Bracing arrangement for a drive train of a vehicle

Abstract

Tensioning arrangement for a drive train of a motor vehicle for pretensioning in the circumferential direction a plug connection between a transmission-side sub-unit, in particular a clutch unit (22), for example a double clutch, and an engine-side sub-unit, in particular a torsional vibration damper, for example a dual-mass flywheel (14), with a flange, in particular output flange (12) of the torsional vibration damper or input flange (20) of the clutch unit (22), wherein the flange (12, 20) has a profiling (16) for transmitting a torque in the circumferential direction to a counter-profile (18), a spring element (26) attached to the flange (12, 20) via a first end for providing a prestressing force in the circumferential direction from the flange (12, 20) to the counter profile (18) and a bracing plate (24) connected to a second end of the spring element (26), wherein the bracing plate (24) is supported on the counter-profile (18) essentially at the radial height of the profiling (16) of the flange (12, 20) in the circumferential direction via a fastening tab (28) which is bent over only axially and formed in one piece with the bracing plate (24).

Description

[0001] The invention relates to a tensioning arrangement for a drive train of a motor vehicle, with the aid of which a plug connection between a transmission-side sub-unit, for example a dual clutch, and an engine-side sub-unit, for example a dual-mass flywheel, can be pre-tensioned in the circumferential direction without play in order to avoid noise development during load changes.

[0002] WO 2007 / 000151 A2 discloses a bracing arrangement in which a dual-mass flywheel is connected to a dual clutch via a spline in a rotationally fixed but axially displaceable manner. An output flange of the dual-mass flywheel is connected to a corresponding counter-profile of an input flange of the dual clutch via a tooth-shaped profile. To prevent noise during load changes, the output flange of the dual-mass flywheel is coupled via a bow spring to a bracing plate. The bracing plate has a protruding U-shaped fastening tab whose open end can circumferentially engage a tooth of the tooth profile of the output flange.Due to the U-shaped design of the fastening tab, the axial position of the bracing plate relative to the output flange of the dual-mass flywheel can be defined, whereby at the same time the base of the U-shaped fastening tab can be pressed away from the encompassed tooth of the output flange by the arc spring with preload in order to compensate for any play in the circumferential direction.

[0003] There is a constant need to be able to provide alternative bracing arrangements for different drive trains in order to meet different installation space requirements.

[0004] The object of the invention is to provide an alternative bracing arrangement for a drive train of a motor vehicle. In particular, the object of the invention is to provide a bracing arrangement for a drive train of a motor vehicle that is easier to install and / or allows for a reduction in installation space in the axial direction.

[0005] The object is achieved according to the invention by a bracing arrangement having the features of claim 1 and by a bracing arrangement having the features of claim 2. Preferred embodiments of the invention are specified in the subclaims.

[0006] A bracing arrangement according to the invention for a drive train of a motor vehicle for preloading in the circumferential direction a plug-in connection between a transmission-side subunit, in particular a clutch unit, for example a dual clutch, and an engine-side subunit, in particular a torsional vibration damper, for example a dual-mass flywheel, has a flange, in particular an output flange of the torsional vibration damper or an input flange of the clutch unit, wherein the flange has a profile for transmitting a torque in the circumferential direction to a counter-profile. Additionally, a spring element fastened to the flange via a first end for providing a preload force in the circumferential direction from the flange to the counter-profile, and a bracing plate connected to a second end of the spring element are provided.According to the invention, the bracing plate is supported essentially at the radial height of the profiling of the flange in the circumferential direction via a fastening tab that only runs axially on the counter-profile.

[0007] Because the fastening tab only extends axially, kinking bends in the circumferential direction are avoided, eliminating the need to thread part of the flange's profile into the fastening tab, making the alternative bracing arrangement easier to install. This takes advantage of the knowledge that it is not absolutely necessary to provide axial positioning of the bracing plate with the flange in the area of ​​the profile. Instead, axial positioning can be achieved, for example, with the help of a spacer bolt guided in a corresponding curved groove in the flange, via which the bracing plate can be connected to the flange in a relatively twistable and captive manner in the circumferential direction.This means that any axial forces that occur can be dissipated over a large area between the flange and the bracing plate, eliminating the need to transmit the axial forces over small areas of a bent fastening tab. This reduces wear and prevents unwanted plastic deformation of the fastening tab under heavy loads. Furthermore, the installation space provided for the axial positioning of the bracing plate with the flange can be shifted radially outwards. Since the fastening tab only runs axially and has no further angled sections once it has reached an intermediate space formed in the counter-profiling, the fastening tab can be designed as an essentially two-dimensional body with a sheet thickness corresponding to the bracing plate. For example, the fastening tab can be designed as a radially projecting tooth of a spline.In particular, it is not necessary to twist the bracing plate against the maximum counterforce of the spring element, especially a straight compression spring, in order to insert the bracing plate together with the flange into the counter profile. It is even possible to use a spring element that is smaller in the circumferential direction and / or a spring element with a steeper spring characteristic without complicating installation. The bracing is primarily applied on the tension side, so that the spring element essentially only needs to cover the torques that occur during overrun of a connected internal combustion engine.

[0008] An alternative tensioning arrangement according to the invention for a drive train of a motor vehicle for pretensioning in the circumferential direction a plug connection between a clutch unit, in particular a dual clutch, and an engine-side sub-unit, in particular a torsional vibration damper, for example a dual-mass flywheel, has according to the invention a flange designed as an input flange of the clutch unit, wherein the flange has a profile for absorbing a torque introduced by a counter-profile.In addition, a spring element is provided which is fastened to the flange via a first end to provide a preload force in the circumferential direction from the flange to the counter-profile and a bracing plate is connected to a second end of the spring element, wherein the bracing plate has a fastening tab for indirect or direct support on a component having the counter-profile, in particular the output flange of the torsional vibration damper.

[0009] Since the bracing of the profiling for counter-profiling does not take place on the engine side, for example on the output flange of a dual-mass flywheel, but on the gearbox side, for example on the input flange of a clutch unit, the installation space required for this can be shifted to the area of ​​the gearbox-side sub-unit. In particular, it is possible to provide parts of the plug-in connection of the alternative bracing arrangement radially inside parts of the clutch unit, for example radially inside a pressure plate of the clutch unit, where unused installation space can be found. The axial installation space requirement can be reduced in this way. It is also possible to make the flange of the engine-side component, for example the output flange of the dual-mass flywheel, thinner, since it is not necessary to provide recesses for arranging and guiding the spring element in the area on the engine side for the plug-in gearing.Because the recesses are avoided, the same or even a greater bending moment can be transmitted with a smaller thickness. This reduces the axial space required. The bracing is primarily applied on the tensile side, so that the spring element essentially only needs to absorb moments occurring during overrun of a connected internal combustion engine. The bracing arrangement can be designed and developed, in particular, as described above.

[0010] The further developments of the invention explained below are applicable to all alternative bracing arrangements according to the invention.

[0011] In particular, the profiling and the counter-profile form a spline, wherein the counter-profile has circumferentially distributed tooth spaces for each receiving a corresponding internal tooth of the flange, wherein the fastening tab of the bracing plate protrudes into at least one tooth space, wherein only the fastening tab is arranged in the tooth space into which the fastening tab protrudes. The fastening tab can therefore replace an otherwise provided tooth of the flange. This utilizes the knowledge that by coupling the flange to the bracing plate with the aid of the spring element, clamping in the circumferential direction is ensured even if the tooth of the flange and the fastening tab are not located in the same tooth space.This makes it possible to increase the axial extension of the flange tooth and / or the fastening tab, in particular by extending it over the entire axial extension of the counter profile. This increases the contact surfaces on the counter profile, thus reducing the loads on the contact surfaces and / or reducing the axial extension of the spline.

[0012] Preferably, at least one fastening tab of the bracing plate protrudes into the counter-profile from a first axial side, and at least one further fastening tab of the bracing plate protrudes into the counter-profile from a second axial side facing away from the first axial side. This allows the forces acting on the fastening tabs to be evened out, so that tilting moments at the plug-in connection, particularly those caused by elastic deformation of the fastening tab, can be avoided.

[0013] Particularly preferably, the fastening tab is formed integrally with the bracing plate, wherein the fastening tab is bent in particular around a substantially tangential bending line and / or a substantially radial bending line. The fastening tab can be partially punched out during the manufacture of the bracing plate and subsequently formed by non-cutting forming. In particular, bending around exactly one bending line is sufficient to allow the fastening tab to extend in the axial direction over a significantly longer distance than the thickness of the bracing plate, even in the case of a sheet-like bracing plate with a comparatively small thickness.

[0014] In a preferred embodiment, the flange is arranged between a first bracing plate and a second bracing plate, wherein the first bracing plate and the second bracing plate are connected to one another in a rotationally fixed manner via spacer bolts and the flange can be rotated in the circumferential direction relative to the bracing plates. The at least one spacer bolt, preferably three spacer bolts, can each be arranged and in particular guided in an associated arcuate groove of the flange so that the flange can be rotated to a limited extent in the circumferential direction relative to the bracing plates. In particular, the flange forms stops in the circumferential direction for the respective spacer bolt so that excessive compression and / or expansion of the spring element can be avoided. Furthermore, the bracing plates can each form a flat contact surface for a respective axial direction in order to be able to absorb and dissipate axial forces of the flange.

[0015] In particular, the flange has a flange window and the bracing plate has a sheet metal window, with the spring element being arranged both in the flange window and in the sheet metal window. The spring element can, in particular, rest with one end against the flange window and with the other end against the sheet metal window, so that a coupling with a preload force between the flange and the bracing plate can be easily provided. It is not necessary to arrange the spring element axially outside the flange or the bracing plate, so that the axial space requirement can be reduced accordingly.

[0016] The bracing plate preferably has an axially projecting guide wing for guiding the spring element, wherein the guide wing extends in particular only over part of the extent of the spring element in the circumferential direction. The spring element, in particular a straight compression spring, can be guided radially inward and / or radially outward by the guide wing, so that the spring element does not inadvertently jam under load and / or is bent out of the flange window or the sheet metal window. Since the spring element is always preloaded, especially during operation, it is possible to provide the extension of the guide wing not over the entire extent of the sheet metal window in the circumferential direction, but for example to reduce the spring travel of the preload.This makes it easier to select a suitable structural design for the guide wings in order to design the guide wings in one piece with the bracing plate and to form them by partial punching and subsequent chipless bending from the material of the bracing plate.

[0017] Particularly preferably, the bracing plate has a guide bevel in the area of ​​the sheet metal window for guiding the spring element, corresponding to the outer contour of the spring element. This allows the spring element, in particular a straight compression spring, to be guided across the sheet metal thickness of the bracing plate. In particular, the radial extent of the sheet metal window is smaller than the radial extent of the spring element, so that the spring element can be securely held between two bracing plates even without a guide vane. The axial extent and the axial space requirement can thus be further reduced.

[0018] In particular, the flange and the bracing plate form a releasable locking device for locking the flange in the circumferential direction relative to the bracing plate in an assembly position. The locking device allows the flange and the bracing plate to be locked in a position relative to one another such that the unit consisting of the flange and bracing plate can be easily inserted into the counter profile with some clearance. The locking device can then be released, for example, by a locking tongue that abuts in the circumferential direction being plastically bent away or springing away in the axial direction due to residual stress in order to enable the intended relative movement in the circumferential direction. This can even occur during commissioning of the bracing arrangement due to the load changes that occur during normal operation.The locking device can be designed in particular as described in WO 2007 / 000151 A2, the content of which is hereby incorporated by reference as part of the invention.

[0019] The invention further relates to a clutch assembly, in particular a dual clutch, having a clamping arrangement as described above, wherein the flange of the clamping arrangement forms an input flange of the clutch assembly. In particular, the flange can be part of a clutch cover and / or part of a counterpressure plate of the clutch assembly.

[0020] The invention further relates to a torsional vibration damper, in particular a dual-mass flywheel, which has a bracing arrangement as described above, wherein the flange of the bracing arrangement forms an output flange of the torsional vibration damper.

[0021] The invention further relates to a drive train for a motor vehicle having an engine shaft, in particular a crankshaft, that can be connected to an internal combustion engine, and a transmission input shaft that can be connected to a motor vehicle transmission. The engine shaft can be coupled to the transmission input shaft via a bracing arrangement that can be designed and developed as described above. Preferably, the engine shaft is connected to a torsional vibration damper, in particular a dual-mass flywheel, and the transmission input shaft is connected to a clutch assembly, in particular a dual clutch. The torsional vibration damper is connected to the clutch assembly via the bracing arrangement in a rotationally fixed but axially displaceable manner.

[0022] The invention will be explained below by way of example with reference to the accompanying drawings using preferred embodiments. They show: Fig. 1: a schematic sectional view of a bracing arrangement according to the invention, Fig. 2: a schematic plan view of the bracing arrangement from Fig. 1, Fig. 3: a schematic sectional view of the bracing arrangement along the line YY from Fig. 2, Fig. 4: a schematic sectional view of the bracing arrangement along the line XX of Fig. 2, Fig. 5: a schematic perspective view of the bracing arrangement from Fig. 2, Fig. 6: a schematic perspective detailed view of the bracing arrangement from Fig. 5, Fig. 7: a schematic perspective view of an alternative bracing arrangement according to the invention, Fig. 8: a schematic perspective detailed view of the bracing arrangement from Fig. 7, Fig. 9: a schematic plan view of a detail of the bracing arrangement in a first embodiment, Fig. 10: a schematic sectional view of the bracing arrangement from Fig. 9, Fig. 11: a schematic plan view of a detail of the bracing arrangement in a second embodiment with the spring element relaxed, Fig. 12: a schematic plan view of a detail of the bracing arrangement from Fig. 11 with compressed spring element, Fig. 13: a schematic sectional view of the bracing arrangement from Fig. 11, Fig. 14: a schematic plan view of a detail of the bracing arrangement in a third embodiment, Fig. 15: a schematic sectional view of the bracing arrangement from Fig. 14, Fig. 16: a schematic plan view of a detail of the bracing arrangement in a fourth embodiment, Fig. 17: a schematic sectional view of the bracing arrangement from Fig. 16, Fig. 18: a schematic plan view of a detail of the bracing arrangement from Fig. 2, Fig. 19: a schematic sectional view of the bracing arrangement from Fig. 18, Fig. 20: a schematic plan view of the bracing arrangement from Fig. 2 in a locked relative position, Fig. 21: a schematic plan view of a detail of the bracing arrangement from Fig. 20, Fig. 22: a schematic plan view of the bracing arrangement from Fig. 2 in a tension-biased relative position, Fig. 23: a schematic plan view of a detail of the bracing arrangement from Fig. 22, Fig. 24: a schematic plan view of the bracing arrangement from Fig. 2 in a shear-side braced relative position, Fig. 25: a schematic plan view of a detail of the bracing arrangement from Fig. 24 and Fig. 26: a schematic sectional view of an alternative bracing arrangement according to the invention.

[0023] The Fig. 1, the partially illustrated bracing arrangement 10 comprises a flange formed by an output flange 12 of a dual-mass flywheel 14, which flange has a profile 16 radially on the inside. The profile 16 can be inserted, with play, in a rotationally fixed but axially displaceable manner into a corresponding counter-profile 18 of an input flange 20 of a clutch unit 22. The output flange 12 is arranged between two bracing plates 24 and, via a spring element 26 in the form of a compression spring, which can be, for example, curved or partially curved, but preferably straight, can be rotated to a limited extent in the circumferential direction with the bracing plates 24 against the spring force of the spring element 26.To compensate for the play between the profile 16 of the output flange 12 and the counter-profile 18, the respective bracing plate 24 has one or more fastening tabs 28, which are formed integrally with the bracing plate 24 and are essentially bent only axially. The spring force of the spring element 26 allows the counter-profile 18 to be clamped to the profile 16 and the fastening tab 28 without play, thus avoiding noise during load changes.

[0024] The dual-mass flywheel 14 has a primary flange 30 that can be connected to a motor shaft 29 (not shown), in particular the crankshaft, of an internal combustion engine of a motor vehicle. The primary flange 30 is coupled to a limited degree of rotation via an energy storage element in the form of a bow spring 32. A starter ring gear 36 is also connected to the primary flange 30 in order to start the internal combustion engine via the primary flange 30 with the aid of a starter.

[0025] As in Fig. 2, Fig. 3 and Fig. 4, the profiling 16 of the output flange 12 can be designed as a toothing in order to form a plug-in toothing with the counter-profile 18, which is also designed as a toothing. However, at regular intervals, a tooth of the profiling 16 is replaced by the fastening tab 28. For assembly of the bracing arrangement 10, the output flange 12 can be positioned with the preload provided by the spring elements 26 in a relative position to the bracing plate 24 with the aid of a locking device 36 such that the position of the fastening tabs would essentially correspond to the position of a tooth of the profiling 16 if the toothing of the profiling 16 were regular. As a result, the output flange 12, together with the bracing plate 24, can be plugged onto the counter-profile 18 with play. The locking of the locking device 36 can then be released in order to provide a preload in the circumferential direction to compensate for the play.

[0026] As in Fig. 3, the bracing plates 24 can be connected to each other at a defined distance via spacer bolts 38. The spacer bolts 38 can be guided in a curved groove 40 of the output flange 12 for limited rotation. As shown in Fig. As shown in Figure 4, the output flange 12 has a flange window 42 for receiving the spring element 26. Accordingly, the bracing plates 24 have a sheet metal window 44 for receiving the spring element 26. In the illustrated embodiment, a guide wing 46 for guiding the spring element 26 protrudes from the bracing plate 24 at the radially outer edge of the sheet metal window 44 in the axial direction.

[0027] As in Fig. 5 and Fig. 6, the fastening tab 28 can be formed by bending a radially inwardly projecting part of the bracing plate 24 around a substantially tangential bending line 48 substantially by 90°. As shown in Fig. 7 and Fig. As shown in Figure 8, the fastening tab 28 can alternatively be formed by bending a part of the bracing plate 24 that projects substantially in the circumferential direction or tangentially around a substantially radially extending bending line 48.

[0028] As in Fig. 9 and Fig. 10, the guide wing 46 can extend substantially over the entire extent of the sheet metal window 44 in the circumferential direction. As shown in Fig. 11, Fig. 12 and Fig. 13, the guide wing 46 can alternatively extend only in a partial area of ​​the extent of the sheet metal window 44 in the circumferential direction. This utilizes the knowledge that the spring element 26 is only completely relaxed in the unassembled state ( Fig. 11) and in the assembled state ( Fig. 12) is always slightly pre-tensioned. Therefore, the guide wing 46 can be shortened in the circumferential direction so that guidance is only provided in the assembled state with the spring element 26 compressed. As shown in Fig. 14 and Fig. 15, the guide vanes can even be omitted to save axial space. In this case, in particular, as shown in Fig. 16 and Fig. 17, the bracing plate 24 can have a guide bevel 50 corresponding to the outer contour of the spring element 26 in order to be able to guide the spring element 26 even without guide wings 46, wherein the guide bevel 50 can be provided radially outside and / or radially inside on the sheet metal window 44.

[0029] As in Fig. 18 and Fig. As shown in Figure 19, the locking device 36 can have a locking tongue 52, which is formed integrally with the bracing plate 24 and abuts in the circumferential direction against a boundary wall 54 of a locking opening 56 provided in the output flange 12. A corresponding holding force in the circumferential direction can be provided by the prestressed spring element 26. It is also possible for the locking tongue 52 to be formed by the output flange 12 and the locking opening 56 by the bracing plate 24.

[0030] In Fig. 20 and Fig. In the locked state of the bracing arrangement 10 shown in Figure 21, the profile 16 and the fastening tab 28 are inserted with play in the counter-profile 18. In this state, the locking tongue 52 is bent into the locking opening 56. In the Fig. 22 and Fig. 23, the locking device 36 is released by the locking tongue 52 being moved out of the locking opening 56 and being arranged substantially parallel to the output flange 12. In the pulling operation, due to the preload of the spring element 26, the fastening tab 28 and the profile 16 rest against the counter profile 18 in different circumferential directions, so that any previously existing play is eliminated. Fig. 24 and Fig. 25, the profiling 16 and the fastening tab 28 can rest on the counter-profile 18 in the same circumferential directions.

[0031] At the Fig. The embodiment of the bracing arrangement 10 shown in Figure 26 is compared to the one shown in Fig. 1, the flange of the tensioning arrangement 10 is not formed by the output flange 12 of the dual-mass flywheel 14 but by an input flange 20 designed as a drive plate of a clutch unit 22 designed as a double clutch. In the direction of force flow, the plug connection formed by the profiling 16 and counter-profile 18 is therefore located in front of the spring element 26 of the tensioning device 10, while in the Fig. In the embodiment of the tensioning device 10 shown in Figure 1, the order is reversed. List of reference symbols 10 Bracing arrangement 12 Output flange 14 Dual-mass flywheel 16 Profiling 18 Counter profile 20 input flange 22 Clutch unit 24 bracing plate 26 spring element 28 Mounting tab 29 Motor shaft 30 Primary flange 32 bow spring 34 starter wreath 36 locking device 38 spacer bolts 40 curved groove 42 flange windows 44 sheet metal windows 46 guide wings 48 Bending line 50 guide bevel 52 locking tongue 54 boundary wall 56 locking opening

Claims

[1] Tensioning arrangement for a drive train of a motor vehicle for pretensioning in the circumferential direction a plug connection between a transmission-side sub-unit, in particular a clutch unit (22), for example a double clutch, and an engine-side sub-unit, in particular a torsional vibration damper, for example a dual-mass flywheel (14), with a flange, in particular output flange (12) of the torsional vibration damper or input flange (20) of the clutch unit (22), wherein the flange (12, 20) has a profiling (16) for transmitting a torque in the circumferential direction to a counter-profile (18), a spring element (26) attached to the flange (12, 20) via a first end for providing a prestressing force in the circumferential direction from the flange (12, 20) to the counter profile (18) and a bracing plate (24) connected to a second end of the spring element (26), wherein the bracing plate (24) is supported on the counter-profile (18) essentially at the radial height of the profiling (16) of the flange (12, 20) in the circumferential direction via a fastening tab (28) which is bent over only axially and formed in one piece with the bracing plate (24). [2] Tensioning arrangement for a drive train of a motor vehicle for pretensioning in the circumferential direction a plug connection between a clutch unit (22), in particular a double clutch, and an engine-side sub-unit, in particular a torsional vibration damper, for example a dual-mass flywheel (14), with a flange designed as an input flange (20) of the clutch unit (22), the flange having a profile (16) for absorbing a torque introduced by a counter-profile (18), a spring element (26) attached to the flange via a first end for providing a prestressing force in the circumferential direction from the flange to the counter profile (18) and a bracing plate (24) connected to a second end of the spring element (26), wherein the bracing plate (24) has a fastening tab (28) for indirect or direct support on a component having the counter-profile (18), in particular the output flange (12) of the torsional vibration damper. [3] Bracing arrangement according to claim 1 or 2 characterized byin that the profiling (16) and the counter-profile (18) form a spline, wherein the counter-profile (18) has circumferentially distributed tooth spaces for receiving a corresponding internal tooth of the flange (12, 20), wherein the fastening tab (28) of the bracing plate (24) projects into at least one tooth space, wherein only the fastening tab (28) is arranged in the tooth space into which the fastening tab (24) projects. [4] Bracing arrangement according to one of claims 1 to 3 characterized by that at least one fastening tab (28) of the bracing plate (24) projects into the counter-profile (18) from a first axial side and at least one further fastening tab (28) of the bracing plate (24) projects into the counter-profile (18) from a second axial side facing away from the first axial side. [5] Bracing arrangement according to one of claims 1 to 4 characterized bythat the fastening tab (28) is designed in one piece with the bracing plate (24), wherein the fastening tab (28) is bent in particular around a substantially tangential bending line (48) and / or a substantially radial bending line (48). [6] Bracing arrangement according to one of claims 1 to 5 characterized by in that the flange (12, 20) is arranged between a first bracing plate (24) and a second bracing plate (24), wherein the first bracing plate (24) and the second bracing plate (24) are connected to one another in a rotationally fixed manner via spacer bolts (38) and the flange (12, 20) is rotatable in the circumferential direction relative to the bracing plates (24). [7] Bracing arrangement according to one of claims 1 to 6 characterized bythat the flange (12, 20) has a flange window (42) and the bracing plate (24) has a sheet metal window (44), wherein the spring element (26) is arranged both in the flange window (42) and in the sheet metal window (44). [8] Bracing arrangement according to claim 7 characterized by that the bracing plate (24) has an axially projecting guide wing (46) for guiding the spring element (26), wherein the guide wing (46) extends in particular only over a part of the extent of the spring element (26) in the circumferential direction. [9] Bracing arrangement according to claim 7 or 8 characterized by that the bracing plate (24) in the region of the sheet metal window (44) has a guide bevel (50) corresponding to the outer contour of the spring element (26) for guiding the spring element (26). [10] Bracing arrangement according to one of claims 1 to 9 characterized bythat the flange (12, 20) and the bracing plate (24) form a releasable locking device (36) for locking the flange (12, 20) in the circumferential direction relative to the bracing plate (24) in an assembly position.

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