HUB ESPECIALLY FOR BICYCLES

Description

[0001] The present invention relates to a rotor and a hub equipped therewith for vehicles, and in particular bicycles, that are at least partially muscle-powered in normal and regular intended use, wherein the hub comprises a hub housing, a rotor, a freewheel mechanism, and a hub axle. The hub housing and the rotor are each rotatably mounted by at least two rolling bearings. The freewheel mechanism is provided in the rotor and the hub housing to connect the rotor to the hub housing in a rotationally fixed manner in the direction of drive. When the user does not apply any driving force or pedals backward, the freewheel mechanism enables a freewheel state in which the hub can continue to rotate while the rotor, for example, is stationary.

[0002] Besides bicycles, the hub can also be used in other partially muscle-powered vehicles and two-wheelers, which, for example, have an electric auxiliary drive. The hub is used in particular in sports bicycles. In all embodiments, the hub according to the invention is used in such vehicles, and especially bicycles, which are at least partially muscle-powered in normal and regular intended use.

[0003] Various hubs with a freewheel mechanism are known in the prior art, preventing the crank arm from constantly rotating, for example, when descending a hill. These hubs feature pawl-type freewheels where the pawls can pivot radially between a freewheel position and an engaged position. Such hubs have a varying number of pawls, often with four pawls arranged symmetrically around the circumference. When power is transmitted, the pawls engage with teeth in the rotor. Due to the relatively small number of pawls, a relatively large rotation angle is required before torque is transmitted again when pedaling.

[0004] DE 10 2016 010 853 A1 and EP 3 118 019 A1 each disclose a rear wheel hub for bicycles with a rotor and a toothed disc freewheel, in which both toothed discs are axially movable and in which the rotor-side toothed disc is arranged radially outside the rotor. EP 3 517 315 ​​A1 of the applicant discloses a rear wheel hub for bicycles in which the hub-side toothed disc is fixedly and axially immovably coupled to the hub housing and in which the rotor-side toothed disc is arranged radially inside the rotor.

[0005] The EP 1 121 255 B1 is a hub with a toothed freewheel that reliably and very quickly transmits the drive force from the rotor to the hub shell. Friction losses are relatively low when the user is not pedaling. The hub provides reliable operation and ensures even loading of the toothed disc teeth. This is achieved in this hub with two toothed discs, each axially movable and pressed axially towards each other from the outside by a spring. This allows both toothed discs to float and align themselves relative to each other in the event of hub deflection or other loads, thus ensuring particularly reliable operation.

[0006] EP 3 275 692 A1, the applicant's patent patent, discloses a further development of such a lightweight hub with a toothed disc freewheel and reliable operation. In this hub, the toothed disc freewheel comprises a rotor-side freewheel component and a hub-side freewheel component. The hub-side freewheel component is screwed into the hub housing and forms a bearing seat for a rolling bearing that supports the hub housing. This increases the hub's stiffness.

[0007] To further increase stability, a hub with such a toothed disc freewheel is known from DE 10 2020 103 129 A1 of the applicant, wherein the hub bearing arranged on the rotor side for supporting the hub housing is located in an area with an increased diameter of the hub axle. This allows for increased stability, as the wall thickness of the hub axle in the area of ​​the hub bearing facing the rotor can be considerably greater.

[0008] German patent DE 10 2015 009 041 A1 discloses a hub in which a type of toothed disc freewheel is provided via coupling rings. The aim is to provide a clearance fit between the hub axle and the inner race of a bearing, simplifying assembly. Furthermore, a noise reduction element is used to dampen the characteristic noises of a toothed disc freewheel. A fastening element inside the hub axle spreads the axle in the area of ​​the bearing to ensure a secure fit and easy assembly. Due to the many different components, the design is complex.

[0009] The object of the present invention is therefore to provide a lightweight hub that enables a simple design, high stability and very reliable function.

[0010] This problem is solved by a rotor having the features of claim 1 and by a hub equipped therewith having the features of claim 4. Preferred embodiments of the invention are the subject of the dependent claims. Further advantages and features of the invention will become apparent from the general description and the description of exemplary embodiments.

[0011] A hub according to the invention is intended for at least partially muscle-powered vehicles, and in particular bicycles, and comprises a hub axle, which is in particular hollow, a hub housing, a rotor according to the invention with a rotor body, and a freewheel device with two toothed disc assemblies. One of the toothed disc assemblies is designed as a hub-side toothed disc assembly and is coupled to the hub housing. The other toothed disc assembly is designed as a rotor-side toothed disc assembly coupled to the rotor body and interacts with the hub-side toothed disc assembly to couple the rotor to the hub housing in a rotationally fixed manner in the drive direction and to decouple them from each other in a freewheel state. The toothed disc assemblies each have face teeth for meshing with each other and are preloaded into an engagement position by means of at least one preloading device.On the outside of the rotor body, at least one pinion receptacle for at least one pinion assembly is formed. At the hub-side end, the rotor body includes an inner radial wall for the radial support of a (hub-side) rotor bearing. At an end face of the hub-side end of the rotor, a circumferential receptacle, accessible from the end face, is formed radially between the inner radial wall and an outer wall of the rotor. The rotor-side toothed disc assembly is mounted in this receptacle so as to be rotationally fixed in the drive direction and axially movable.

[0012] The rotor and hub according to the invention offer many advantages. A significant advantage of the hub according to the invention is its compact design, which features an encapsulated structure and allows for broad rotor support. By providing or accommodating a hub-side rotor bearing on an inner radial wall at the hub-side end of the rotor body, particularly broad rotor support can be ensured. The receptacle in the rotor body, accessible from the hub-side end face, which houses the rotor-side toothed disc assembly, ensures a simple and reliable seal for the freewheel mechanism, while simultaneously allowing the rotor-side toothed disc assembly to move axially and be guided axially on the rotor.

[0013] In a preferred embodiment, the hub-side toothed disc assembly is mounted radially within the hub housing, and the spur gearing is oriented towards the rotor. In particular, the rotor-side toothed disc assembly is mounted radially within the rotor, and the spur gearing is oriented towards the hub housing.

[0014] Particularly preferably, at least half the axial width of the rotor-side toothed disc assembly is radially enclosed within the hub housing. This means that the rotor-side toothed disc assembly is directly surrounded in the radial direction by parts of the rotor, which in turn is at least partially surrounded radially by the hub housing in the region of the rotor-side toothed disc assembly. In other words, there is a cross-sectional plane of the rotor-side toothed disc assembly transverse (and in particular perpendicular) to the axis of symmetry (axis line) (of the hub) that intersects the rotor with the rotor-side toothed disc assembly and also the hub housing. This ensures a compact design.

[0015] Preferably, the hub-side toothed disc assembly and the rotor-side toothed disc assembly are each radially externally and rotationally fixed to the hub housing and rotor, respectively, in the drive direction. In particular, the rotor-side toothed disc assembly has an external radial toothing that engages with a radial internal toothing in the rotor. The rotor-side toothed disc assembly is axially movable relative to the rotor and is guided axially by the meshing radial internal toothing and the external radial toothing. This means that the rotor-side toothed disc assembly can move in at least two different axial positions relative to the rotor. The different axial positions can also differ in the circumferential direction, for example, if the external radial toothing is designed as helical gearing.

[0016] Preferably, the gear assembly on the hub side also has an external radial toothing which engages with a radial internal toothing in the hub housing. Preferably, the gear assembly on the hub side is axially movable relative to the hub housing. Helical toothing is also conceivable here.

[0017] In preferred embodiments, the outer diameter of the pinion mount is smaller than the outer diameter of the rotor-side gear assembly and / or smaller than the outer diameter of the face teeth of the rotor-side gear assembly. The pinion mount serves to accommodate at least one pinion, several pinions, or a pinion cluster on the rotor and typically has a standardized outer shape or diameter.

[0018] By ensuring that the outer diameter of the rotor-side toothed disc assembly is preferably larger than the outer diameter of the pinion mount, particularly secure support and highly reliable transmission of the drive torque are guaranteed. The large outer diameter of the spur gear teeth of the rotor-side toothed disc assembly allows for a large number of teeth on the spur gear, resulting in a particularly small pressure angle. This ensures a direct response from the freewheel mechanism. Only a small pedaling angle is required to re-engage the gear.

[0019] In preferred embodiments, the radial internal toothing on the hub housing is formed on a threaded ring screwed into the hub housing. The threaded ring can be made of the same material as the hub housing, or of a lighter or stronger material. For example, the threaded ring can be made of steel, aluminum, titanium, or an alloy of such materials.

[0020] In preferred embodiments, the threaded ring has a central and, in particular, conical recess on its axial outer side (facing the rotor), into which a conical section formed on the hub-side end face of the rotor immerses without contact. This enables a compact design. Furthermore, a conical sealing section can be formed between the conical recess and the conical section.

[0021] Preferably, the threaded ring has a (conical) support section on its axial inner side facing away from the rotor, which rests against a correspondingly (conical) receiving contour in the hub housing. In particular, the support section is supported against the receiving contour in the hub housing.

[0022] The threaded ring has an external thread that screws into an internal thread of the hub shell. Its orientation is such that when pedaling, the threaded ring is screwed further into the hub shell in the direction of rotation, thus transmitting a corresponding torque. This ensures that the threaded ring does not loosen unintentionally.

[0023] In preferred embodiments, the external thread of the threaded ring extends axially outwards beyond the hub-side toothed disc assembly and preferably radially beyond the rotor-side toothed disc assembly, at least partially covering it (in the radial direction). This results in a particularly compact design. Furthermore, the external thread on the threaded ring can be extended, thereby reducing the surface load.

[0024] In particularly preferred embodiments, the external thread of the threaded ring comprises at least two separately formed and continuous threads. Preferably, the internal thread in the hub housing comprises two correspondingly separately formed and continuous threads. Such a multi-start thread allows for an overall higher load-bearing capacity and a lower axial force exerted on the hub housing by the applied torque.

[0025] Preferably, at least one toothed disc assembly, and in particular at least the rotor-side and / or hub-side toothed disc assembly, has an engagement body on which the face teeth and the outer radial teeth are formed. Preferably, the engagement body has an axial extent greater than the axial width of a rolling bearing. In particular, the axial extent is greater than the axial width of the hub-side rotor bearing. Preferably, the axial extent of the engagement body is at least greater than half the axial width of the hub-side rotor bearing. This ensures a considerable length of axial guidance for at least one toothed disc assembly.

[0026] Particularly preferably, the engagement body of at least one toothed disc assembly has an axial extent that is greater than the radial height of the face teeth on the engagement body. In particular, the axial extent is at least 1.5 times greater than the radial height of the face teeth. Specifically, the axial length of the outer radial teeth on the engagement body is (at least 1.5 times) greater than the radial height of the face teeth. This enables a toothed disc assembly with a large clear inner diameter and a large contact area of ​​the toothed disc assembly in the region of the face teeth, while simultaneously providing reliable and reproducible guidance in the axial direction.

[0027] In particularly preferred embodiments, the hub-side toothed disc assembly and the rotor-side toothed disc assembly are essentially identical and, most preferably, exactly identical. Identical toothed disc assemblies simplify assembly and reliably prevent assembly errors. Furthermore, inventory management is simplified.

[0028] Particularly preferably, each of the two toothed gear assemblies is assigned at least one preloading device, which presses the toothed gear assemblies together in a floating manner. The freewheel assembly then comprises two freewheel components, each of which includes a toothed gear assembly and a (preferably identical) preloading device. In simple embodiments, a toothed gear assembly is formed by the engagement body, on which both the external radial teeth and the face teeth are formed.

[0029] The rotor is particularly preferably mounted with at least, and especially exactly, two axially spaced rotor bearings rotatably opposite and, in particular, on the hub axis. One of the rotor bearings is arranged closer to the hub housing and can be referred to as the hub-side rotor bearing, and the other rotor bearing is located further away from the hub housing and can be referred to as the outer rotor bearing.

[0030] Preferably, the hub housing is rotatably mounted on the hub axis by at least, and in particular exactly, two axially spaced hub bearings. One of the hub bearings is arranged closer to the rotor and can be referred to as the rotor-side hub bearing, while the other hub bearing is located further away from the rotor and can be referred to as the outer hub bearing. The outer hub bearing and the outer rotor bearing are then arranged at opposite ends of the hub.

[0031] The rotor body has a hub-side end and an opposite outer end. Preferably, the rotor body has an end section with an increased diameter at the hub-side end, in which (and particularly in which) the rotor-side toothed disc assembly is accommodated. The end section preferably extends from the hub-side end of the end section or the hub-side end of the rotor to another end located remotely from it.

[0032] A sealing device is preferably formed between the hub housing and the rotor, comprising an axially inner (and in particular conical) sealing gap between the hub housing and the rotor, an axially outer sealing gap, and a sealing unit with a sealing lip axially between these two gaps. In particular, the axially inner sealing gap is formed by a conical gap between the conical section on the rotor and the conical recess in the threaded ring. The conical section preferably has a clear gap width of less than 1.5 mm and preferably less than 1 mm.

[0033] In preferred embodiments, the end section of the rotor has a circumferential groove on its outer circumference in which the sealing unit is arranged. The sealing unit preferably comprises a circumferential annular section within the groove and an elastic sealing lip projecting obliquely outwards from the annular section. In the assembled state, the annular section and the elastic sealing lip have a V-shape opening towards the axially outer end (of the rotor). The elastic sealing lip tapers conically outwards.

[0034] At the hub-side end of the rotor's end section, a conical section is preferably formed, and at the other end of the end section, a further enlarged diameter area is formed. Between this enlarged diameter area and a radially inwardly projecting sealing wall at the rotor-side end of the hub housing, a (radial) sealing gap is formed between the rotor and the hub housing. The sealing gap preferably has a clear dimension of less than 1 mm or less than 0.5 mm.

[0035] Preferably, a radially circumferential sealing groove is formed in the hub housing adjacent to the sealing wall, into which the elastic sealing lip projects. When water penetrates from the outside, the elastic sealing lip conforms elastically (more firmly) to the inner wall of the sealing groove. Under normal conditions, the elastic sealing lip can (lightly) touch the circumferential sealing groove.

[0036] The radially largest inner diameter (outermost point) of the sealing groove is preferably larger than the largest outer diameter (outermost point) of the elastic sealing lip under normal conditions. The largest inner diameter of the sealing groove is preferably located axially further outward than the largest outer diameter of the elastic sealing lip. The largest outer diameter (outermost point) of the elastic sealing lip under normal conditions is preferably larger than the diameter of the outer sealing gap between the hub housing and the rotor.

[0037] The rotor according to the invention is designed for a hub for at least partially muscle-powered vehicles, and in particular bicycles, and comprises a rotor body extending from an inner, hub-side end to an outer end (an end facing away from the hub housing). The rotor further comprises a rotor-side toothed disc assembly coupled to the rotor body to couple the rotor body to the hub housing in a rotationally fixed manner in the drive direction and to decouple it from the hub housing in a freewheeling state. The rotor-side toothed disc assembly has a spur gear for engaging with a spur gear coupled to a hub housing. The rotor-side toothed disc assembly is preloaded into an engagement position by means of at least one preloading device. At least one pinion receptacle for at least one pinion assembly is formed on the outside of the rotor body.The rotor body comprises an inner radial wall at the hub end for the radial support of a hub-side rotor bearing. At an end face of the rotor, a circumferential recess, accessible from the end face, is formed radially between the inner radial wall and the outer wall. The rotor-side toothed disc assembly is mounted in this recess, fixed in the drive direction but axially movable.

[0038] The rotor according to the invention has many advantages. The rotor according to the invention has the significant advantage that the rotor-side toothed disc assembly is protected within the receptacle. Furthermore, the fact that the hub-side rotor bearing is mounted on an inner radial wall at the hub-side end of the rotor enables a particularly wide axial support for the rotor. The rotor-side toothed disc assembly has a large inner clear diameter, which allows for a high number of teeth in the spur gearing. At the same time, a large force-transmitting surface is provided.

[0039] In a preferred embodiment of the rotor, the rotor body comprises at least two rotor bearings, namely the hub-side rotor bearing and an outer rotor bearing located further away from it. At least one of the rotor bearings, and in particular both rotor bearings, are designed to support the rotor body (directly) on a hub axis.

[0040] In particular, the rotor body has an end section with an increased diameter at the hub end, on which, and especially within which, the rotor-side toothed disc assembly is accommodated. A radial internal toothing (internal radial toothing) is formed on the inner circumference of the end section. The rotor-side toothed disc assembly is rotationally fixed to the outer radial toothing of the toothed disc assembly in the drive direction via this radial internal toothing.

[0041] Preferably, the end section on the outer circumference comprises a circumferential groove with a sealing unit arranged therein, wherein the sealing unit comprises a circumferential annular section in the groove and an elastic sealing lip projecting obliquely outwards from the annular section. In the assembled state, the annular section and the elastic sealing lip form a V-shape opening towards the outer end of the rotor. The sealing unit is conically open to the outside. This ensures a particularly reliable seal.

[0042] In particular, the rotor body can comprise at least two rotor parts, wherein a first rotor part supports the outer rotor bearing and a second rotor part supports the hub-side rotor bearing. This allows for flexible design. Preferably, the second rotor part is screwed into or bolted to the first rotor part.

[0043] Preferably, a connection area is formed on the first rotor part and a connection section on the second rotor part, wherein the connection area of ​​the first rotor part is connected to a connection section of the second rotor part. The connection section has a threaded section and a guide section, and the connection area comprises a liner section and a guide section. The threaded section is screwed to the threaded section, and the guide section is centered on the guide section. The radial tolerance between the first and second rotor parts is greater at the threaded section than at the guide section. This design ensures reliable and secure guidance of the two rotor parts relative to each other. Precise and concentric alignment of the rotor body is particularly important.This is ensured through the cooperation between the management area and the management section.

[0044] Further advantages and features of the present invention will become apparent from the exemplary embodiments, which are explained below with reference to the accompanying figures.

[0045] The figures show: Figure 1: a schematic representation of a mountain bike; Figure 2: a schematic representation of a racing bike; Figure 3: a perspective view of a hub according to the application; Figure 4: a front view of the hub according to Figure 3 Figure 5 shows a section AA through the hub. Figure 4 Figure 6 shows an enlarged detail "X" from Figure 5 Figure 7 shows a schematic cutaway view of the rotor of the hub. Figure 5Figure 8: an enlarged detail of a variant of a hub according to the application; Figure 9: a schematic cutaway view of a two-part rotor for a hub according to the application; Figure 10: a schematic detail of the two-part rotor according to Fig. 9 Figure 11a,b schematic views of a freewheel device and the toothed disc device for a hub according to the application; and Figure 12a-c a schematic perspective view and schematic cross-sections of a threaded ring for a hub according to the application.

[0046] In the Figures 1 and 2Figure 1 shows a mountain bike and a racing bike 100, respectively, each equipped with a hub 1 according to the invention. The mountain bike and racing bike 100 each have a front wheel 101 and a rear wheel 102. The hub 1 according to the invention is used on the rear wheel 102. Both wheels 101 and 102 have spokes 109, a rim 110, and a sprocket assembly 111. Conventional rim brakes or other brakes, such as disc brakes, can be used.

[0047] A bicycle 100 has a frame 103, handlebars 106, a saddle 107, a fork or suspension fork 104, and, in the case of a mountain bike, a rear shock absorber 105. A crankset 112 with pedals provides propulsion. An electric assist motor may be provided on the crankset 112 and / or the wheels. The hub 1 of each wheel can be attached to the frame via a clamping device 58 (e.g., thru-axle or quick-release skewer).

[0048] The bicycles according to Figures 1 and 2 Each of the 102 hubs used on the rear wheel shows Figure 3 in a perspective and Figure 4 in a front view.

[0049] The hub 1 has a hub housing 2 and a rotor 10, as well as a brake disc mount 38. A sprocket mount 10b is provided on the outside of the rotor 10 for receiving a sprocket set with a corresponding number of sprockets. End stops 50, 51 are provided at both ends of the hub 1; these are shown here as being attached, but can also be inserted or screwed in. As can be seen here, the end stops 50, 51 are hollow and serve to receive a clamping axle 59, with which the hub 1 can be attached to the frame.

[0050] Figure 5 shows the AA from Figure 4 The hub 1 has an installation length 25 of 148 mm. The hub 1 comprises the hollow hub axle 5, on which the hub housing 2 is rotatably mounted via the hub bearings 6 and 7. The rotor 10 is also rotatably mounted directly on the hub axle 5 via roller bearings 16 and 17.

[0051] On the hub shaft 5, closer to the rotor 10, a thickening 54 with a radial shoulder 54a is formed, and at the outer end below the hub flange 2b, a thickening 55 with a radial shoulder 55a is formed. The rotor-side hub bearing 6 rests against the radial shoulder 54a, and the outer hub bearing 7, located at the other end of the hub housing 2, rests against the shoulder 55a of the hub shaft 5. Axially outward, the end stop 50 adjoins the outer hub bearing 7. Here, the end stop is pushed onto the hub shaft 5 and seals the hub housing to the outside via an outwardly projecting double flange.

[0052] Towards the rotor 10, a (thin, disc-shaped) spacer 53 is attached to the rotor-side hub bearing 6, and the hub-side rotor bearing 16 is attached to the spacer. A sleeve 52 is slid onto the hub axle 5 as a spacer between the hub-side rotor bearing 16 and the outer rotor bearing 17. The end stop 51 is attached to the outer rotor bearing 17, extending axially outwards. The hub 1 is clamped firmly into the frame.

[0053] The hollow hub axle 5 has an inner clear diameter 5a, which, depending on the design, can be 12 mm, 15 mm, 16 mm, 17 mm, or more. A clamping axle 59 of a clamping device 58 can be inserted through the hollow hub axle 5 to attach the hub 1 to a bicycle frame. At one end, the clamping axle 59 can, for example, have an end piece 59a with an external thread, with which the clamping axle 59 can be screwed into a corresponding thread on the frame. At the other end, a corresponding clamping mechanism can be provided to reliably hold and clamp the hub 1 to a frame.

[0054] The outer diameter 59b of the clamping axle 59 and the inner diameter 5a of the hollow hub axle 5 are matched in such a way that, on the one hand, the clamping axle can be guided (relatively) unimpeded through the hollow hub axle 5, while on the other hand, the hollow hub axle 5 can also be supported by the clamping axle 59 during operation if local deflections occur due to the loads. This increases the overall stability of the hub 1.

[0055] However, it is also possible to dispense with this additional support. In that case, a clamping axle 59 is used, which has a significant radial distance between the hub axle 5 and the clamping axle 59 over large parts of the hub axle 5, in order to impede or minimize the insertion or removal of the clamping axle.

[0056] According to the application, the hub bearings 6 and 7 and also the rotor bearings 16 and 17 are each designed as rolling bearings 8 and each have a plurality of rolling elements 8. In this exemplary embodiment, the rolling bearings are all designed as deep groove ball bearings.

[0057] Hub 1 is clamped rigidly in the frame in the axial direction. The force flow runs, for example, from the left end into Figure 5The force is transmitted through the end stop 50, the inner bearing ring of the outer hub bearing 7, and via the shoulder 55a of the thickening 55 into the hollow hub axle 5. From there, the applied force is directed via the shoulder 54a of the thickening 54 into the inner bearing ring of the hub bearing 6 and through the spacer 53 between the rotor-side hub bearing and the hub-side rotor bearing 16. From there, the force enters the inner bearing ring of the hub-side rotor bearing 16 and is transmitted via the sleeve 52 to the inner bearing ring of the outer rotor bearing 17 and from there through the end stop 51 back into the frame. The hub housing 2 and the rotor 10 are held radially and axially by the deep groove ball bearings.

[0058] The hub housing 2 has a hub flange 2a on the rotor side and a hub flange 2b on the other side. The spokes can be attached to the hub flanges 2a and 2b. Opposite the rotor 10, the brake disc mount 38 is provided at the other and outer end of the hub.

[0059] Radially within the rotor-side hub flange 2a, a threaded ring 40 is screwed into the hub housing. This ring has radial internal teeth 43 into which the hub-side toothed disc assembly 30 is inserted. At the hub-side end of the rotor 10, the rotor-side toothed disc assembly 20 of the freewheel assembly 9 is inserted radially within the end section 60. The end section 60 extends axially outwards from a hub-side end 60a at the hub-side end face 10a to another, or outer, end 60b.

[0060] Both the rotor-side toothed disc assembly 20 and the hub-side toothed disc assembly 30 each have external radial teeth 23, 33 which mesh with corresponding radial internal teeth 43 in the threaded ring 40 and inside the end section 60. The rotor-side toothed disc assembly 20 and the hub-side toothed disc assembly 30 are thus rotationally fixed to the rotor 10 and the hub housing 2, respectively.

[0061] Simultaneously, both toothed disc assemblies 20, 30 can be moved axially between an engaged position E and a freewheel position F. Due to the spur gearing, the helical tooth surfaces of the spur gears slide against each other when pedaling backwards, pushing the toothed disc assemblies 20, 30 apart axially. When drive force is applied, the spur gears re-engage with each other.

[0062] The toothed gear assembly 20 is preloaded into the engagement position E shown by the preloading device 24, here in the form of a cylindrical coil spring. Correspondingly, the toothed gear assembly 30 is axially preloaded into the engagement position E by a preloading device or preloading device 34, also designed here as a cylindrical coil spring. This means that the hub-side toothed gear assembly 30 is preloaded towards the rotor, while the rotor-side toothed gear assembly 20 is preloaded towards the hub housing 2 by the preloading device or preloading device 24. The effect of the preloading device can be achieved by mechanical springs, magnetic springs, or pneumatically.

[0063] The rotor 10 has a rotor body 11 that extends from the hub-side end 11a to the opposite and outer end 11b. The pinion receptacle 10b is provided on the outer surface of the rotor body 11. One or more pinions, or a pinion cluster, can be attached there.

[0064] At the hub-side end 11a, the end section 60 has an enlarged diameter. Within the end section 60, the rotor-side toothed disc assembly 20 is accommodated, which has an outer diameter 20a that is larger than the outer diameter 10c of the pinion receptacle 10b of the rotor body 11.

[0065] The outer diameter 30a corresponds to the outer diameter 20a. The axial widths 20b and 30b are also the same.

[0066] As in Figure 5It is clearly evident that the rolling element planes or cross-sectional planes 3, 4 (through the rolling elements 8a of the rotor-side hub bearing 6 and the hub-side rotor bearing 16) also intersect the toothed disc assemblies 20, 30. It can be seen that the rolling element plane or cross-sectional plane 4 runs through the hub-side rotor bearing 16, the preload device 24, the radial teeth of the rotor-side toothed disc assembly 20, and through the hub flange 2a of the hub housing. Furthermore, a sealing unit 68 arranged radially outside on the end section 60 is intersected by the cross-sectional plane or rolling element plane 4.

[0067] Such an arrangement, in which the cross-sectional planes or rolling element planes 3 and 4 intersect the engagement areas of the radial teeth of the two toothed disc assemblies and the respective associated rolling bearings 6, 16, offers optimal dissipation of the loads occurring during operation. The distance 26 between the two rotor bearings 16, 17 can be chosen to be very large here, since the rotor-side toothed disc assembly 20 is arranged radially outside the hub-side rotor bearing 16 and radially surrounds it. A distance 27 between the two hub bearings 6, 7 can also be chosen to be very large, since the hub-side toothed disc assembly 30 is also arranged radially outside the rotor-side hub bearing 6 and radially surrounds it.

[0068] The clear inner diameter 20c, 30c of the two toothed disc assemblies is each (significantly) larger than the outer diameter of the respective rolling bearings 6, 16. The clear inner diameters 20c, 30c (cf. Fig. 6) are considerably larger, since the rolling bearings 6, 16 each have an inner wall 18, 36 on the rotor 10 or hub housing 2 at the outer diameters 6b, 16b, which each extend towards each other like fingers under the receptacles 15, 35.

[0069] Radially outside the inner wall 18 of the rotor, a receptacle 15 is formed in which the rotor-side toothed disc assembly 20 is fixedly mounted. Radially outside the inner wall 36 in the hub housing, a receptacle 35 is formed in which the hub-side toothed disc assembly 30 is fixedly mounted on the threaded ring 40.

[0070] With this design, a spacing 27 between the two hub bearings of between 55 mm and 60 mm, specifically 57 mm in this case, is possible with an installation width 25 of, for example, 148 mm. The spacing 3a between the two cross-sectional planes 3 and 4 can be very small, for example, 7 mm, 8 mm, or 9 mm. The spacing 26 between the two rotor bearings 16 and 17 can be between 27 mm and 35 mm, for example, 32 mm in this case. The spacing 28 can be 18 mm, and the spacing 29 can be 33 mm.

[0071] Figure 6 The enlarged detail X shows Figure 5On the hub axis 5, the rotor-side hub bearing 6 with a width 6a and its hub-side rotor bearing 16 with a width 16a are visible, between which a thin spacer 53 is visible. The spacer 53 serves to decouple the two outer bearing rings of the bearings 6 and 16 from each other. The width of the spacer 53 is less than half, a quarter, or an eighth of the axial width 16a of the hub-side rotor bearing 16.

[0072] The rotor-side hub bearing 6 carries a wall 36 of the hub housing 2, which extends towards the rotor 10 in a finger-like and, in particular, wedge-like manner, and radially surrounds the rotor-side hub bearing 6. The hub housing 2 is supported by the wall 36. Radially around this wall is the receptacle 35, in which the hub-side toothed disc assembly 30 is received. The hub-side toothed disc assembly 30 is preloaded into the engagement position E by the preloading device 34.

[0073] The toothed disc assembly 30 has an external radial toothing 33 (compare Figure 11b ), which has a radial internal toothing 43 (compare Figure 12a ) in the threaded ring 40. The threaded ring 40 is screwed into the internal thread 48 in the hub housing 2 via the external thread 41.

[0074] A receptacle 15 is formed on the hub-side end face 10 of the rotor 10, in which the rotor-side toothed pulley assembly 20 is received. The rotor-side toothed pulley assembly 20 has a face tooth 22 oriented towards the hub housing. The face tooth 22 meshes with the face tooth 32 on the hub-side toothed pulley assembly 30. The toothed pulley assemblies 20 and 30 are each pressed axially towards each other by the preloading device 24 and 34, respectively.

[0075] The holder or insert 24a in the receptacle 15 on the hub-side end face 10 of the rotor 10 ensures that identical toothed pulley assemblies 20, 30 can be used, thus simplifying assembly by eliminating the possibility of confusion. For production purposes, it is necessary to enlarge the receptacle 15 to accommodate the radial internal toothing 13 in the end section 60 of the rotor 10. Identical conditions prevail in the receptacles 15, 35.

[0076] An axial width 33a of a radial toothing 33 of the hub-side toothed disc assembly 30 and the (preferably) identical axial width 23a of the radial toothing 23 of the rotor-side toothed disc assembly 20 can in particular be larger than an axial width 16a or also an axial width 6a of a rolling bearing 6 or 16.

[0077] The axial width 42 of the threaded ring 40 is radially larger on the outer side because the threaded ring has a central recess 44 on the rotor side, which is described here as a conical recess or chamfer 44 (compare Figure 12b ) is formed. This allows the thread length of the external thread 41 to be increased, which increases stability.

[0078] The engagement bodies 21, 31 of the rotor-side toothed disc assembly 20 and the hub-side toothed disc assembly 30 each have radial teeth 23, 33 over an axial length 23a and 33a, respectively, which is significantly greater than the radial height 22b and 32b of the face teeth 22 and 32, respectively. This ensures precise axial guidance of the two toothed disc assemblies. The axial length 21a, 31a of the engagement bodies 21, 31 is each greater by the axial width of the face teeth.

[0079] The threaded ring 40 can be screwed to the hub housing 2 via a multi-start thread. For this purpose, see the upper right in Figure 6 An optional embodiment is shown in which two continuous and separate threads 41a and 41b are screwed into corresponding threads 49a and 49b in the hub housing 2.

[0080] The sealing device 65 for sealing the freewheel device 9 against environmental influences comprises a nearly horizontal (outer) narrow sealing gap 67 with a small radial height or clear dimension 67a, which is less than 0.5 mm. The outer sealing gap 67 extends between an enlarged diameter area 63 at the end section 60 and a radially inwardly projecting wall 46 on the hub housing 2.

[0081] Viewed axially inwards from that point, a groove 62 is formed radially outwards on the end section 60, in which a sealing unit 68 with an annular section 69 is received. An elastic sealing lip extends obliquely outwards from the groove 62 from the annular section 69, so that a V-shaped cross-section is formed between the annular section 69 and the elastic sealing lip 70, which is open axially outwards towards the outer sealing gap 67. The sealing lip 70 projects into a circumferential groove 47 (compare Figure 8 ).

[0082] A conical gap 66a, or cone gap, extends axially further inwards, with a clear gap width 66b. The sealing device 65 therefore comprises three sealing gaps: firstly, the cone gap 66a; secondly, the gap between the elastic sealing lip 70 and the wall of the sealing groove 47 in the hub housing; and thirdly, the outer sealing gap 67 between the outer wall 19 in the enlarged diameter area 63 at the end section 60 of the rotor 10.

[0083] In Figure 6It is again clearly evident that the cross-sectional plane 4 extends through the rolling elements 8a of the hub-side rotor bearing 16, through the radial gearing 23, and through the sealing unit 68, as well as the rotor-side hub flange 2a. The hub-side rotor bearing 16 supports the inner radial wall 18 of the rotor body 11. Radially outside this is the receptacle 15, in which the rotor-side toothed disc assembly 20 is fixedly coupled to the rotor 10.

[0084] The simple design reliably prevents assembly errors.

[0085] Figure 7Figure 1 shows a schematic cross-section through the rotor body 11 of the rotor 10, extending from the hub-side end 11a to the outer end 11b. On the outside of the rotor body 11, the pinion receptacle 10b is provided, which has an outer diameter 10c that is smaller than the diameter of the inner radial teeth 13 on the receptacle 15 for the rotor-side toothed pulley assembly 20.

[0086] At the end region 60 is the enlarged diameter region 63, which provides a wall for the sealing gap 67. The sealing unit 68 can be arranged in the circumferential groove 62. At the hub-side end 11a, the conical section 11c is formed, which, together with the conical recess 44 on the threaded ring 40, forms the inner sealing gap 66 or conical gap 66a. Radially inside, the inner radial wall 18 can be seen, against which the rotor 10 rests on the hub-side rotor bearing 16.

[0087] Figure 8 shows an enlarged detail of a variant of Figure 6 , in contrast to the execution according to Fig. 5 Identical rolling bearings 6 and 16 (with identical widths 8b) are used as hub-side rotor bearings 16 and 6, respectively. This further simplifies assembly and inventory management, as the number of different parts is reduced even further. Here, too, the rotor-side toothed disc assembly 20 is received in the receptacle 15 of the rotor body 11. The radial internal toothing 13 on the outer wall 19 guides the radial toothing 23 of the rotor-side toothed disc assembly 20 in the axial direction. The preloading device 24 presses the face toothing 22 towards the hub housing.

[0088] The outer diameter 70a of the elastic sealing lip 70 is larger than the outer diameter 61 of the outer sealing gap 67. This causes water penetrating axially through the sealing gap 67 to deform the sealing lip 70, which then presses (more firmly) against the wall of the sealing groove 47 and achieves an even greater sealing effect.

[0089] A central cross-sectional plane 20d (central toothed disc plane) through the radial teeth 23 of the rotor-side toothed disc is only a small distance 4b away from a cross-sectional plane 4 (rolling element plane) through the rolling elements 8a of the hub-side rotor bearing 16. The distance 4b between the cross-sectional planes 20d and 4 is, in particular, less than half the diameter or radius of a rolling element 8 and is especially preferably also less than the minimum wall thickness of the hollow hub axle 5. The same applies to the central cross-sectional plane 30d through the axial center of the radial teeth of the rotor-side toothed disc assembly 30. Here, too, the distance 3b between the two cross-sectional planes 3 (rolling element plane) and 30d (central toothed disc plane) is very small and, in particular, less than half the diameter or half the radius of a rolling element 8a of the rotor-side hub bearing 6.

[0090] The central cross-sectional plane 20d through the radial toothing 23 intersects the rolling elements 8a of the hub-side rotor bearing 16. The central cross-sectional plane 30d through the radial toothing 33 also intersects the rolling elements 8a of the rotor-side hub bearing 6. This allows even the highest forces to be effectively dissipated. The distances 3b and 4b are very small and less than half the diameter 8c or even less than half the radius of the rolling elements 8a.

[0091] Figure 9Figure 11 shows a modification of the rotor 10, which here consists of two rotor parts 12 and 14. The rotor body 11 has a first rotor part 12, which provides the pinion receptacle 10b. Furthermore, the wall 37 is formed on the first rotor part 12, by means of which the rotor 10 is supported on the hub axle 5 via the outer rotor bearing 17. The inner radial wall 18 is formed on the second rotor part 14, by means of which the rotor 10 is rotatably supported on the hub axle 5 by the rotor bearing 16 on the hub side.

[0092] The second rotor part 14 is screwed to the first rotor part 12. To ensure precise guidance and concentricity, which is particularly important for the rotor, the first rotor part 12 and the second rotor part 14 each have a connection area 121 and a connection section 141. The connection area 121 comprises a threaded section 122 and a guide section 123. The connection section 141 has a threaded section 142 and a guide section 143. The guide section 143 has a diameter 145.

[0093] A length 141a of the connecting section 141 of the second rotor part 14 corresponds in particular to at least 1 / 4 or 1 / 3 of a length 14a of the second rotor part 14, in particular between a quarter and half of the length of the rotor body 11.

[0094] The ratio of the length 143a of the guide section 143 to the diameter 145 of the guide section 143 is greater than 1:10. Preferably, the ratio of the length 143a of the guide section 143 to the length 141a of the connecting section 141 is greater than 1:4.

[0095] In the assembled state, threaded section 122 and threaded section 142 are screwed together. Guide section 123 and guide section 143 ensure the necessary centering. The radial tolerance in guide section 143 is smaller than the radial tolerance between threaded section 122 and threaded section 142.

[0096] Figure 10 Figure 1 shows the interaction between the connection area 121 and the connection section 141 in an enlarged schematic representation. The connection area 121 extends over a length 121a, which is composed of the length 122a of the threaded area 122 and the length 123a of the guide area 123.

[0097] Accordingly, a connecting section 141 is formed on the second rotor part 14, extending over a length 141a. The connecting section 141 consists of the threaded section 142 and the guide section 143, which extend over lengths 142a and 143a, respectively. The threaded area 122 (or the threaded section 142) has a tighter tolerance 148 than the screwed-together guide area 123 (or guide section 143), which has a tolerance 147. This ensures high precision and repeatability of the radial alignment of the rotor 10.

[0098] Figures 11a and 11bFigure 1 shows identical toothed disc assemblies 20, 30, each comprising a meshing body 21, 31, a face tooth 22, 32, and an outer radial tooth 23, 33. The outer radial tooth 23, 33 extend axially over a length 23a, 33a. The axial extent 21a, 31a of the meshing bodies 21, 31 is greater than the axial length 23a, 33a of the outer radial tooth 23, 33 by at least the axial width of the face tooth 22, 32. The inner diameter 20c is larger than the outer diameters of the rolling bearings 6, 16. The outer diameter 22a, 32a is larger than the outer diameter 10c of the pinion receptacle 10b.

[0099] The number of teeth in the front teeth is preferably greater than 72 and may also be 90, 100, 110 or 120 or more.

[0100] The outer radial teeth 23, 33 of the toothed disc assemblies 20, 30 and the radial internal teeth 13, 43 preferably have between 20 and 60 radial teeth. In this exemplary embodiment, the toothed disc assemblies 20, 30 comprise approximately 36 radial teeth.

[0101] The radial extent 22b, 32b of the face teeth 22, 32 is less than the axial length 23a, 33a of the radial teeth 23, 33.

[0102] In the Figures 12a, 12b and 12c Variants of the threaded ring 40 are shown, each having an axial width 42 and having a preferably multi-start thread on its outer circumference, with which the threaded ring is screwed into a corresponding thread in the hub housing 2.

[0103] At the rotor-side end 40a of the threaded ring 40, a central recess 44 is formed here in the form of a chamfer or conical recess 44, which runs at an angle 44a of, for example, 30° and has a depth 44b.

[0104] The threaded ring 40 is screwed into the hub housing 2 in its intended assembled state. The hub-side toothed disc assembly 30 of the freewheel assembly 9 is received therein. The face teeth 32 point towards the rotor 10 and are preloaded into the engaged position (E) by a preloading device 24.

[0105] The threaded ring 40 has an outer contour 41d with an external thread 41 and a central through-opening 40c with an inner contour 40d. The inner contour 40d has a non-circular inner coupling contour 43b, which couples rotationally fixedly with a matching non-circular outer coupling contour 33b on the outer circumference 33c of the hub-side toothed disc assembly 30 in the drive direction. The inner coupling contour 43b can extend over the entire length or only a portion of the length of the inner contour 40d.

[0106] The threaded ring 40 has a central recess 44 at its rotor-side end 40a, such that the external thread 41 on the threaded ring 40 extends axially further outwards towards the rotor 10 than the inner coupling contour 43b. This makes it possible to widen the external thread 41 of the threaded ring 40 towards the rotor 10. This allows for better engagement of the threaded ring 40 in the hub housing 2. Strength is improved. The external thread 41 is lengthened.

[0107] This results in an axial length 41c of the external thread 41 being greater than an axial length 33a of the coupling structure, which comprises the inner coupling contour 43b and the outer coupling contour 33b. The threaded ring 40 is screwed into an internal thread 48 of the hub housing 2 via the external thread 41.

[0108] The hub-side toothed disc assembly 30 is radially fixed within the threaded ring 40 via the coupling structure 33b, 43b in the drive direction and axially movable. The threaded ring 40 has a central and concentric recess 44 at its rotor-side end 40a. The axial width 41c of the external thread 41 is wider than the axial width 33a of the coupling structure.

[0109] The central depression 44 is in the variant according to Figure 12b The recess 44 is designed as a conical recess. In all embodiments, the recess 44 has an axial depth 44b of at least 5% (and in particular at least 10%) of the axial width 42 of the threaded ring 40. An axial length 41c of the outer contour 41d of the threaded ring 40 is greater than an axial length 43a of the radial internal toothing 43 (as the inner coupling contour 43b).

[0110] The axial depth 44b of the central recess 44 is between 5% and 25% of the axial width 42 of the threaded ring 40, and preferably between 10% and 20% of the axial width 42 of the threaded ring 40. The axial depth 44b of the central recess 44 is preferably between 0.5 mm and 3 mm.

[0111] The central recess 44 can also be stepped in all configurations and, for example, be designed as a stepped recess 44d, as shown, for example, with a dashed line in Figure 12b indicated. A stepped and conical design is also possible. Preferably, the central recess 44 is conical or bulbous, forming a central chamfer. The angle or cone angle 44a of the (conical) recess 44 to a plane transverse to an axis of symmetry of the hub or hub axis is particularly between 5% and 30°.

[0112] In the exemplary embodiment, the inner coupling contour 43b comprises a radial internal toothing 43 on the threaded ring 40 or is designed as such. The outer coupling contour 33b on the hub-side toothed disc assembly 30 comprises an external radial toothing 33 or is designed as such. A conical section 11c formed on the end face 10a of the rotor 10, when assembled, engages without contact in the central recess 44 on the threaded ring 40. A sealing gap is formed between them.

[0113] At the other end 40b a conical support section 45 can be formed (cf. Fig. 12c ), which extends at a conical angle 45a (e.g., 30°). Such a conical support section 45 can save axial installation space. However, it is also possible for the support section 45 to be formed perpendicular to the axis of symmetry. This simplifies manufacturing.

[0114] Overall, a advantageous hub 1 is provided, which is of simple design. The hub 1 is easy to assemble and has a relatively small number of parts. High stability is achieved. A high number of teeth on the face gear allows for a very small pressure angle.

[0115] By arranging the rotor-side toothed disc assembly 20 in the receptacle 15 in the rotor, a compact hub 1 can be provided in which the rotor-side toothed disc assembly 20 is guided in the inner radial teeth 13 of the rotor. This ensures high-quality axial guidance. The large diameter of the radial teeth, and thus of the axial guidance, prevents tilting and jamming and ensures reliable operation. Reference symbol list: 1 hub 148 Tolerance of 143 / 123 2 Hub housing 15 Recording 2a Hub flange 16 hub-side rotor bearing 2b Hub flange 16a axial width 3 Cross-sectional plane, rolling element plane 16b Outer diameter 17 outer rotor bearing 3a Distance of 3, 4 18 inner radial wall 3b Distance 3.30d 19 exterior wall 4 Cross-sectional plane, rolling element plane 20 rotor-side toothed gear assembly 4b Distance 4.20d 20a Outer diameter 5 Hub axle 20b axial width 5a Passage opening 20c clear inner diameter 6 rotor-side hub bearing 20d central cross-sectional plane 6a axial width 6b Outer diameter 21 Interventional body 7 outer hub bearing 21a axial extension 8 rolling bearings 22 Front teeth 8a rolling elements 22a Outer diameter 8b axial width 22b radial height 8c Diameter 8a 23 radial gearing 9 Free-running device 23a axial length 10 rotor 24 Pre-tensioning device 10a hub-side front face 24a holder 10b sprocket mount 25 Installation length 10c Outer diameter 10b 26,27 Storage distance 11 rotor body 28 Distance 11a hub-side end 29 Distance 11b outer end 30 hub-side toothed gear assembly 11c Cone section 12 first rotor part 30a Outer diameter 121 Connection area 30b axial width 121a Length of 121 30c clear inner diameter 122 Thread area 30d central cross-sectional plane 122a Length of 122 123 Management area 31 Interventional body 123a Length of 123 31a axial extension 13 radial internal toothing 32 Front teeth 14 second rotor part 32b radial height 141 Connection section 33 radial gearing 141a Length of 141 33a axial length 142 Threaded section 33b outer coupling contour 142a Length of 142 33c External circumference 143 Guided section 34 Pre-tensioning device 143a Length of 143 35 Recording 145 Diameter of 143 36 inner wall 147 Tolerance of 142 / 122 37 wall 38 brake disc mount 58 Clamping device 40 threaded ring 59 Tensioning axis 40a rotor-side end, axial outer side 59a End piece 59b diameter 40b hub-side end, axial inner side 60 Final section 60a hub-side end (60) 40c central passageway 60b other end of 60 61 diameter 40d Inner contour of 40 62 Nut 41 external thread 63 enlarged diameter range 41a,b thread pitch 41c axial length 65 Sealing device 41d Outer contour 66 inner sealing gap 42 axial width 66a Cone gap 43 radial internal toothing 66b clear gap width 43a axial length 67 outer sealing gap 43b inner coupling contour 67a clear dimensions 44 central depression, conical depression 68 Sealing unit 69 Ring section 44a angle 70 Sealing lip / elastic wall 44b depth 44c Height 70a Outer diameter 44d graduated intensification 100 Bicycle 45 (conical) support section 101 wheel, front wheel 102 wheel, rear wheel 45a angle 103 Frame 46 Sealing wall 104 Fork, suspension fork 47 sealing groove 105 rear wheel damper 47a diameter 106 handlebars 48 Threads in 2 107 saddle 49a,b thread pitch 109 spoke 50,51 End stop 110 rim 52 Sleeve body 111 pinion gear 53 spacers 112 crank 54,55 radial thickenings F Freewheel condition 54a Paragraph E Intervention position 55a Paragraph 56 Image contour (conical)

Claims

1. Rotor (10) for a hub for at least partially muscle-powered vehicles and in particular bicycles (100), comprising a rotor body (11), which extends from an inner, hub-side end (11a) toward an outer end (11b), and comprising a rotor-side toothed disk device (20) coupled with the rotor body (11), to couple the rotor body (10) with a hub shell in a rotationally fixed manner in the driving direction, and to decouple from the hub shell (2) in a freewheeling state (F), wherein the rotor-side toothed disk device (20) comprises an end toothing (23) for engagement with an end toothing (33) coupled to a hub shell (2), and wherein the rotor-side toothed disk device (20) is biased to an engagement position (E) by means of at least one biasing device (24), wherein at least one sprocket accommodation (10b) for at least one sprocket device (111) is configured outwardly on the rotor body (10), and wherein the rotor body (10) comprises on the hub-side end (11a), an inner radial wall (18) to radially support a hub-side rotor bearing (16), characterized in that on an end face (10a) on the hub-side end (11a) of the rotor (10), radially between the inner radial wall (18) and the outer wall (19), a circumferential accommodation (15) accessible from the end face (10a) is configured, in which the rotor-side toothed disk device (20) is accommodated in a rotationally fixed manner in the driving direction and axially movable.

2. The rotor (10) according to the preceding claim, wherein the rotor body (11) comprises at least two rotor bearings (16, 17), namely, the hub-side rotor bearing (16) and an outer, further distant rotor bearing (17), and wherein at least one rotor bearing (16) is configured to support the rotor body (11) on a hub axle (2), and wherein the rotor body (11) comprises on the hub-side end (11a), an end portion (60) with an enlarged diameter, on which the rotor-side toothed disk device (20) is accommodated, wherein an inner radial toothing (13) is configured on the inner periphery (20) of the end portion, in which the rotor-side toothed disk device (20) couples to an outer radial toothing (23) in a rotationally fixed manner in the driving direction, wherein the end portion (60) on the outer periphery comprises a circumferential groove (62) with a sealing unit (68) disposed therein, wherein the sealing unit (68) comprises a circumferential ring portion (69) in the groove (62) and an elastic sealing lip (70) protruding from the ring portion (69) obliquely outwardly, and wherein in the mounted condition, the ring portion (69) and the elastic sealing lip (70) show a V-shape open toward the outer end (11b).

3. The rotor (10) according to any of the two preceding claims, wherein the rotor body (11) comprises two rotor parts (12, 14), wherein a first rotor part (12) supports the outer rotor bearing (17), and a second rotor part (14) supports the hub-side rotor bearing (16), and wherein the second rotor part (14) is screwed into the first rotor part (12).

4. Hub (1) for at least partially muscle-powered vehicles and in particular bicycles (100) comprising a hub axle (5), a hub shell, a rotor (10) according to any of the preceding claims with a rotor body (11), and a freewheel device (9) with two toothed disk devices (20, 30), namely, one hub-side toothed disk device (30) coupled to the hub shell, and the rotor-side toothed disk device (20) interacting therewith and coupled to the rotor body (11), to couple the rotor (10) to the hub shell (2) in a rotationally fixed manner in the driving direction, and to decouple them from one another in a freewheeling state (F), wherein each of the toothed disk devices (20, 30) comprises an end toothing (22, 32) for engagement with one another, and is biased by means of at least one biasing device (24, 34) to an engagement position (E), wherein at least one sprocket accommodation (10b) for at least one sprocket device (111) is configured outwardly on the rotor body (10).

5. The hub according to the preceding claim, wherein the hub-side toothed disk device (30) is accommodated radially within the hub shell (2), and the end toothing (32) is oriented to the rotor (10), and / or wherein the rotor-side toothed disk device (20) is accommodated radially within the rotor (10), and the end toothing (22) is oriented to the hub shell (2), and wherein at least half the axial width (20b) of the rotor-side toothed disk device (20) is accommodated radially within the hub shell (2).

6. The hub according to any of the two preceding claims, wherein the outer diameter (10c) of the sprocket accommodation (10b) is smaller than the outer diameter (20a) of the rotor-side toothed disk device (20) and / or smaller than the outer diameter (22a) of the end toothing (22) of the rotor-side toothed disk device (20).

7. The hub according to any of the three preceding claims, wherein the hub-side toothed disk device (30) comprises an outer radial toothing (33), which is engaged with an inner radial toothing (43) in the hub shell (2) and is axially movable, and wherein the inner radial toothing (43) is configured on a threaded ring (40) screwed into the hub shell (2).

8. The hub according to the preceding claim, wherein the threaded ring (40) on the outer axial surface (40a) has a conical depression (44), into which a conical portion (11c) configured on the hub-side end face (10a) of the rotor (10) plunges contactless.

9. The hub according to any of the two preceding claims, wherein the threaded ring (40) has a support portion (45) on the axially inner surface (40b) facing away from the rotor (10), which support portion bears against a correspondingly configured accommodating contour (56) in the hub shell (2).

10. The hub according to any of the three preceding claims, wherein the external thread (41) of the threaded ring (40) extends axially outwardly beyond the hub-side toothed disk device (30) up to radially beyond the rotor-side toothed disk device (20), which it partially overlaps.

11. The hub according to any of the seven preceding claims, wherein at least one toothed disk device (20, 30) comprises an engagement body (21, 31), on which the end toothing (22, 32) and the outer radial toothing (23, 33) are configured, and wherein the engagement body (21, 31) comprises an axial extension (21a, 31a), which is larger than the axial width (8b) of a roller bearing, and is in particular larger than the axial width (16a) of the hub-side rotor bearing (16), and wherein the engagement body (21, 31) comprises an axial extension (21a, 31a), which is larger than the radial height (22b, 32b) of the end toothing (22, 32).

12. The hub according to any of the eight preceding claims, wherein the rotor (10) is supported for rotation with two axially spaced-apart rotor bearings (16, 17) on the hub axle (5), namely, a hub-side rotor bearing (16) disposed closer to the hub shell, and an outer rotor bearing (17) further distant from the hub shell, and wherein the hub shell (2) is supported for rotation with two axially spaced apart hub bearings (6, 7) on the hub axle (5), namely, a rotor-side hub bearing (6) disposed closer to the rotor and an outer hub bearing (7) further distant from the rotor, and wherein the rotor body (11) comprises a hub-side end (11a) and an opposite, outer end (11b), and wherein the rotor body (11) on the hub-side end (11a), comprises an end portion (60) with an enlarged diameter (61), on which the rotor-side toothed disk device (20) is accommodated, wherein the end portion (60) extends from a hub-side end (60a) of the end portion (60) to another end (60b).

13. The hub according to any of the nine preceding claims, wherein a sealing device (65) is configured between the hub shell (2) and the rotor (10), having an axially inner sealing gap (66) between the hub shell (2) and the rotor (10), and axially further outwardly, an outer sealing gap (67), and axially in-between, a sealing unit (68) with a sealing lip (68b), and wherein the axially inner sealing gap (66) is configured by a cone gap (66a) between the conical portion (11c) on the rotor (10) and the conical depression (44) in the threaded ring (40), and has a clear gap width (66b) smaller than 1.5 mm, and wherein the end portion (60) of the rotor (10) on the outer periphery comprises a circumferential groove (62), in which the sealing unit (68) is disposed, wherein the sealing unit (68) comprises a ring portion (69) in the groove and an elastic sealing lip (70) protruding from the ring portion obliquely outwardly, wherein in the mounted condition, the ring portion (68a) and the elastic sealing lip (70) show a V-shape open toward the axially outer end (11b).

14. The hub according to any of the two preceding claims, wherein the conical portion (11c) is configured on the hub-side end (60a) of the end portion (60) of the rotor (10), and wherein a further enlarged diameter area (63) is configured on the other end (60b) of the end portion (60), and wherein a sealing gap (67) is configured between the enlarged diameter area (63) and a sealing wall (46) on the rotor-side end of the hub shell (2) between the rotor (10) and the hub shell (2), wherein the sealing gap (67) has a clear dimension (67a) of less than 1 mm or less than 0.5 mm, and wherein a circumferential sealing groove (47) is configured in the hub shell (2) adjacent to the sealing wall (46), into which the elastic sealing lip (70) protrudes, and wherein the elastic sealing lip (70) protrudes into the sealing groove (47) and e.g. in the case of water penetrating from the outside, bears elastically against the wall of the sealing groove (47), and wherein the radially largest inner diameter (47a) of the sealing groove (47) is larger than what is the largest outer diameter (70a) of the elastic sealing lip (70) in the normal state, and wherein the largest inner diameter (47a) of the sealing groove (47) is axially further outwardly than the largest outer diameter (70a) of the elastic sealing lip (70), and wherein what is the largest outer diameter (70a) of the elastic sealing lip (70) in the normal state, is larger than the diameter (47a) of the outer sealing gap (67) between the hub shell and the rotor.