DRIVER FOR ATTACHING A MULTI-PEARL ARRANGEMENT FOR A BICYCLE GEARBOX WITH SMALL PEARLS

Description

[0001] The present invention relates to a multiple pinion arrangement having a plurality of pinions with different numbers of teeth for mounting on a rear wheel axle of a bicycle. In particular, the present invention relates to a multiple pinion arrangement comprising a pinion assembly on which at least some of the plurality of pinions are provided, wherein the driver is connected or connectable to the pinion assembly in a torque-transmitting manner, and an adapter that can be coupled to the driver. The pinion assembly can also comprise pinions that have a smaller inner diameter or root circle than the outer diameter of the driver, and wherein the pinion assembly can be connected to the driver via the adapter in the region of the smaller-diameter pinions. The invention further relates to a rear wheel axle arrangement for a bicycle.

[0002] Various systems for attaching multiple pinion assemblies for bicycle gearshifts to rear wheel axles are known in the prior art. In one widely used system, a driver is rotatably mounted on the rear wheel axle of a bicycle via a bearing arrangement. The driver is in torque-transmitting engagement with the hub shell via a one-way clutch and allows torque transmission in one direction of rotation (drive direction), while being rotationally decoupled from the hub shell in the other direction to provide freewheeling. Such a driver is typically provided with a spline or a similar profile on its outer circumferential surface in order to be able to attach individual pinions or an assembly consisting of several pinions in a torque-transmitting manner. One such solution is shown, for example, in the prior art in document DE 199 15 436 A1.Comparable solutions are also shown in the documents JP 59-165293, GB 2 177 628 A or EP 0 277 576 A2.

[0003] A widely used solution is described in document EP 1 342 657 B1.

[0004] This document is considered to be the closest prior art to the subject matter of claim 1, since it shows the preamble of claim 1. It also shows a possibility for attaching smaller diameter pinions to a relatively solid driver.

[0005] Although this system is widespread, it is increasingly reaching its limits and has considerable disadvantages. For example, the number of sprockets in highly developed bicycle gears, as is now used both in professional cycling and by recreational athletes, is increasing. In some cases, relatively large increments are used, but in particular relatively close increments are also used, for example to enable optimal gear ratios when riding on flat terrain or when riding in a group with a constant cadence. In both cases, i.e. when close increments with small gear ratio steps are required, or when large gear ratio steps are to be provided, there is a growing demand for very small sprockets, i.e. sprockets with 10 teeth or fewer.However, such small pinions can no longer be mounted on a conventional driver, necessitating auxiliary structures that usually require additional parts and are therefore complex and difficult to install. Particularly for the smaller-diameter pinions, relatively complex drive profiles are required. Overall, the adapter solution presented in this state-of-the-art design presents the problem of requiring a multitude of different parts that are complicated to install and relatively heavy.

[0006] A further disadvantage of this prior art solution is that, precisely because of the multi-part design, the outer bearing must be positioned further axially inside the driver. This means that, especially when the chain rests on the smallest pinion, there is a relatively large axial distance between the point of chain engagement, and thus the point of power transmission, and the bearing. This leads to undesirable mechanical stresses and an unfavorable power flow.

[0007] It is an object of the present invention to provide a multiple pinion arrangement of the type described at the outset, as well as a rear wheel axle arrangement formed therewith, which take into account the problems described above and which can be designed with a considerably simplified structure and a significantly reduced weight.

[0008] This object is achieved by a multiple pinion arrangement having the features of claim 1.

[0009] In contrast to the prior art, in which all pinions generally engage the driver directly or indirectly via a corresponding external toothing profile, it was recognized that the entire driver does not have to be provided with corresponding external toothing, but that sections on the outer side of the driver can also be used to at least axially fix the adapter for attaching the pinion assembly. The torque transmission between the pinion assembly and driver can also take place spatially separate from the coupling section. The adapter preferably serves solely to fix the pinion assembly in the axial and radial directions. This has the advantage that the sections of the pinion assembly used for torque transmission can be specifically designed for this purpose, and the sections used for axial and radial fixation via the adapter can be adapted accordingly to the requirements of the axial fixation.

[0010] Furthermore, the adaptability for the use of different pinion assemblies increases through the respective adaptation of the adapter. A corresponding pinion assembly only needs to be equipped with the appropriate torque transmission section and can then be axially fixed with an adapter matched to the pinion assembly. The adapter engages the designated areas of the driver. This allows the use of pinion assemblies with very small pinions, which cannot be combined with conventional drivers at all or only with considerable technical effort.

[0011] In particular, a driver for mounting on a rear wheel axle of a bicycle can be designed as follows, wherein the driver is designed to attach the pinion assembly on which a plurality of pinions with different numbers of teeth are provided, wherein the driver comprises: a torque receiving formation for torque-transmitting coupling with the pinion assembly, a positioning section for positioning the pinion assembly in the radial direction, an external thread formation onto which an adapter for axially fixing the pinion assembly can be screwed, and an output formation for transmitting a torque to a hub assembly of a rear wheel axle of a bicycle, wherein the external thread formation extends between the torque absorption formation and the positioning section.

[0012] This design offers many advantages, in particular a compact design with simple manufacturing and low weight.

[0013] A further development provides a guide section arranged between the torque absorption formation and the positioning section, preferably adjacent to the external thread formation. The guide section does not have to transmit any forces or moments, nor any tensile stresses, and can therefore be designed with a relatively thin wall and thus be lightweight. An advantage of this design is that the guide section enables reliable and error-free assembly of the adapter on the driver. The guide section guides the adapter during screwing on the external thread formation and prevents the adapter from being tilted and screwed on incorrectly, which could potentially damage or destroy the external thread formation or the corresponding internal thread formation assigned to the adapter.

[0014] The external thread formation can be arranged close to the torque absorption formation, so that the areas where moments and tensile stresses occur are locally concentrated, allowing the driver to be made correspondingly solid in these mechanically stressed areas. The remaining, less heavily stressed areas can be made correspondingly lighter.

[0015] A further development of the driver provides an axial stop for the pinion assembly, which is arranged adjacent to the torque absorption formation. Again, this stop, which serves to transmit force, can also be arranged in close proximity to the external thread formation and the torque absorption formation, so that the resulting forces and moments can be concentrated locally.

[0016] With regard to the goal of achieving a particularly compact design, a further development of the driver provides that the torque absorption formation extends only over a partial section of the axial length of the driver between the axial stop and the free end of the positioning section, preferably over a partial section that is less than a quarter, particularly preferably less than a fifth of this axial length of the driver. It has been shown that the torque absorption formation, which serves as a torque-transmitting driving profile for the pinion arrangement, does not have to extend over the entire or a large part of the length of the driver, but that it is sufficient for the torque transmission to take place in a correspondingly solid, small axial region.In this context, it can be provided that the partial section essentially corresponds to the axial length of the corresponding torque transmission formation of the pinion assembly.

[0017] A further development of the driver provides for the external thread formation to be directly adjacent to the torque absorption formation. This allows axial forces occurring between the stop and the external thread formation used for clamping with the adapter to be concentrated on a relatively short axial section, rather than being transmitted over a longer axial section. Furthermore, this arrangement of the external thread formation offers the advantage that bearing surfaces or sections in which bearings must be accommodated do not axially overlap with the external thread formation. They therefore remain unaffected by the external thread formation.

[0018] A further development of the driver provides for the guide section to be formed by a substantially cylindrical or slightly conical outer surface, either closed or provided with openings for weight reduction. The design of the driver thus allows the guide section to be specifically designed for its task of guiding the adapter during its assembly, thus preventing faulty assembly that could, for example, damage the external thread formation on the driver or the corresponding thread formation on the adapter. Overall, the use of the guide section allows for optimal positioning of the pinion assembly on the driver.

[0019] In this context, it can further be provided that the guide section has a smaller maximum outer diameter than the torque absorption formation and the external thread formation. Furthermore, it can be provided that the positioning section is provided at an end remote from the torque absorption formation and is designed with a smaller outer diameter than the outer diameter of the guide section. Such a guide section with a reduced outer diameter offers the advantage that even very small pinions can be provided on the multiple pinion arrangement, which is often problematic with conventional drivers. It is possible for the guide section with a reduced outer diameter to be designed to accommodate a bearing.In order to make it possible to accommodate larger bearings to absorb larger loads, a further development provides for an enlarged inner diameter section to be formed at an end remote from the torque absorption formation.

[0020] A particular embodiment provides that the positioning section comprises a partial section of the outer circumferential surface of the bearing that projects axially from the driver or is formed by the driver. In other words, it can be provided that the driver is formed, at its end remote from the torque absorption formation, with an inner diameter section for receiving the bearing. This inner diameter section is designed so large that, compared to other embodiments, a positioning section integrally formed on the driver is completely eliminated. The bearing, which is partially received in the driver and partially projects axially therefrom, forms a projecting section with its outer bearing shell, which is then used as a positioning section.This has the advantage that the precisely manufactured outer surface of the outer bearing shell of the bearing, which partially protrudes from the driver, can be used as a geometrically precisely designed positioning section.

[0021] With regard to the bearing arrangement, it can further be provided that the driver is formed at its end near the torque absorption formation with an inner diameter section for receiving a bearing.

[0022] A further development provides that the pinion assembly can be pre-assembled as a coherent assembly and can be clamped to the driver via the adapter, wherein the adapter is formed with the first coupling section, via which it can be attached to the driver, and is formed with a second coupling section, with which it is coupled or can be coupled to the pre-assembled pinion assembly.

[0023] In contrast to the state of the art, this further development has the significant advantage that the pinion assembly can be pre-assembled as a coherent unit, making it easier to handle as a whole during assembly. This also makes the adapter considerably simpler. The adapter can then be designed in such a way that it does not have to accommodate and support individual pinions or a sub-assembly of individual pinions. Instead, the adapter is constructed in such a way that it only ensures the function of primarily axially (and possibly also radially) fixing the pinion assembly to the driver. Since the pinion assembly is self-supporting, it does not need to be additionally supported relative to the driver via the adapter, as is the case with state-of-the-art systems that require the assembly and fixing of individual pinions or pinion groups.It is understood that advantageously drivers specifically adapted to the adapter (as described above) are preferred over conventional drivers.

[0024] The torque transmission from the pinion assembly to the driver can also be designed much more simply than is the case with a multi-part solution with some individual pinions. The adapter can therefore be functionally designed precisely for the singular function of positioning and fixing the pinion assembly in the axial and radial directions relative to the driver, which allows for weight optimization. For example, the adapter or components assigned to it can be provided with fitting surfaces that position the pinion assembly in a defined position relative to the driver in the axial and / or radial directions. Conicities can also be formed on the adapter to ensure centering and clamping when the adapter is tightened. The torque transmission between the pinion assembly and the driver can take place at a different location on the pinion assembly, independent of the adapter.

[0025] In particular, it can be provided that the adapter is formed in the region of its first coupling section and / or in the region of its second coupling section with a fitting surface for radial and / or axial positioning relative to the pinion assembly and the driver. It is possible for the fitting surface to be formed by a plastic body attached to the adapter, for example on the plastic ring. The plastic ring can be injection-molded onto the adapter. In this context, it can further be provided that the adapter is provided with local openings, with the plastic mass extending through these local openings. This variant ensures reliable fixing of the plastic body to the adapter and ensures that a corresponding plastic ring with suitable fitting surfaces can be formed on both sides of the adapter, i.e. on the inner circumferential surface and on the outer circumferential surface.

[0026] Various functions, such as those performed in the prior art according to EP 1 342 657 B1 by the adapter or by complex intermediate pinions mounted on it, namely the positioning and torque-transmitting support of individual pinions of smaller diameter, are eliminated in the present invention. Overall, the result is a significantly simplified system that is significantly optimized in terms of weight savings.

[0027] One design variant provides for the adapter to be designed in the form of a stepped tubular sleeve with a first diameter section having a first outer diameter and a second diameter section having a second outer diameter that is smaller than the first outer diameter. The first diameter section is matched to the diameter of the driver, and the second diameter section is matched to the smaller diameter areas of the pinion assembly. This avoids the need for a massive, heavy adapter design.

[0028] In this embodiment, it is preferably provided that the first coupling section of the adapter is formed on its first diameter section. It is possible for the first coupling section to be designed in the form of a thread formation, preferably an internal thread formation, which can be brought into engagement with a corresponding mating thread formation on the driver. The adapter can thus be screwed onto the driver via corresponding thread formations. This allows for simple assembly with a reliable, permanent hold.

[0029] In this context, it can further be provided that the driver and the adapter each have a contact surface which, when mutually abutting in the assembled state, defines a predetermined relative position in the axial direction and / or in the radial direction (centering) between the driver and the adapter.

[0030] Furthermore, in this embodiment, it can be provided that the second coupling section is designed in the form of a thread formation, preferably an external thread formation, via which the multiple pinion arrangement can be clamped to the adapter. The clamping can be achieved, for example, via an additional nut that can be screwed onto the external thread formation on the second coupling section of the adapter and engages the pinion assembly for axial positioning and clamping. It can be provided that the second coupling section is arranged on the second diameter section of the adapter.

[0031] As an alternative to a screw connection between the adapter and the pinion assembly, it is also possible to assign the adapter directly to the pinion assembly, for example by attaching it to it by frictional or positive locking. In this context, a preferred embodiment provides that the second coupling section is designed in the form of at least one retaining projection that can be brought into engagement with a corresponding retaining formation on the pinion assembly. The adapter is therefore attached to the pinion assembly by a type of locking mechanism. The interaction between the retaining projection and the retaining formation can be achieved via an undercut. This embodiment has several advantages. Firstly, the pinion assembly no longer needs to be axially clamped to the smallest pinion with an additional nut.It should be noted that, with the current state of the art, relatively high contact forces can act on the smallest pinion during axial clamping, which is why the entire pinion assembly or parts thereof must be relatively solid and thus heavy. The interaction between the retaining projection and the retaining formation via an undercut allows for better dimensioning of the pinion assembly and, in particular, only needs to be designed for stability where the clamping forces actually act, i.e., in the area of ​​the retaining formation.

[0032] In this context, it can be provided that the retaining projection is arranged at an axial end of the adapter, wherein the adapter is axially slotted multiple times at this axial end to form locking tabs. This makes it possible to insert the adapter into the pinion assembly and lock it there, wherein during locking, the locking tabs can elastically spring radially inward due to the axial slot and then engage behind the holding formation in a locking manner. In other words, it can be provided that the locking tabs are designed to lock into the holding formation. The locking can be assisted by providing the holding tabs with chamfers to create corresponding run-in slopes.

[0033] To facilitate assembly of the adapter, a further development provides for it to have an engagement formation designed to transmit torque for assembly purposes. In this context, the engagement formation can be provided directly on the adapter or on a mounting ring that can be coupled to the adapter in a torque-transmitting manner. According to the first alternative, radial toothing, spur toothing, or another mechanical engagement profile can be formed directly on the adapter. In both cases, an assembly tool can be brought into engagement with the respective engagement formation.

[0034] In the case of a separate mounting ring, it can be provided with radial projections that engage in the axial slots between the locking tabs, transmitting torque. The mounting ring is thus coupled to the adapter in a torque-transmitting manner.

[0035] With regard to the mounting ring, it is also possible for it to be provided with contact surfaces for radially and / or axially positioning the pinion assembly relative to the driver. In contrast to the previously described embodiments, the radial and / or axial positioning of the pinion assembly can also be fully or partially handled by the mounting ring.

[0036] A further development provides for the pinion assembly to be provided with a support ring, which is coupled to the driver for torque transmission between the pinion assembly and the driver. This support ring can be made particularly solid to meet the requirements of torque transmission to the driver. The rest of the pinion assembly can then be made correspondingly lighter. One or more final pinions can then be formed or attached to the support ring.

[0037] A tubular clamping element can also be provided, designed as an axial stop between the support ring of the pinion assembly and the adapter and / or the pinion assembly. In certain embodiments, this tubular clamping element serves as an axial stop for the adapter or for the pinion assembly during clamping with the driver. This can prevent the pinion assembly itself from being excessively clamped and undesirably deformed.

[0038] According to an alternative embodiment, which can be combined with the possibilities for further development described above, it can further be provided that the adapter encompasses at least one bearing accommodated in the driver. The bearing can also be inserted into the adapter, with the adapter then being screwed into the driver with an external thread or onto it with an internal thread.

[0039] Furthermore, the adapter as such can be designed for attaching a pinion assembly to the driver of a multiple pinion arrangement according to the above description, wherein the adapter is designed with a first coupling portion, via which it can be attached to the driver, and with a second coupling portion, with which it is or can be coupled to the pinion assembly. The adapter can have individual, combinations, or all of the adapter-specific features explained above. In particular, it is possible for the second coupling portion to be formed on a multiply axially slotted end of the adapter. Furthermore, as already explained above, it is possible for the adapter to have an engagement formation or to be coupled in a torque-transmitting manner to an engagement formation designed for the torque-transmitting attachment of an assembly tool.

[0040] Finally, the invention relates to a rear wheel axle assembly for a bicycle having a rear wheel axle configured for attachment to a bicycle frame, a hub body rotatably mounted on the rear axle, a driver, a multiple pinion assembly of the type described above cooperating with a drive chain, and a torque transmission assembly, for example a freewheel, for directionally selectively transmitting a torque from the multiple pinion assembly to the hub body to drive the hub body, wherein the multiple pinion assembly is rotatably mounted on the rear wheel axle.

[0041] The invention is explained below by way of example with reference to the accompanying figures. They depict: Fig. 1 shows an axle-containing sectional view of a first embodiment of a rear wheel axle assembly according to the invention with a multiple pinion assembly according to the invention; Fig. 2 shows a corresponding sectional view of the adapter; Fig. 3 shows a corresponding axle-containing sectional view of the driver; Fig. 4 shows a spatial view of the driver in an individual part representation; Fig. 5 shows an axle-containing sectional view of a second embodiment of the rear wheel axle assembly according to the invention with a multiple pinion assembly according to the invention; Fig. 6 shows a corresponding axle-containing sectional view of the adapter of the second embodiment; Fig. 7 shows a spatial view of the adapter of the second embodiment; Fig. 8 shows a corresponding axle-containing sectional view of the driver of the second embodiment; Fig. 9 shows a spatial view of the driver of the second embodiment in an individual part representation; Fig.10 shows a partial sectional view, including the axle, of a third embodiment of the rear wheel axle arrangement according to the invention, with a multiple pinion arrangement according to the invention; Fig. 11 shows a corresponding sectional view, including the axle, of the adapter of the third embodiment; Fig. 12 shows a corresponding sectional view, including the axle, of a mounting ring of the third embodiment; Fig. 13 shows a front view of the mounting ring of the third embodiment; Fig. 14 shows a sectional view, including the axle, of the driver of the third embodiment; and Fig. 15 shows an embodiment of the invention with an advantageously designed driver; Figs. 16 and 17 show various representations of the driver; Fig. 18 shows an alternative design of the driver according to. Fig. 17for accommodating a larger bearing; Fig. 19 a partial sectional view of a further embodiment of the invention with an advantageously designed adapter; Fig. 20 an axis-containing sectional view of the adapter as a blank; Figs. 21 and 22 various sectional views of the adapter in different sectional planes and

[0042] Fig. 23 a cutaway perspective view of the adapter. In Fig. 1A multiple pinion arrangement according to the invention is shown in a section including the axis and is generally designated 10. This comprises a pinion assembly 12 on which several pinions 14 1 to 14 10 with different diameters and different numbers of teeth are formed. The pinion assembly 12 is formed in one piece or as a coherent assembly that can be handled as a single component during assembly. Even though the pinion assembly 12 itself may consist of several individual parts, these are firmly connected after assembly and form a self-supporting unit, so to speak.

[0043] The pinion assembly 12 is mounted on a driver 16, which in the individual part view is shown in the Figures 3 and 4is shown. This driver 16 can be attached in a manner known per se to a rear wheel axle (not shown) of a bicycle. In an area 18, an arrangement for transmitting the torque from the driver 16 or the pinion assembly 12 to a freewheel device and from this to a hub body (both not shown) of a rear wheel axle assembly can be attached. The driver 16 can be designed in a conventional manner and, in particular, have provisions to be compatible with already known, conventional systems widely available on the market. In particular, the driver 16 has external teeth 17 for receiving the pinion assembly 12 in a torque-transmitting manner. Furthermore, the driver 16 has an annular radial projection 19 which, together with an axial stop surface 21, serves for the axial positioning of the pinion assembly 12.

[0044] At his in Figure 1At its right end, the driver 16 is provided with a section 20 with a reduced outer diameter. This section has an external thread formation 22 which ends in a shoulder 24 with an outer circumferential surface 25 designed as a fitting surface. A sleeve-shaped adapter 26 is screwed onto this section 20 with its reduced outer diameter in the assembled state. The adapter 26 is shown in section in the individual part view in Figure 2 is shown. For this purpose, the adapter 26 has a first section 28 with a large diameter, on which an internal thread formation 30 is formed. This internal thread formation 30 is followed by an inner circumferential surface 29, which is designed as a fitting surface and, together with the corresponding fitting surface 25 on the driver 16, is designed for the radial positioning of the adapter 26 relative to the driver 16.

[0045] The first section 28 ends in an end face 32 which is in the Figure 1In the assembled state shown, it is in defined contact with the shoulder 24 and thus determines the axial position of the adapter 26 relative to the driver 16. The adapter 26 further has a second section 34 which has a smaller diameter than the first section 28. The two sections 28 and 34 are connected to one another via a transition section 36.

[0046] An external thread formation 38 is provided on the smaller diameter section 34. In the assembled state, this is Figure 1A clamping nut 40 is screwed on. The clamping nut 40 has several recesses 42 on its outer circumferential surface, which a tool can engage to exert a torque on the clamping nut 40 during assembly. The clamping nut 40 bears with a lateral contact surface 44 against an axial end surface 46 of the pinion assembly 12 facing it. By tightening the clamping nut 40, the pinion assembly 12 can be positioned and clamped in the axial direction.

[0047] In Figure 1One can also see a tubular element 50, which is axially supported at one end 52 on a support ring 54 of the pinion assembly 12 and at another end 56 within the pinion assembly 12 on one of the smaller pinions, namely the pinion 14 2 . The force flow in the axial direction applied by tightening the nut 40 thus extends via the two small pinions 14 1 and 14 2 , the tubular element 50 to the support ring 54 and from there to the driver 16.

[0048] It should be noted that the pinion assembly 12 consists of the separate support ring 54, on which the largest pinion 14 10 is integrally formed, and a subassembly of the remaining pinions 14 1 to 14 9 , as well as the tubular element 50, which is inserted before the support ring 54 is attached. As already explained, the support ring 54 is firmly connected to the subassembly of the remaining pinions 14 1 to 14 9 , for example, by pressing, riveting, gluing, or the like. The support ring 54 has an internal toothing as a torque transmission section, which corresponds to the external toothing 17 of the driver 16, and serves to transmit torque between the pinion assembly 12 and the driver 16.

[0049] Finally, Figure 1also the bearing 55, which is arranged in the driver 16 in a bearing recess designed for this purpose with a fitting surface 57 and is provided for mounting the driver 16 on the rear wheel axle, not shown.

[0050] The assembly of the entire system is relatively simple. The driver 16 is fitted with the Figure 1 The adapter 26 shown is screwed on and secured. The pinion assembly 12 is then placed on the driver 16. Finally, the clamping nut 40 is screwed on and tightened until the tubular element 50 serves as a defined stop, so to speak.

[0051] Overall, this results in a system that is considerably simplified compared to the state of the art and can be designed much more easily than, for example, the complex multi-part system according to the closest state of the art.

[0052] However, this system can be combined with existing driver solutions that have been in use for a long time, so that pinion assemblies with pinions with a very low number of teeth can also be mounted on such drivers in accordance with the state of the art.

[0053] Figures 5 to 9 show a second embodiment. To avoid repetition, the same reference numerals are used for components of the same type or with the same function as in the first embodiment. The following will only discuss the differences from the first embodiment.

[0054] Again, it can be seen that an external thread formation 22 is attached to the driver 16. This external thread formation 22 is followed by a thread-free section 20. The adapter 26 is in turn provided with a section 28 on which an internal thread formation 38 is provided. Unlike the first embodiment according to Figure 1the adapter 26 is supported with its end face 32 in the axial direction not on the driver 16, but on the tubular element 50 (see Figure 5 ).

[0055] Another difference between the first embodiment according to Figure 1 and the second embodiment according to Figure 2lies in how the adapter 26 is coupled to the pinion assembly 12. The adapter 26 has a section 60 with an enlarged diameter, an outer circumferential surface 61 for radial positioning, and a shoulder-like contact surface 62. This section 60 engages in a radial recess 64 in the pinion assembly 12, which forms a kind of undercut. The contact surface 62 rests against a corresponding counter-contact surface 66 and ensures that the pinion assembly 12 cannot slip over the contact surface 62 in the assembled state in the axial direction. This is where the clamping forces act when the pinion assembly 12 is clamped to the driver. This is better for the power flow than the state of the art, in which the pinion assembly is clamped onto the driver at the smallest pinion with a clamping element, which leads to an unfavorable effect of sometimes high clamping forces, especially at the smallest pinion.It should be noted that the adapter 26 is not pressed into this radial recess 64, but is received therein with slight play, so that the adapter 26 can be rotated relative to the pinion assembly 12.

[0056] The inner circumferential surface 65, arranged at a distance a from the fitting surface 61 to increase the elasticity of the adapter, interacts with a corresponding outer circumferential surface 67 (see Figure 8 ) for radial positioning. A slight conicity 69 is arranged in front of the outer peripheral surface 67.

[0057] An additional difference to the first embodiment is in the second embodiment according to Figures 5 to 9in that the adapter 26 no longer has an external thread formation on its (smaller-diameter) section 34 because an additional clamping nut is no longer required. However, the adapter 26 has radially inward-projecting projections 68 on its smaller-diameter section 34, which a tool can engage to transmit torque for assembly purposes.

[0058] In this embodiment, the pinion assembly comprises the support ring 54 designed for torque transmission to the driver with its integrally formed largest pinion 14 10 (terminal pinion), the subassembly comprising the pinions 14 1 to 14 9 , the pre-inserted tubular element 50, and the pre-inserted adapter 26. This assembly is slipped onto the driver 16 and fixed by screwing the adapter 26 with its internal thread formation 38 onto the external thread formation 30 of the driver 16. During this screwing, the adapter 26 rotates relative to the subassembly comprising the pinions 14 1 to 14 9 .

[0059] This results in a relatively simple, lightweight, and, above all, extremely easy-to-assemble design. Both versions have the advantage of allowing the use of a pinion assembly with very small pinions and thus a low number of teeth. The second version, according to the Figures 5 to 9has the further advantage that the use of an additional clamping nut is no longer necessary. This means that there are no longer any contact forces acting on the smallest pinion, which could impair its elasticity during power transmission from the chain. Furthermore, by omitting the clamping nut, associated practical disadvantages can be avoided, such as the requirement for additional installation space for the clamping nut. In addition, undesirable interaction of an assembly tool inserted into the outer profile of the clamping nut with the teeth of the pinion during assembly or undesirable interaction of the outer profile of the clamping nut with the chain resting on the smallest pinion during operation can be avoided.

[0060] In the Figures 10 to 13 A further variant is shown, which is based on the second variant according to the Figures 5 to 9The following section will discuss the differences to this second version.

[0061] The driver 16 according to the third embodiment is designed similarly to the driver of the second embodiment, but the external thread 22 is shifted further to the left in the axial direction. The main differences lie in the design of the adapter 26 and the attachment of an additional mounting ring 70.

[0062] The adapter 26 has an internal thread 30 in its area 28. It is tubular and has only small diameter differences. Figure 11 right end it has a circumferential projection 60 with a contact surface 62 and a circumferential chamfer 63. One can see in Figure 11The adapter 26 is provided at its axial end with a plurality of axial slots 72 that radially penetrate the adapter 26 beyond the circumferential projection 60, thus creating individual locking tabs 74. The axial slots 72 allow the locking tabs 74 to elastically spring radially inward. The locking tabs 74 are provided with a circumferential bevel 75 to facilitate the locking process.

[0063] Figures 12 and 13show the mounting ring 70. This has two ring-like sections 80 and 82, which are connected to each other via a connecting section 84. The outer ring section 80 has an external toothing 86 with radially projecting projections 86 on its outer circumference. The number and dimensions of the projections 86 as well as their arrangement are precisely matched to those of the slots 72 in the adapter 26, so that the mounting ring 70 can be inserted into the adapter 26 in such a way that the projections 86 engage more or less precisely in the slots 72. However, a radial play 88 results between the mounting ring 70 and the inner circumferential surface of the tabs 74 (see Figure 10 ) to ensure that the tabs 74 can spring radially inwards. On the inner circumferential surface, the mounting ring 70 has a toothing 68, as already described with reference to Figure 5 was explained.

[0064] The inner peripheral surface 89 of the outer ring portion 80 is designed as a mating surface intended for radial positioning of the mounting ring 70 relative to the driver. It sits precisely on the outer peripheral surface 25 of portion 20 of the driver 16.

[0065] The inner ring portion 82 of the mounting ring 70 is provided with a mating surface 91, which cooperates with an inner peripheral surface 93 on the pinion assembly 12 for radial positioning. Furthermore, a stop surface 95 is provided on the inner ring portion 82, which serves to axially position the pinion assembly relative to the driver. This surface cooperates with a corresponding end face 97 of the driver 16.

[0066] The assembly of this third embodiment is similar to that of the second embodiment. First, the adapter 26 is screwed onto the driver 16. Subsequently, the mounting ring 70 is inserted into the adapter 26 so that the projections 86 engage the slots 72. The pinion assembly 12 is then fitted and finally locked with the locking tabs 74. The chamfer 63 facilitates positioning and insertion. The radial play between the mounting ring 70 and the locking tabs 74 allows for appropriate elastic deformation of the tabs 74 during locking.

[0067] Finally, a torque-transmitting assembly tool can engage the toothing 68 on the inner circumferential surface of the mounting ring 70, allowing the mounting ring 70 and, with it, the adapter 26 to be rotated to screw it onto the external thread 30. This allows the pinion assembly 12 to be clamped axially onto the driver 16, with the corresponding axial forces being generated via the interaction of the two surfaces 62 and 66 between the adapter 26 and the pinion assembly 12.

[0068] Figures 15 to 17 show a further embodiment, wherein again the same reference numerals have been used for similar or equivalent components as in the preceding description of the embodiments according to Fig. 1 to 14 .

[0069] The embodiment according to Fig. 15 to 17is characterized by a particularly advantageously designed driver 16, which is mounted on an axle 11. This driver 16 in turn has the annular radial projection 19 with its axial stop surface for axial positioning of the pinion assembly 12. Directly adjacent to the radial projection 19, the external toothing 17 extends over a relatively small length section for torque transmission between the pinion assembly 12 and the driver. Adjacent to the external toothing 17 extends the external thread formation 22. In terms of arrangement, the driver 16 according to the embodiment according to Fig. 15 to 17 the driver according to the embodiment according to Fig. 14 . As in Fig. 15If, as shown, the adapter 26 is screwed onto the pinion assembly 12 and fixed by tightening the screw connection, tensile forces occur in the driver 16 only in the area between the annular section 19 due to its stop function and the threaded section 22. The area in which these tensile forces occur is relatively small in the axial direction and is designed to be stable due to the toothing 17.

[0070] Extending axially adjacent to the external thread formation 22 is a relatively large cylindrical section 23 which interacts with a corresponding cylindrical inner circumferential surface to guide the adapter 26. This surface section 23 also serves as a guide surface for the adapter 26 and the pinion assembly 12 attached thereto during assembly. This guide surface 23 allows the adapter 26 to be securely pushed and screwed onto the driver 16 with a certain radial play, without the adapter 26 becoming tilted relative to the driver 16 or even being screwed on at an angle that could damage the thread formations 22 and 30. It should be noted that both the driver and the adapter can be made of lightweight aluminum, which material is relatively easily deformed. It is precisely for this reason that the guide surface 23 is advantageous.At the axial end of the surface section 23, the driver 16 is formed with the shoulder 24 and terminates in the reduced-diameter projection with the outer peripheral surface 25, which in turn serves as a mating surface for radial positioning of the adapter 26. Radially within this area, the mating surface 57 is provided for receiving the radial bearing 55.

[0071] Fig. 18shows an alternative embodiment in which an end face 24 is provided instead of a shoulder 24, and the axial section of the driver 16, which serves to position the adapter 26 and has been reduced in its outer peripheral surface, has been omitted at its axial end. Instead, the radially inner fitting surface 57 has been radially enlarged to accommodate a larger-diameter bearing 55, which protrudes from the driver 16 by an axial section. This projecting axial section, with its precisely formed outer peripheral surface, forms the fitting surface 25 usable for positioning the adapter.

[0072] Figures 19 to 23 show a further embodiment, wherein again the same reference numerals have been used for similar or equivalent components as in the preceding description of the embodiments according to Fig. 1 to 18 .

[0073] The embodiment according to Fig. 19 to 23corresponds essentially to the embodiment according to the Figures 15 to 18 and is characterized by an advantageously designed adapter 26. This adapter 26 has a plastic body 100 in its right-hand end region, which is arranged near the mating surface 25 in the assembled state. This plastic body 100 provides an annular plastic sheath 102, 104 on both the outer peripheral surface and the inner peripheral surface of the adapter 26.

[0074] How to Figure 20 As can be seen, the adapter body 26 as a blank is slightly conical in this area and has radial openings 106 arranged at regular angular intervals. In the area of ​​these radial openings 106 are the two plastic rings 102, 104. They are integrally connected to each other by webs 108 which extend through the openings 106. Thus, the two plastic rings 102, 104 can be attached to the adapter blank according to Figure 20injection molded and integrally molded onto the adapter 26.

[0075] The two plastic rings 102, 104 are formed with mating surfaces 110, 112, each extending parallel to the longitudinal axis A and with a surface portion orthogonal to the longitudinal axis A. The mating surface 112 on the inner plastic ring 104 serves to radially and axially position the adapter 26 relative to the driver 16. The mating surface 110 on the outer plastic ring 102 serves to position the pinion assembly relative to the adapter 26.

[0076] The two plastic rings 102, 104 enable tolerance compensation in the interface to the adjacent component and the provision of suitable positioning or fitting surfaces for those components that come into contact with the adapter with relatively little effort.

[0077] In the embodiments according to the Figures 5 to 23 There are further advantages compared to the state of the art: The locking mechanism eliminates the contact forces on the small pinion via an additional clamping nut. Other disadvantages associated with the clamping nut, such as additional installation space or undesirable interaction with the chain or the smallest pinion during operation or assembly, can also be avoided. The pinion assembly can be dimensioned for greater rigidity, particularly in the locking area, but can be made weaker and therefore lighter in other areas. Special positioning mating surfaces can also be provided for the driver and pinion assembly for centering and absorbing radial loads. The driver's structure and weight can also be significantly improved compared to the state of the art.It features an external thread for clamping and a corresponding drive profile for torque transmission, even in the area of ​​the smaller pinions, which prevents unfavorable stress conditions. The arrangement of the bearing within the pinion assembly is subject to significantly fewer restrictions. In particular, the designs according to . Fig. 15 to 23 are advantageous due to the advantageous concentration of the tensile forces occurring in the area of ​​the relatively solid toothing 17.

[0078] Overall, all embodiments of the invention provide numerous advantages over the prior art. The individual components have been significantly optimized compared to the prior art and interact with their individual features to create a lighter, easier-to-assemble, and more stable system.

Claims

1. Multiple sprocket arrangement (10), having a plurality of sprockets (141-1410) with different numbers of teeth, for mounting on a rear-wheel axle of a bicycle, comprising - a sprocket assembly (12), on which at least some of the plurality of the sprockets (141-1410) are provided, wherein the sprocket assembly (12) is provided with a torque-transmission section and is connected or connectable in a torque-transmitting manner to a driver (16), which is configured for mounting onto the rear-wheel axle, and - an adaptor (26) which, for fixing the sprocket assembly (12) axially, is connected or connectable to the driver (16) via a first coupling portion (28), characterized in that the adaptor (26) engages around the driver (16) in the axial region of at least one sprocket of the sprocket assembly and is screwable or screwed onto a threaded formation of the driver (16), wherein the adaptor (26) is designed with a second coupling portion (34), by way of which it is coupled or couplable to the sprocket assembly (12).

2. Multiple sprocket arrangement (10) according to Claim 1, characterized in that, in the region of its first coupling portion (28) and / or in the region of its second coupling portion (34), the adaptor (26) is designed with a mating surface (110, 112) for radial and / or axial positioning relative to the sprocket assembly (12) and to the driver (16).

3. Multiple sprocket arrangement (10) according to Claim 2, characterized in that the mating surface (110, 112) is formed by a plastic body (100) which is fitted on the adapter (26).

4. Multiple sprocket arrangement (10) according to Claim 3, characterized in that the plastic body (100) comprises at least one plastic ring (102, 104), which is injection moulded onto the adaptor (26), and preferably extends through through-passages (106) in the adaptor (26).

5. Rear-wheel-axle arrangement for a bicycle, having - a rear-wheel axle, which is designed to be fastened on a bicycle frame, - a hub body, which is mounted in a rotatable manner on the rear axle, - a driver (16), - a multiple sprocket arrangement (10) according to one of Claims 1 to 4, said multiple sprocket arrangement interacting with a drive chain, and - a torque-transmission arrangement for direction-selective transmission of a torque from the multiple sprocket arrangement (10) to the hub body, in order to drive the hub body.