate shaft (30) connected with a coupling tooth structure (34) to mesh in the internal tooth structure (52), characterized in that, The coupling toothing (34) is configured on the intermediate shaft (30) and has an outer diameter which is smaller than an inner diameter of the hollow pinion shaft (20) for being introduced through the hollow pinion shaft (20), wherein a thrust ring (40) configured to have an outer diameter which is smaller than an inner diameter of the hollow pinion shaft for being introduced through the hollow pinion shaft (20) is arranged on the intermediate shaft (30) in the region of the coupling toothing (34), wherein the thrust ring (40) has an outer surface (41) on which at least one sealing element (44) is arranged.

2. The double-joint coupling (10) according to claim 1, characterized in that The coupling toothing (34) is configured integrally with the intermediate shaft (30).

3. Double-joint coupling (10) according to claim 1 or 2, characterized in that A fixing ring (45) can be arranged on the outer surface (41) by which an axial movement of the intermediate shaft (30) can be supported, i.e. limited.

4. Double-joint coupling (10) according to claim 1 or 2, characterized in that The thrust ring (40) is configured to be fixed to the intermediate shaft (30) at an inner surface (43) by at least one sealing element (44).

5. Double-joint coupling (10) according to claim 1 or 2, characterized in that The thrust ring (40) is configured to be axially supported on the hollow pinion shaft (20).

6. The double-joint coupling (10) according to claim 1 or 2, characterized in that A carrier ring (50) is releasably connected to the hollow pinion shaft (20) or is configured integrally with the hollow pinion shaft (20).

7. Double-joint coupling (10) according to claim 1 or 2, characterized in that The intermediate shaft (30) is configured integrally with a sheet-like flange (35).

8. The double-joint coupling (10) according to claim 1 or 2, characterized in that The intermediate shaft (30) is in the form of a hollow shaft.

9. A method (100) for assembling a double-joint coupling (10) according to any one of claims 1 to 8, the double-joint coupling (10) having a carrier ring (50), the method comprising the following steps: a) providing the hollow pinion shaft (20), after which b) introducing the intermediate shaft (30) through the hollow pinion shaft (20); c) fitting at least one sealing element (44) and / or at least one fixing element to an outer surface (41) of the thrust ring (40); d) fixing a carrier ring (50) having an inner toothing (52) to the hollow pinion shaft (20) for engaging with the coupling toothing (34), characterized in that the thrust ring (40) is fitted to the intermediate shaft (30) in the step a).

10. A bogie (75) of a rail vehicle (70) comprising a traction motor (72) connected with a double-joint coupling (10) to transmit torque thereto, the double-joint coupling (10) being connected via a gear mechanism (74) to an axle (77) and / or a wheel (76) to transmit torque, characterized in that, The double-joint coupling (10) is configured as a double-joint coupling (10) according to any one of claims 1 to 8.

11. A rail vehicle (70) comprising a bogie (75) fixed to a car body (71), characterized in that, The bogie (75) is configured as a bogie (75) according to claim 10.

12. An industrial application device comprising a drive unit (92) connected via a coupling (96) with an output unit (94) to transmit torque, characterized in that, The coupling (96) is in the form of a double-joint coupling (10) according to any one of claims 1 to 8.

13. A computer program product (80) for simulating the operating behavior of a double-joint coupling (10) in a rail vehicle (70), characterized in that The double-joint coupling (10) is configured as a double-joint coupling (10) according to any one of claims 1 to 8.

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