HUB

Abstract

A hub for bicycles comprising a hub axle, a hub shell, a rotor, and a toothed disk freewheel including a pair of interacting freewheel components namely, a hub-side freewheel component and a rotor-side freewheel component. The freewheel components each comprise axial engagement components biased in the engagement position through a biasing device. The hub-side freewheel component is axially displaceably received in a threaded ring and non-rotatably coupled with the hub shell in the driving direction. The rotor-side freewheel component is non-rotatably provided at the rotor for transmitting rotational movement from the rotor to the hub shell in the engagement position of the two freewheel components. The threaded ring comprises a thread with a thread groove that extends along a helical line in an axial direction around a circumference of the threaded ring, where the helical line shows less than five full revolutions around the circumference of the threaded ring. The thread is screw-connected with a thread of the hub shell.

Claims

1. A hub for at least partially muscle-powered vehicles and in particular two-wheeled vehicles having a hub axle nd a hub shell and a rotor and a freewheel comprising a pair of interacting freewheel components namely, a hub-side freewheel component and a rotor-side freewheel component, wherein the freewheel components each comprise axial engagement components for intermeshing with one another and are biased in the engagement position through at least one biasing device,wherein the hub-side freewheel component is axially displaceably received in a threaded ring and non-rotatably coupled with the hub shell, and wherein the rotor-side freewheel component is non-rotatably provided at the rotor for transmitting rotational movement from the rotor to the hub shell in the engagement position of the two freewheel components, wherein the threaded ring is provided with at least one thread with at least one thread groove, wherein the thread groove extends along a helical line extending in the axial direction around an outer circumference of the threaded ring, and wherein the helical line shows less than five full revolutions around the circumference of the threaded ring, and wherein the thread is screw-connected with a thread of the hub shell.

2. The hub according to claim 1 , wherein the helical line comprises at least more than two full revolutions of the thread groove.

3. The hub according to claim 1 , wherein the helical line comprises between two and four full revolutions of the thread groove.

4. The hub according to claim 1 , wherein the thread groove extends continuously along the circumference of the threaded ring.

5. The hub according to claim 1, wherein the thread extends over more than 50% of the axial width of the threaded ring.

6. The hub according to claim 1, wherein the thread extends over the entire axial width of the threaded ring.

7. The hub according to claim 1, wherein the axial width of the threaded ring is at least the same size as the axial width of the hub-side freewheel component.

8. The hub according to claim 1 , wherein the thread is a multiple thread which is screw-connected with a multiple thread of the hub shell.

9. The hub according to claim 8, wherein the threaded ring consists of a stronger material than does the hub shell.

10. The hub according to claim 8 , wherein multiple outer threads are formed on the threaded ring and multiple inner threads, on the hub shell, which are screwed to one another when mounted.

11. The hub according to claim 1, wherein a thread groove of at least one of the threads shows a gradient of between 1.5 mm and 4.0 mm.

12. The hub according to claim 11 , wherein a thread groove shows a gradient of 2 mm.

13. The hub according to claim 10 , wherein the multiple outer and inner threads include two, three or more separate thread grooves aligned in parallel.

14. The hub according to claim 1 , wherein the engagement components form one axial toothing each, and wherein at least one of the two freewheel components is configured as a toothed disk.

15. The hub according to claim 1 , wherein a cross-section of the freewheel component is configured U- or L-shaped, and wherein the radial leg is provided with the engagement components.

16. The hub according to claim 1 , wherein the freewheel component has a non-round outer contour and is received in a corresponding non-round inner contour of the threaded ring or of the rotor to be non-rotatable and axially displaceable.

17. The hub according to claim 1 , wherein the biasing device is at least partially disposed in the interior of the freewheel component, and wherein the biasing device presses against the radial leg of the freewheel component in the axial direction, and wherein the engagement components of the rotor-side freewheel component is configured as an end toothing at the rotor.

18. The hub according to claim 1 , wherein at least one freewheel component and the threaded ring consists of steel and the hub shell consists at least in part of at least one lightweight material such as light metal or a fibrous composite material.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

[0046] Further advantages and features of the present invention can be taken from the description of exemplary embodiments which will be discussed below with reference to the enclosed figures.

[0047] The figures show in:

[0048] FIG. 1 a schematic side view of a racing bicycle equipped with a hub according to the invention;

[0049] FIG. 2 a schematic side view of a mountain bike equipped with a hub according to the invention;

[0050] FIG. 3 a schematic cross-section of a first hub according to the invention;

[0051] FIG. 4 an enlarged detail from FIG. 3;

[0052] FIG. 5 an exploded view of the toothed disk freewheel of the hub according to FIG. 3;

[0053] FIG. 6 another schematic cross-section of a hub of another exemplary embodiment;

[0054] FIG. 7 an enlarged perspective view of a threaded ring having four full revolutions of the thread groove.

[0055] FIG. 8 an enlarged perspective view of a threaded ring having three full revolutions of the thread groove.

[0056] FIG. 9 an enlarged perspective view of a threaded ring having two full revolutions of the thread groove.

DETAILED DESCRIPTION

[0057] In FIG. 1 a vehicle 100 is illustrated in a schematic side view presently configured as a two-wheeled vehicle 50 and in particular as a racing bicycle. The bicycle 50 is at least partially muscle-powered and may be provided with an electric auxiliary drive.

[0058] The racing bicycle is illustrated in a simplistic side view and comprises a front wheel 51, a rear wheel 52 and a frame 53. A handlebar 56 serves as a control and may have different configurations. Apart from a racing handlebar configuration other known configurations are conceivable as well. Beneath the saddle 57 a battery 58 may be provided which is employed in particular for electro-assisted two-wheeled vehicles. Generally speaking, such a battery 58 may be attached to the frame in other places or incorporated into the frame or received elsewhere.

[0059] In the bicycle according to FIG. 1 the tire 60 is configured as a tubeless tire and is for example glued onto the rim 61. The rims 61 of the front wheel 51 and the rear wheel 52 are each connected with the hub via spokes 59. The rear wheel 52 is provided with a hub 1 according to the invention as the rear wheel hub.

[0060] FIG. 2 illustrates a mountain bike as the bicycle 50 in a simplistic side view comprising a front wheel 51, a rear wheel 52, a frame 53, a sprung front fork 54 and a rear wheel damper 55. In this exemplary embodiment, disk brakes are provided. The rear wheel 52 is also provided with a hub 1 according to the invention.

[0061] FIG. 3 shows a simplistic cross-section of an inventive hub 1 for a bicycle 50 according to FIG. 1 or FIG. 2.

[0062] The hub according to the invention is provided with a hub axle 2 presently configured hollow and a hub shell 3 presently configured one-piece which comprises two hub flanges 26 for fastening the spokes. In other configurations the hub shell 2 may be configured multipart and for example be provided with a separate hub sleeve to which separate hub flanges 26 are fastened. It is also possible to configure the hub as a “straight pull hub” where no conventional hub flanges are provided.

[0063] The rotor 4 serves to receive at least one sprocket and in particular to receive a sprocket cluster having multiple sprockets. Selecting a corresponding sprocket allows to vary the driving gear ratio as desired.

[0064] The hub shell is supported in the two axial end regions of the hub shell relative to the hub axle 2 through a roller bearing 27. The rotor is likewise supported relative to the hub axle 2 by means of two bearings 27.

[0065] A freewheel 5 is provided here which is configured as a toothed disk freewheel. The freewheel serves to transmit the driving torque to the hub shell while for example in downhill rides or the like a decoupling of the rotational movements of the hub shell and the rotor may occur.

[0066] In the illustrated exemplary embodiment the freewheel 5 is provided with two freewheel components 6 and 7 each provided with axial engagement components 8, 9 which in the engagement position 10 illustrated in FIG. 3 are engaged with one another.

[0067] In the exemplary embodiment the two freewheel components 6, 7 are each configured as a toothed disk 16 or 17, preferably showing identical architecture. The engagement components 8 and 9 each form an axial toothing 18 (cf. FIG. 5) on the front faces of the freewheel components 6, 7 respectively toothed disks 16, 17.

[0068] The cross-section of each of the toothed disks is generally about U-shaped, the geometry of the toothed disks 16 and 17 resulting from combining a perforated disk or washer and a sleeve. The axial toothing 18 is provided at the axial front face of the perforated disk.

[0069] It is also possible to configure the toothed disks solid and provided with an inner hollow cylindrical aperture. These toothed disks have engagement components (in particular in the shape of teeth) configured on one front face and on the other front face a biasing device 11 or 12 acts for biasing the two freewheel components 6, 7 in the engagement position 10.

[0070] The freewheel component 6 configured as a toothed disk 16 is accommodated in the hub component 23 configured as a threaded ring 32 to be axially displaceable and non-rotatable. To this end the toothed disk 16 comprises an external toothing engaging in a corresponding internal toothing of the threaded ring 32 so as to allow axial movement while prohibiting rotational movement of the toothed disk 16 relative to the threaded ring 32.

[0071] One advantage of the separate threaded ring 32 is that the threaded ring 32 is made of a harder and more robust material than the hub shell 3. Since the threaded ring 32 shows a relatively small volume the total weight of the hub is only slightly increased while the service life of the hub is clearly extended.

[0072] The radially outside surface of the threaded ring 32 is provided with a multiple thread 34, presently with two separate, axially spaced apart thread grooves 34a and 34b as the enlarged detail shows. Each separate thread groove 34a, 34b is provided with three continuous thread grooves 34c and extends between the endpoints 62a, 62b along a helical line 62 (not shown) having three full revolutions 62c (wraps) around the threaded ring. The multiple thread 34 of the threaded ring 32 is screwed to a matching, multiple internal thread 35 in the hub shell 3, showing separate thread grooves 35a, 35b, each with three continuous thread grooves 35c. The thread 35 is likewise provided with two continuous thread grooves 35c showing three full revolutions each. The multiple internal thread 35 comprises two separate thread grooves 35a and 35b.

[0073] The gradient R of the thread grooves of the threads 34 and 35 in this exemplary embodiment is 2.0 mm (or 3.0 mm), while the pitch P is 1.0 mm (or 1.5 mm) each. This means that the same pitch “P” shows double the gradient “R” such that the axial forces exerted on the hub shell by the threaded ring in the axial direction are considerably lower than in the prior art where the threaded ring was screwed into the hub shell by a single thread.

[0074] The multiplicity and the helical line 62 (not shown) predetermine a low number of continuous thread grooves 34c with a low number of full revolutions 62c. Basically, this also reduces the retention of the thread 34. However, reduced retention is advantageous since in operation the threaded ring 32 keeps driving into the hub shell 3 such that automatic detachment is excluded in this respect. This thread 34 extends over more than 50% of the width 32a of the threaded ring 32.

[0075] According to the FIGS. 3 and 4 the bearing 27 for supporting the hub shell is radially partially surrounded by the threaded ring 32 on the rotor side. A direct radial contact is not required and is as a rule not present. The threaded ring 32 in particular does not provide a bearing seat. The bearing seat (with correspondingly lower tolerances) is configured in the hub shell 3. It is as a rule provided with a force fit into which the bearing 27 is pressed.

[0076] The other of the freewheel components 7 in the present exemplary embodiment is configured as a toothed disk 17 and also comprises a non-round outer contour and in particular an external toothing which is disposed in a corresponding internal toothing of the rotor 4 to be non-rotatable but axially displaceable.

[0077] In all the configurations the rotor and the hub shell are disposed fixedly spaced apart in the axial direction in (normal) operation.

[0078] Each of the two toothed disks 16, 17 are urged toward one another in the axial direction by means of a biasing device 11 or 12 configured as a coil spring to have the axial toothings 18 of the two toothed disks engage with one another. In this way a torque transmission from the rotor to the hub shell 3 is enabled in the driving direction while in the reversed rotational direction the teeth of the toothed disks 8, 9 are urged away from one another against the force of the biasing devices 11, 12, gliding past one another on their tooth flanks.

[0079] For sealing, a seal 30 is provided between the rotor 4 and the hub shell 3 which can presently comprise a contactless labyrinth seal and/or a contacting elastomeric seal to keep moisture and dust and the like away from the freewheel 5.

[0080] One of the ends is provided with an adapter ring 28 and the other of the ends with an adapter ring 29 which are pushed onto the hub axle 2 and which at their extreme ends comprise regions suitable to be pushed into the dropouts of a bicycle fork or a bicycle frame. A quick release not illustrated in FIG. 3 may for example serve for fastening. It is likewise possible to use a through axle for fastening, wherein the adapter rings 28 and 29 are as a rule not required or not in this shape.

[0081] The adapter ring 28 presently comprises a double-flange seal 31 acting as a double labyrinth seal and showing high efficiency. The adapter ring 29 may be configured in analogy and be provided with a double-flange seal.

[0082] The bearings 27 used are preferably commercially available roller bearings provided with an outer ring, an inner ring and rolling members disposed in-between. The rolling members are preferably retained by a holding device such as a rolling member cage or the like. Particularly preferably, the axial ends of the roller bearings show seals for protecting the interior of the roller bearing. The seals may be elastomeric seals. The bearings used are preferably deep-groove ball bearings.

[0083] A clear inner diameter of the freewheel components 6, 7 is in particular not larger than twice or three times or four times the axial width 13 of the toothed disk 16. This ensures a secure seat of the toothed disk 16 in the threaded ring 32 and prevents possible tilting of the toothed disk 16 in moving back and forth. This will further increase the reliability of the toothed disk freewheel.

[0084] For reinforcement a radial bulge 33 may be provided as is presently illustrated in broken lines. The bulge 33 may be configured inwardly at the hub axle 2. It is also possible to provide the bulge 33 radially outwardly.

[0085] The clamping forces in the frame are dissipated by the inner rings of the bearings 27, the sleeves 36 and 37 and by a part of the hub axle 2 into which the clamping force is introduced and outlet through radial bulges on the bearings 27 for supporting the hub shell 3. The clamping forces are outlet at the outwardly ends through the adapter rings 28 and 29.

[0086] In the FIGS. 4 and 5 the toothed disk freewheel is illustrated in an enlarged cross-section or in an enlarged, exploded view for better illustration of the details.

[0087] FIG. 4 shows the region of the threaded ring 32 in an enlarged illustration. Additionally and again enlarged, a detail showing the multiple threads 34, 35 in the threaded ring 32 and the hub shell 3 is illustrated. By way of their thread grooves 34a and 34b, the two multiple threads 34, 35 engage the thread grooves 35a and 35b in the hub shell to securely receive the threaded ring 32 in the hub shell. Presently, the thread 34 with two thread grooves 34a, 34b extends over a considerable portion of the width 32a of the threaded ring 32, along a helical line 62 showing three full revolutions 62c each, which engage in the continuous thread grooves 35c of the thread 35 of the hub shell 3. The multiple threads 34, 35 provide for reliable guiding and secure retention of the threaded ring 32 in the hub shell 3.

[0088] In the lower right corner of FIG. 4 a possible embodiment of the threaded ring 32 is shown, where the thread 34 only comprises two full revolutions 41 and 42.

[0089] As can be clearly seen in FIG. 4 the threaded ring shows at its axially outwardly end a slightly enlarged (and here) circumferential flange 38 at the axially inwardly end of which a stopper 38a is formed which rests against a corresponding stopper 39a of a radial shoulder 39 in the hub shell 3. This configuration results in a (narrower) gap 40 remaining at the inner axial end of the threaded ring between the inner axial end of the threaded ring 32 and the body of the hub shell 3. This configuration again contributes to limiting the axial forces acting on the hub shell.

[0090] FIG. 5 is an exploded view, wherein the outer radius 14 of the axial toothings 18 is not larger than double the axial width 13 of the toothed disks 16, 17. The size of the axial width 13 of the toothed disks 16, 17 is at least 30 % or 40 % or half the outer radius 14 of the axial toothings 8 respectively 9.

[0091] FIG. 5 shows two simplistic thread grooves 34a and 34b on the outer surface of the threaded ring 32, which combined form a multiple thread 34 with two separate thread grooves 34a, 34b, each with three continuous thread grooves 34c.

[0092] FIG. 6 shows another exemplary embodiment of a hub 1 according to the invention, which is configured substantially the same as is the hub according to the invention according to FIG. 3. Therefore, like or similar parts are provided with the same reference numerals.

[0093] The hub 1 in the exemplary embodiment according to FIG. 6 is provided with a hub axle 2 and a hub shell 3 equipped with hub flanges 26. The hub shell 3 is supported rotatably relative to the hub axle 2 through two bearings 27. The rotor is likewise rotatably supported relative to the hub axle by means of two bearings 27.

[0094] Between the hub shell 3 and the rotor 4 a freewheel 5 is provided which in turn comprises freewheel components 6 and 7. A contactless and/or contacting sealing may be provided between the rotor 4 and the hub shell 3.

[0095] In this exemplary embodiment the freewheel components 6 and 7 are not configured identical but differently. While the freewheel component 6 is configured as a toothed disk 16, the freewheel component 7 is configured as an end toothing at (in particular integrally with) one axial end of the rotor. In this way the axial end of the rotor 4 with the axial toothing 18 provided thereat is in engagement with the axial toothing 18 of the toothed disk 16.

[0096] The toothed disk 16 is biased in the axial direction toward the rotor 4 by a biasing device 11 presently configured as a coil spring such that the teeth of the axial toothings 18 are as a rule engaged with one another.

[0097] In the exemplary embodiment the bearings 27 provided to support the hub shell 3 adjacent to the toothed disk 16 are for example inserted by means of force fit.

[0098] In FIG. 3, a threaded ring 32 for receiving the toothed disk 16 is equipped with a multiple external thread 34 with two separate thread grooves 34a, 34b extending along a helical line 62 with three full revolutions 62c, which is screwed with a corresponding multiple internal thread 35 in the hub shell 3.

[0099] The enlarged details beneath FIG. 6 schematically show the region of the intermeshing multiple threads 34 and 35, wherein for the sake of simplicity two thread grooves are indicated at the threads 34 and 35. Again, the threads 34, 35 extend continuously, that is, uninterrupted, along a helical line 62 with three full revolutions 62c, around the outside surface of the threaded ring 32.

[0100] For better illustration, the threaded ring 32 with the one single helical line 62 and a separate helical line 62 (presently) showing four full revolutions 62c and the endpoints 62a, 62b, are once again illustrated separately in the lower left region of the FIG. 6, for better understanding. The first revolution 41, the second full revolution 42, the third full revolution 43 and the fourth full revolution 44 are indicated.

[0101] Again, the gradient of each of the thread grooves 34a, 34b and 35a, 35b, is twice that of a single thread, so that the forces acting on the threaded ring are largely transmitted in the peripheral direction of the threaded ring 32 into the hub shell 3, and wherein the moment of resistance of the hub shell 3 to torsion is larger than that to bending. However, due to the separate thread grooves 34a, 34b, the pitch of the thread 34 remains as low as that of a single thread. This leads to decreased axial loads acting on the hub shell 3 such that the wall thicknesses of the hub shell may be reduced. This allows to reduce the total weight and it is also possible to reduce air drag since for example the cross-sectional area may be reduced.

[0102] FIG. 7 shows an embodiment of the threaded ring 32 comprising four full revolutions 41, 42, 43 and 44 of the thread groove 34a. Specifically, the threaded ring 32 is provided with a thread 34 with the thread groove 34a. The thread groove 34a extends along a helical line 62 extending in the axial direction around an circumference 32b of the threaded ring 32. The helical line 62 shows less than five full revolutions 62c of the thread grove 34a.

[0103] FIG. 8 shows another embodiment of the threaded ring similar to that of FIG. 7. In this embodiment the threaded ring 32 comprises three full revolutions 41, 42 and 43 of the thread groove.

[0104] FIG. 9 shows a further embodiment of the threaded ring 32 comprising two full revolutions 41 and 42 of the thread groove.

[0105] On the whole the invention provides an advantageous hub 1 which provides a lower weight combined with increased rigidity and enhanced durability.

[0106] Basically, the thread of the threaded ring assumes three functions: [0107] transmitting the forces into the hub shell for driving, [0108] attaching the threaded ring in the hub shell, [0109] centering the freewheel component for accurate function.

[0110] In the present invention, the gradient of the thread is increased on the narrow threaded ring of the hub shell 3 compared to the prior art, so that a larger portion of the axial force acting on the threaded ring 32 and the hub shell 3, is derived in the peripheral direction of the hub shell 3, in which the moment of resistance to deformation is larger than in its axial direction, so that smaller wall thicknesses are feasible given large thread gradients.

[0111] Starting out from the known prior art, a skilled person will use for a screwed connection, a (metric ISO) standard/fine-pitch thread, to ensure safe function of the screwed connection. Basically, however, due to the narrow threaded ring 32 in conjunction with the centering function of the thread 34, 35, the skilled person would tend to use a fine-pitch thread showing a low gradient, so as to provide a thread flank with a large surface, given an appropriate length of thread engagement.

[0112] To reduce the weight respectively the wall thickness of the hub 1, the skilled person might reduce the gradient further, so as to (still) further reduce the width of the threaded ring. Alternately, he might reduce the wall thickness of the threaded ring 32, by matching the material used.

[0113] In any case, a skilled person would have strong reservations about providing the narrow threaded ring 32 with a thread 34, 35 showing a clearly larger gradient (in particular larger than for a standard thread with a regular gradient), since this would no longer allow to ensure safety of function of the screwed connection, and in particular sufficient length of thread engagement, thus securing retention of the threaded ring 32 in the hub shell 3.

[0114] In the present case this is possible only since, due to the dynamic load and deformation of the hub shell 3, in particular by means of a thread 34 having a very high gradient (in particular beyond the normalized standards), the narrow threaded ring 32 is permanently driven into the hub shell 3 where it is securely retained. Moreover, a multiple thread 34a, 34b increases this effect by way of increased friction, and additionally allows improved centering.

TABLE-US-00001 List of reference numerals 1 hub 28 adapter ring 2 hub axle 29 adapter ring 3 hub shell 30 seal 4 rotor 31 double flange seal 5 freewheel 32 hub component, threaded ring 6 freewheel component 7 freewheel component 32a width of 32 8 engagement component 33 bulge 9 engagement component 10 engagement position 34 thread 11 biasing device 34a thread groove 12 biasing device 34b thread groove 13 axial width 34c continuous thread groove of 34a, 34b 14 outer radius 15 radial extension 35 thread 16 toothed disk 35a separate thread groove 17 toothed disk 35b separate thread groove 18 axial toothing 35c continuous thread groove of 35a, 35b 19 inner diameter 20 radial leg 36 sleeve 21 axial leg 37 sleeve 22 outer diameter 38 flange 23 hub component 38a stopper 24 hub component 39 shoulder 25 outer radius 39a stopper 26 hub flange 40 gap 27 bearing 41 first revolution 42 second revolution 43 third revolution 44 fourth revolution 50 bicycle 51 front wheel 52 rear wheel 53 frame 54 fork 55 rear wheel damper 56 handlebar 57 saddle 58 battery 59 spoke 60 tire 61 rim 62 helical line 62a first endpoint 62b second endpoint 62c full revolution 100 vehicle