Patent Grant
11485173
The present invention relates to a hub for a vehicle, which in normal and regular proper use is at least partially muscle-powered, and in particular for bicycles, the hub comprising a hub shell which is in particular rotatably supported relative to a hub axle by way of two roller bearings disposed on opposite end regions of the hub shell. In an embodiment as a rear wheel hub, the hub comprises a rotor for non-rotatable arrangement of at least one sprocket. The rotor is rotatably supported on the hub axle by at least two rotor bearings. In the case of a rear wheel hub a freewheel device is provided between the rotor and the hub shell. In the case of a front wheel hub, a rotor and a freewheel device are not required as a rule.
In the field of high quality cycling, the stressability and weight play a major role. The users set great store by high-grade components where each gram of weight counts.
Document DE 94 193 571 U1 has disclosed a hub with a toothed disk freewheel for rear wheels. The toothed disk freewheel works fast and reliably and transmits the driving force from the rotor to the hub shell. Concurrently, the friction loss is comparatively low while the user is not actuating the pedals. In this toothed disk freewheel, a pair of toothed disks transmits forward rotational force of the rotor to the hub shell while in backpedaling, the teeth disengage axially. The known hub per se functions satisfactorily and is used in the area of sports and also in professional riding. However, there is the disadvantage that the high loads acting on the hub for example in uphill rides may generate bending moments in the hub so as to cause the toothed disk to slightly tilt which results in higher wear on the teeth, which are subjected to higher forces, so that durability is limited and the toothed disks require early replacement to avoid malfunction. Moreover the hub has a relatively high weight.
EP 1 121 255 B1 has disclosed a lightweight hub having a toothed disk freewheel and showing a still more reliable function wherein the teeth of the toothed disks are stressed more evenly. This hub for the rear wheel uses a pair of toothed disks for the freewheel, both of which are axially movable and are axially urged toward one another from the outside by means of a spring. The two toothed disks are thus floatingly supported and for example in case of the hub flexing or given other types of stresses they may show better positioning to one another so as to provide more even wear on the toothed disks and a particularly reliable operation. However, an even stiffer hub and a more lightweight hub are desirable.
EP 3 275 692 B1 has disclosed a hub for a rear wheel of bicycles showing increased stiffness and a lower total weight. To this end, a hub-side freewheel component provided with axial toothing is screwed into the hub shell. In the interior of the hub-side freewheel component, a bearing seat is configured for accommodating one of the roller bearings to support the hub shell. This allows an increase in the axial bearing distance of the two roller bearings used for supporting the hub shell, thus increasing the stiffness of the hub. Moreover, the wall thicknesses of the hub shell can be reduced so as to reduce the total weight of the hub. However, further weight reduction and increase of the stiffness are desirable.
It is therefore the object of the present invention to provide a hub for at least partially muscle-powered bicycles to allow more ease of constructing and optionally a still stiffer design.
A hub according to the invention is in particular configured as a bicycle hub and is provided to be used with an at least partially muscle-powered bicycle and comprises a hub shell and an axle device. The hub shell is supported by means of bearing devices to be rotatable relative to, and in particular (indirectly or directly) on, the axle device. At least one bearing device is configured as a roller bearing, comprising two bearing rings with rolling members disposed between. Between the bearing rings, at least one roller bearing receives a modular unit at which a sealing unit is configured, which is shaped in particular as a washer for laterally sealing the roller bearing, and comprising guide units laterally protruding inwardly from the modular unit, for guiding the rolling members.
The hub according to the invention has many advantages. The fact that the roller bearing comprises a modular unit which concurrently serves to guide the rolling members and to laterally seal the roller bearing outwardly and/or inwardly, enables a narrower construction of the roller bearing so as to save considerable weight. Reduction of the width of the roller bearing does not only allow to reduce the weight of the roller bearing itself and thus of the hub on the whole, but also to increase the lateral distance of the two roller bearings for supporting the hub shell relative to the axle device. This also provides a still stiffer hub which withstands increased loads and whose weight can be lower still. The compact structure of the modular unit including an in particular annular sealing washer and protruding laterally inwardly thereof, guide units for individually guiding the rolling members, enables a still more compact structure so as to still better utilize a tight mounting space. The hub volume may be reduced, so that aerodynamic drag is reduced as well. The wider support also positively influences the (lateral) stiffness of a wheel structured with a suitable hub.
A considerable advantage is also obtained by the fact that the hub according to the invention is provided for use in bicycles and bicycle-type vehicles. Thus, a bicycle wheel showing a circumference of ca. 2 m only rotates ca. 830 times per minute at a traveling speed of 100 km/h. This means that in real operation, the roller bearings in a hub operate as a rule at speeds of less than 1000 revolutions/min. This is considerably slower than in other technical fields where standardization tests for ball bearings are as a rule performed at speeds of 6000 revolutions/min. This is why less heat is generated in the interiors of roller bearings of bicycle hubs than in other applications involving higher rotational speeds, so as to allow using smaller dimensions and other materials.
Particularly preferably, the hub shows at least one narrow roller bearing and the axial width of the roller bearing is less than 1.7 times, and in particular less than 1.6 times the diameter of a rolling member of the roller bearing, in particular for increasing the axial distance between the roller bearings of the hub shell (and/or of a rotor) and to obtain a wider support.
Advantageously, for a wider support of the hub shell at least one roller bearing is configured narrow (or narrower) by way of configuring the guide units for guiding the rolling members and the sealing unit on one shared modular unit. Then, the shared modular unit in particular does not axially protrude beyond the bearing rings.
Particularly preferably, the roller bearings are disposed spaced apart as far as possible, and the hub shell has the widest possible support. To this end, the roller bearings are configured narrower by way of configuring the guide units for guiding the rolling members and the sealing unit on one shared modular unit accommodated radially between the inner ring and the outer ring. The inner ring and the outer ring preferably show the same width, any difference being preferably 0 or less than +/−1% or 2%.
In preferred specific embodiments, a bearing ring is configured as an inner ring and the other of the bearing rings, an outer ring. The rolling members are preferably accommodated axially between the modular units and, in particular, radially between the bearing rings. Deep-groove ball bearings are particularly preferably employed as roller bearings. Alternately, it is possible to employ a roller bearing in the shape of a separable ball bearing or the like.
The rolling members are preferably spherical in structure. The axial width of at least one or both of the bearing rings is preferably smaller than 1.7 times the diameter of a rolling member. Conventional, outwardly sealed deep-groove ball bearings, however, tend to show a ratio of the axial width of a bearing ring to the diameter of a rolling member of 1.8 or even 2.0 or more. The narrower structure and a reduction of the ratio from 2.0 to 1.7 or lower allow saving more than 5% weight. This is quite a lot in the field of high-quality bicycle components. Preferably the axial width of the roller bearing is smaller than 1.7 times (or 1.6 times) the diameter of a rolling member.
Particularly preferably, the ratio of the axial width of a bearing ring to the diameter of a rolling member is between 1.2 and 1.6 and particularly preferably between 1.4 and 1.6. Particularly preferably, the ratio of the axial width of the roller bearing to the diameter of a rolling member is between 1.2 and 1.6 and particularly preferably between 1.4 and 1.6.
Preferably, the sealing unit contacts, resting (in the radial direction) against, at least one bearing ring for sealing. Particularly preferably, the sealing unit contacts, resting (in the radial direction) against, both of the bearing rings for sealing. Preferably, the bearing rings protrude axially outwardly to both sides beyond the modular units. Particularly preferably, the modular units do not axially protrude beyond the roller bearing.
In advantageous configurations, the modular unit comprises an annular unit. The annular unit is, in particular, connected in particular integrally with the sealing unit configured in a washer shape. Particularly preferably, the sealing unit is a seal against at least one bearing ring.
Particularly preferably, the entire modular unit is configured of a single material or at least one-piece. In preferred configurations, the entire modular unit is substantially or completely made of one material.
Preferably, at least one roller bearing (and in particular all of the roller bearings) comprise(s) two modular units each, other than the bearing rings and the rolling members. The modular units are in particular provided on opposite axial sides of the roller bearing. It is particularly preferred for the modular units to show a narrow axial distance from the pertaining axially outside surface of the roller bearing. The modular units may, for example, show an axial distance between 0.1 and 1.5 mm from the axially outermost end. Thus, it is ensured that any components bearing against the bearing rings do not directly press on the modular units, which might cause increased friction.
It is possible and preferred for the two modular units to interlock by way of click elements (configured on the modular units). To this end, suitable projections on click elements may lock into depressions or recesses to interconnect the two modular units. Alternately, it is possible to (lock and) retain the two modular units on the roller bearing via the rolling members. Thus, a modular unit may partially enclose individual rolling members by means of the guide units from one side, and the other modular unit may partially enclose individual rolling members from the other side. Alternately, it is possible for the two modular units to interlock by means of click elements on one side, and to be retained on the roller bearing by means of the rolling members on the other side. Preferably, the guide units are at least partially resilient, locking in the final position during mounting.
In particular, at least some of the guide units extend at least partially in the axial direction over between 45% or 50% or 55% and 80% of the axial width of at least one bearing ring. In particular, at least some of the guide units extend in the axial direction over between 60% and 70% of the axial width of at least one bearing ring. In the case that each of the two guide units extend from what is the other side, for example over 65% in the axial direction, an overlap of 30% ensues. Optionally more, if the modular unit shows an axial distance from what is the axially outside surface of the bearing ring.
In preferred configurations, the guide units show rounded and, in particular, spherical or cylindrical guide surfaces facing away from one another, for rolling members. One rolling member each is in particular guided on the guide surfaces facing away from one another. Thus, one rolling member each is guided on one guide surface of the two outside surfaces of a guide unit. It is possible and preferred for one guide unit to comprise two guide members (axially) protruding from the modular unit, between which a recess is configured for example in the shape of a groove or the like. Thus, the weight is reduced and manufacturing is simplified. This guide unit also guides two rolling members.
In advantageous embodiments, the interior of the guide unit shows at least one recess and/or at least one hollow space. This allows for one, to reduce the weight and for another, to simplify manufacturing since the flow characteristics of the materials can be better taken into account for manufacturing the modular unit.
In advantageous specific embodiments, an axial elevation for separating the rolling members is configured between two guide units on the axially inside surface of the annular unit. A number of guide units is distributed over the circumference of the annular unit. Preferably, each of the guide units shows on its circumferentially outside surfaces, one guide surface each for guiding one of the rolling members. Due to this, two rolling members are disposed between two circumferentially adjacent guide units which are reliably separated by the axial elevation. Dedicated guide surfaces may be configured on the axial elevation.
In particularly preferred specific embodiments, the two modular units are identical in construction. This simplifies manufacturing and assembly and storage. Particularly preferably, the two modular units interlock at an offset when mounted. Connecting the two modular units is not required. The feature of the two modular units interlocking at an offset, preferably means firstly, that a guide unit of one of the modular units is positioned between two guide units of the other modular unit during mounting. Thus, the guide units of the two modular units alternate over the circumference. It is in particular possible and preferred that on one of the sides of each rolling member, one guide unit of the one modular unit provides a guide surface for the rolling member, while on the other side of the rolling member, a guide unit of the other modular unit forms a guide surface for the same rolling member. All of the rolling members are in particular provided with a guide surface of one of the modular units on one circumferential surface, and a guide surface of the other of the modular units, on the other circumferential surface.
Preferably, at least during mounting, a device is disposed between the guide units which brings the rolling members to the correct position during assembly of the roller bearing (at least while inserting the sealing units). Mounting is thus simplified.
In preferred configurations, the modular unit consists at least partially and in particular nearly completely or entirely of plastics and particularly preferably of a polyamide. PA66 is particularly preferably used.
Using polyamide is also possible because relatively low speeds of a maximum (as a rule) of less than 1000 revolutions/min is reached. In this way, even in high traveling speeds of a bicycle, the waste heat generated in the roller bearings is relatively low, so that materials such as polyamide or like or similar materials are suitable for forming the guide units and also for forming sealing lips of the sealing unit of the modular unit.
Preferably, at least one bearing ring consists at least partially of steel or at least partially of ceramics. It is also possible to use a metal-matrix composite for the bearing rings and optionally also for the rolling members. Such a composite consists of a continuous metal matrix together with an in particular discontinuous ceramic or organic reinforcement in their interiors. The reinforcement may comprise reinforcing elements in the shape of fibers or whiskers. Reinforced aluminum, reinforced magnesium and copper materials and in particular titanium or steel may be used. The matrix is, in particular, an elemental metal or preferably an alloy. For the reinforcing phase, for example ceramic particles (e.g. silicon carbide), short fibers, continuous fibers (based on carbon) or open-pored foams may be used.
It is also possible for at least one bearing ring to be configured as a hybrid bearing ring consisting at least partially of steel and at least partially of ceramics. Both of the bearing rings may be configured as a hybrid bearing ring. Partially or completely using ceramics allows further weight reduction. Particularly preferably, the rolling members consist at least partially and in particular completely of steel.
In all the configurations, it is particularly preferred for the sealing surfaces of the bearing ring to be ground. This means that the sealing unit is in rubbing contact with the radially inwardly and the radially outwardly sealing surfaces, bearing against the inner respectively outer bearing ring, where little friction occurs. This allows permanent operation and achieves high stability under load. The low friction between the contacting sealing surfaces and the inner and outer bearing rings ensures a high degree of seal tightness combined with low friction.
Preferably, the interior of the roller bearing, between the sealing units of the two modular units, is provided with a quantity of lubricant sufficient for lubricating the rolling members over the service life of the roller bearing. This eliminates servicing of the roller bearings. In the case of wear or defects, the entire roller bearings can be exchanged.
In specific embodiments, the axial width of at least one of the roller bearings, given an external diameter between 20 mm and 40 mm, is less than 6.5 mm and in particular less than 6 mm. Particularly preferably, the axial width of at least one of the roller bearings is <6 mm, given an external diameter of the roller bearing between 24 mm and 30 mm. For example, given an external diameter of 24 mm or 25 mm, the axial width of the roller bearing may be between 5 mm and 6 mm and in particular 5.5 mm+/−0.1 mm.
Preferably, at least one of the roller bearings is designed for a speed of less than 2000 revolutions/min and in particular for a permanent speed (in operation) of less than 1500 and preferably less than 1000 revolutions/min. Particularly preferably, the axle device comprises a hollow axle as the hub axle. The hollow axle in turn allows passing through a quick release when mounting to the bicycle. Such a quick release may show a thin quick release axle or a thicker through axle.
Preferred more specific embodiments provide for the hub to be configured as a rear wheel hub. Preferably, the hub comprises a rotor rotatably supported relative to the hub axle by means of at least two rotor bearings configured as roller bearings. A freewheel device having two interacting freewheel components is in particular provided namely, a hub-side freewheel component and a rotor-side freewheel component. The two freewheel components each preferably comprise axial engagement elements and they are movable relative to one another in the axial direction at least between a freewheel position and an intermeshing engagement position. The hub-side freewheel component preferably provides for defined accommodation of a rolling member to support the hub shell relative to the axle device respectively the hub axle. The hub shell preferably includes an attachment portion and a centering portion. An attachment region and a centering region are in particular configured in the hub-side freewheel component. Particularly preferably, the attachment region is connected with the attachment portion and the centering region is centered at the centering portion. This provides high stability and stiffness combined with a low weight rear wheel hub. Moreover, reliable mounting can be ensured.
Particularly preferably, a hub configured as a rear wheel hub comprises a freewheel device with two freewheel components. At least one of the freewheel components preferably forms part of a freewheel unit. The freewheel comprises a freewheel component, a support unit and at least one spring unit. The freewheel component preferably comprises a tubular body section extending around a central axis and configured hollow, showing a non-round outer contour for non-rotatable and axially displaceable coupling, and a front surface with axial engagement components. The spring unit preferably urges the freewheel component and the support unit apart in an axial direction of the central axis. The freewheel component, the support unit, and the spring unit in particular form a pre-assembled module. The spring unit is attached to the freewheel component and to the support unit.
A hub having such a freewheel unit forming a pre-assembled module, allows reliable and reproducible mounting. This allows a reduction in required tolerances, so that even some wall thicknesses can be reduced, thus reducing the total weight.
In preferred configurations of a hub according to the invention, the hub comprises a hub shell which is supported for rotation relative to the axle device by means of bearing devices configured as hub bearings. This hub comprises a rotor with at least two rotor bearings that is supported for rotation relative to the axle device, and a freewheel device with two interacting freewheel components, a hub-side freewheel component and a rotor-side freewheel component, wherein the two freewheel components each comprise axial engagement elements and are movable relative to one another in the axial direction at least between a freewheel position and an intermeshing engaging position, wherein in the engaging position a driving torque can be transmitted in a direction of drive rotation. The hub-side freewheel component comprises an axial, threaded body section and is screwed into the hub shell by means of a thread. The hub-side freewheel component comprises an annular surface on which the axial engagement elements are formed at least in part. The rolling members of a hub bearing are located in a defined accommodation within the hub-side freewheel component to support the hub shell relative to the axle device. The hub-side freewheel component comprises at least one tool contour configured for coupling with a matching tool for unscrewing the hub-side freewheel component from the hub shell.
In another specific embodiment, and configuration of the hub, the hub shell is supported for rotation relative to the axle device by means of bearing devices configured as hub bearings. The hub comprises a rotor with at least two rotor bearings supported for rotation relative to the axle device, and a freewheel device with two interacting freewheel components, a hub-side freewheel component and a rotor-side freewheel component, wherein the two freewheel components each comprise axial engagement elements and are movable relative to one another in the axial direction, at least between a freewheel position and an intermeshing engaging position. The hub-side freewheel component provides for defined accommodation of rolling members to support the hub shell relative to the axle device. An attachment portion and a centering portion are configured in the hub shell, and an attachment area and a centering area are configured on the hub-side freewheel component. The attachment area is connected with the attachment portion and the centering area is centered on the centering portion.
A considerable advantage of the hub according to the invention is the simple construction and the weight advantage obtained by the construction.
The modular units are preferably accommodated between the bearing rings. Particularly preferably, one sealing unit each, in particular washer-shaped, is formed on a modular unit for laterally sealing the roller bearing.
In all the configurations, the modular units of the roller bearings of the hubs provide a combined sealing and guiding device. In this respect, the term “modular unit” may be continuously replaced by the term “combined sealing and guiding device”.
The modular units are in particular radially disposed between the bearing rings. The modular unit is preferably provided with an annular sealing washer each for laterally sealing the roller bearing. Guide members protrude in particular laterally inwardly respectively guide members project laterally inwardly from the modular unit or the sealing washer so as to guide the rolling members.
The guide units of a modular unit, and in particular, of both of the modular units combined also form a cage respectively two cage units by means of which the rolling members are retained between the bearing rings spaced apart from one another.
The sealing unit bears against, making contact with, at least one and preferably both of the bearing rings, at least in sections and particularly preferably in its entirety. This reliably seals the roller bearing axially outwardly.
On the whole, the width of the bearing rings of the roller bearings can be reduced. This provides more lightweight hubs. Bearings can be arranged in a hub with a higher degree of freedom. It is also possible to increase the system stiffness combined with a reduced total weight. The width of the roller bearings can be reduced by more than 10% and in particular by 15% or ca. 20%. For example, the presently used bearing rings showing 7 mm width can be reduced to a width of ca. 5.5 mm.
Due to the narrower roller bearings, a hub can be provided showing an increased distance of the roller bearings for supporting the hub shell and/or the rotor. Given a mounting width of a front wheel hub of e.g. 110 mm, an enlargement of the roller bearing distance by 3 mm is quite a considerable enlargement. In the case of a rear wheel hub, this applies even more, although the mounting widths may be e.g. 130 mm or 150 mm. In the case of rear wheel hubs, the rotor and the freewheel constrict the space available still more, so that enlargement of the bearing distance involves great advantages.
Due to the relatively low maximum speed of the roller bearings for the hubs according to the invention, metal cages do not need to be used for the rolling members of the standardized deep-groove ball bearings. This allows for a one-piece modular unit which takes care both of inwardly and outwardly sealing and of positioning each of the rolling members.
Each of the modular units in particular guides one half of the rolling members and in particular the balls and preferably retains them in position.
Further advantages and features of the present invention can be taken from the exemplary embodiments which will be discussed below with reference to the enclosed figures.
The figures show in:
The
A bicycle 100 comprises a frame 103, a handlebar 106, a saddle 107, a fork or suspension fork 104 and in the case of the mountain bike, a rear wheel damper 105 may be provided. A pedal crank 112 with pedals serves as a drive. Optionally, the pedal crank 112 and/or the wheels may be provided with an electrical auxiliary drive. An auxiliary drive may be accommodated in the bottom bracket or e.g. in the seat tube, visible from the outside or invisible. The battery may likewise be accommodated inside the frame. The hubs 1 of the wheels may be attached to the frame by means of a through axle or a quick release 49.
With reference to the
The hub 1 according to the invention illustrated in
The hub 1 furthermore comprises a rotor 8 on which to dispose at least one sprocket. In particular, a sprocket cluster may be pushed on and attached or arranged. A freewheel device 9 including two freewheel components 10, 20 is provided between the rotor 8 and the hub shell 2. The hub-side freewheel component 10 and the rotor-side freewheel component 20 are comprised. The rotor-side freewheel component 20 is part of a freewheel unit 81.
To prevent entry of water and dust into the interior of the hub 1 and in particular admission of water and dust to the freewheel device 9, a sealing device 38 is configured between the rotor 8 and the hub shell 2, comprising a labyrinth-like sealing gap and a downstream lip seal contacting the rotor 8 and reliably protecting the freewheel 9 from entry of dirt and water.
Limit stops 39 and 40 are pushed onto the two ends of the hub axle which—in particular, while the wheel equipped therewith is not clamped in the frame—are secured on the hub axle by way of O-rings 48. The limit stops 39 and 40 are each provided with a sealing flange 46 or 47 protecting the ends of the hub 1 from entry of dirt and water. This rotor-side limit stop 40 is provided with a radial sealing flange 47 while the other limit stop 39 is provided with a double flange 46 consisting of a pair of circumferential radial sealing flanges between which an axial distance and free space is formed.
The two limit stops 39 and 40 are each provided with a taper 25 which serves as a recessed grip and simplifies pulling a limit stop 39, 40 off of the axis 5 after removing a wheel.
The roller bearings 14, 24 for rotatably supporting the hub shell 2 rest in the axial direction on radial shoulders of bulges 43, 44 of the hub axle 5. The bulges 43 and 44 are each located axially inwardly of the (hub shell) roller bearings 14, 24. The roller bearings 14, 24 show an axial width 14a respectively 24a each.
In all the configurations of the hub 1, the bulges 43, 44 preferably show a somewhat larger radial wall thickness of the hub axle 5. In particular, is the radial wall thickness in the region between about 1.5 times and three times the radial wall thickness in the other regions. Other than the bulges 43, 44 the hub axle 5 is substantially a hollow cylinder in configuration and shows differences in the wall thickness of preferably less than 20% and in particular, less than 15% or less than 10% or less than 5% or less than 2%. Preferably, the relation of the maximum outer diameter of the hub axle (including bulge) to the minimum inner diameter of the hub axle is less than 2.0 and, in particular, less than 1.75 and preferably less than 1.6. Preferably, the relation of the maximum outer diameter of the hub axle to the minimum inner diameter of the hub axle is larger than 1.25 and in particular larger than 1.4. Preferably, the inner through hole of the hub axle is cylindrical in configuration and comprises a constant clear inner diameter over at least a substantial portion of the length or over the entire length.
The rotor 8 is supported, in this case directly, on the axle 5, rotatable via two roller bearings 6 and 7 which serve as rotor bearings.
The roller bearing 14 is accommodated inwardly of the hub-side freewheel component 10 in a central receiving space 11 in a defined location on a bearing seat 12. This saves considerable axial mounting space so that the stability and stiffness of the hub can be increased. Moreover, the total weight of the hub 1 is considerably reduced. Both the weight of each of the freewheel components and the weight of the hub shell can be reduced since the wall thickness in the rotor-side end region 4 of the hub shell 2 can be reduced.
The hub-side freewheel component 10 shows in radial cross-section an approximately L-shaped configuration where an axial and tubular body section 13 has a single-thread and presently preferably multiple external thread 10c in an attachment area 10a that is screwed into a corresponding (single-thread or multi-thread) internal thread 2c in the attachment portion 2a in the hub shell so that the freewheel component 10 is axially fixedly, and in the driving direction non-rotatably, connected with the hub shell 2.
The small detail on the bottom left in
The centering portion 2b in which the centering area 10b of the hub-side freewheel component 10 is received in a close fit serves for defined radial positioning of the hub-side freewheel component 10 and the roller bearing 14 accommodated therein. In particular is the fit nearly without play. An interference fit may be provided so that the hub-side freewheel component 10 is pressed into the hub shell 2 during screwing in.
A cylindrical bearing seat 12 is formed radially inwardly of the axial body section 13 where the rotor-side roller bearing 14 is accommodated to rotatably support the hub shell 2. When the roller bearing 14 is mounted it is form-fittingly accommodated with its inner ring 61 in the axial direction between the bulge 44 and the sleeve body 41.
The force-fit in the axial direction 30 is effected from the limit stop 40 via the inner ring of the rotor bearing 7, the sleeve body 42, the inner ring of the rotor bearing 6, the sleeve body 41, the inner ring of the roller bearing 14 and it is then introduced via the radial bulge 44 into the hub axle 5 from where it is transmitted via the radial bulge 43 to the inner ring of the roller bearing 24 from where the clamping force is ultimately dissipated via the limit stop 39.
In the mounted state, the inner end of the hub-side freewheel component rests against a radial shoulder 36 within the hub shell 2. In the mounted state, the outer ring 60 of the roller bearing 14 also rests against this shoulder 36.
The roller bearing 14 shows a free distance 16a from the inside surface of the annular flange 18 of the hub-side freewheel component 10.
The roller bearings 14, 24 and presently also the rotor bearings 6, 7, are each provided with two modular units 70 including a sealing unit 71 each for sealing the roller bearings and each including a number of guide units 72 for individually guiding the rolling members. The roller bearings 14, 24 and the rotor bearings 6, 7 each comprise rolling members 53.
A multiple thread connection between the hub shell and the hub-side freewheel component 10 is advantageous since it exerts less axial forces on the hub shell than does a single-thread screwed connection showing the same pitch. The reason is that the gradient angle of the thread groove is considerably larger so that smaller axial forces result. Disassembly is also facilitated since self-retention is lower. Due to the lower axial forces, the hub shell is subjected to lower loads. The wall thicknesses can be reduced while durability is increased.
The rotor-side freewheel component 20 comprises on its front face 22 a rotor-side annular flange 28 on which the engagement components 33 are configured. The rotor-side annular flange 28 is in particular configured integrally with the tubular body section 23.
The roller bearing 14 (and the other roller bearing 24 for supporting the hub shell 2) comprise(s) an inner ring 61 and an outer ring 60. The roller bearings 14, 24 are configured as deep-groove ball bearings showing, radially between the bearing rings 60, 61, a number of rolling members 53 designed as balls. For laterally sealing and for guiding the rolling members 53, modular units 70 are provided to the right and the left on the axial sides of the roller bearing 14 so as to seal off the interior of the roller bearing 14 while simultaneously guiding, respectively retaining in position, the rolling members 53.
To this end, the modular units 70 are axially approached from the side concerned and the guide units 72 axially protruding from the annular sealing unit 71 are introduced between the bearing rings 60, 61 respectively they are mounted so that the guide members 76, 77 of the guide units 72 guide one ball each on the guide surfaces 76a, 77a. Since each of the modular units 70 is provided with a plurality of guide units 72 (presently, five each), a corresponding number of rolling members may be guided. Overall, there are ten guide units for guiding a total of 20 rolling members. The modular units 70 are mounted such when mounting the roller bearings so as to leave a slight lateral clearance up to the axial outer edge of the bearing rings. This prevents the modular units 70 from protruding axially outwardly. The radially outer surfaces and inner surfaces of the sealing unit 71 bear against, making contact with, the pertaining inner sealing surface of the outer ring 60 and the outer sealing surface of the inner ring 61. To this end, the corresponding sealing surfaces of the bearing rings 60 and 61 are ground so as to reduce friction.
An axially reproducible positioning of the modular units 70 is ensured by the guide surfaces 76a and 77a of the guide members 76 and 77, which grip respectively guide the rolling members 53 resiliently, so as to provide a sufficiently firm seat of the modular units 70 on the roller bearing 14 (respectively 24, or 6, 7).
This construction noticeably increases the distance 26 between the roller bearings 14, 24 for supporting the hub shell. The distance 27 between the rotor bearings 6 and 7 can likewise be clearly increased. This increases the stability and stiffness of the hub 1 on the whole.
The enlarged detail on the bottom right in
This freewheel component 20 shows an approximately L-shaped configuration in radial cross-section. The long leg of the “L” is formed by the tubular body section 23. The short leg of the “L”, presently facing radially inwardly, is formed by the front face 22 of the freewheel component 20. The front face is provided with the engagement components 33. A takeup tab 86 is disposed axially rearwardly on the annular flange 18 which provides on its front the front face 22 and in this case is in particular configured as a circumferential takeup flange 86. The takeup flange 86 extends from the axially inside surface of the annular flange (also denoted front flange) sleeve-like rearwardly. The sleeve-like body extends approximately concentric to the tubular body section 23. The takeup flange 86 may be cylindrical but it may show conical sections to e.g. facilitate pushing on or to ensure a better hold.
An accommodation section 82 for fastening the spring unit 32 is provided on the radially outside surface of the circumferential takeup flange 86. The spring unit 32 is pushed with a coil end or coil portion onto the takeup flange 86 where it is retained in a force fit. For better gripping, the front end of the spring unit 32 may be bent radially inwardly or outwardly to achieve a firmer grip on the takeup flange 86. To this end a length of 2 to 5 mm may be slightly bent over at the coil end.
On the radially outside surface and/or inside surface of the circumferential takeup flange 86, a circumferential recess may be configured which serves as a form-fit accommodation of the end of the spring unit 32.
At the front end the spring unit 32 is typically supported over at least part of the circumference on the inside surface (supporting surface) 22a of the annular flange 18.
At the other end of the spring unit 32, at least part of a coil 32a or at least a coil end 32b is supported on the support unit 84 which comprises a support disk 88 and a support tab 89. The support tab 89 may be configured as a circumferential support flange. On the radially outside surface, at least one coil portion of the spring unit 32 rests against the support tab respectively the support flange 89 in a force fit and/or form fit. Clamping can be achieved by way of the diameter of the spring unit 32 being slightly smaller than the outer diameter of the support flange prior to mounting. Alternatively, it is possible for the end of the coil to be slightly bent radially inwardly to achieve better clamping. It is also possible for the support flange to show a (an at least partially) circumferential recess in which the end of the spring unit 32 is received in a form fit.
The support unit rests, for example, on a radial shoulder 35 in the rotor 8 on the axially outside surface to enable reliable dissipation of the forces occurring. When manufacturing the rotor and forming the non-round inner contour 37 of the rotor, which enables a non-rotatable accommodation and axial displaceability of the rotor-side freewheel component 20, an undercut in the shape of a groove 91 is as a rule inserted. The groove 91 axially follows the non-round inner contour 37 and is finally delimited by the shoulder 35. A ring 92 for centering the support unit 84 may be received in the groove 91 as is shown in the bottom half of
The bearing rings 60 and 61 each show the same axial width 60a respectively 61a, corresponding to the axial width of the roller bearing 14. A broken line exemplarily shows a width 14b of a roller bearing of a prior art hub. The axial width 14a, which is narrower than the width 14b, allows to (suitably) increase the axial distance between the two hub bearings 14, 24.
It is assumed that what in the
In analogy, the axial distance between the two hub bearings 6, 7 can be (suitably) increased. The wider support and the narrower roller bearings enable a more stable structure of the hub and a lower weight of the hub.
One can clearly identify the radially outwardly sealing surface 71a and the radially inwardly sealing surface 71b of the sealing unit 71. Each modular unit 70 comprises an annular unit 71, the cross section of the sealing unit 71 tapering radially outwardly and radially inwardly so as to maintain the lowest possible friction of the contact surface against the bearing rings. The contact surfaces 60b and 61b on the bearing rings 60 and 61 are ground to ensure low friction.
Also shown is the presently identical axial width 60a, 61a of the bearing rings 60 and 61, and also the axial width 53a respectively the diameter 53a of the rolling members 53. The ratio of the axial width 60a to the diameter 53a is 1.55. Optimization may further reduce this ratio. This reduces weight still further.
The components of the freewheel unit 81 which together form the assembly 83 are shown enlarged beneath. The freewheel unit 81 consists of the freewheel component 20, the spring unit 32 the coil ends 32b of which can be recognized, and the support unit 84, which when assembled result in a preassembled assembly 83 which is inserted into the hub as a whole in mounting.
The roller bearings 14, 24 and the roller bearings 6, 7, which are located inside the rotor, are configured according to
At any rate the freewheel unit 81 comprises a freewheel component 20, a spring unit 32 and a support unit 84, combined to form an assembly 83. The spring unit 32 is fastened at a first end on an accommodation section 82 of the freewheel component 20. The accommodation section 82 may be configured on a circumferential takeup flange 86.
It is also possible for the accommodation section 82 to consist of multiple part sections configured on individual takeup tabs 86 which are disposed over the circumference of the freewheel component 20. Takeup tabs or accommodating members 86 may for example be present in specific angular sections. Individual accommodating members 86a are shown on the right half in
It is also possible for a takeup tab or a circumferential takeup flange to be configured on a separate annular wall 87 disposed in parallel to, and spaced apart from, the front face 22. Instead of the annular flange 18 this annular wall 87 may serve to support and to attach the spring unit 32 secure against loss.
It is likewise possible for a circumferential support flange 89 to provide a circumferential support section 85 on the support unit 84, as is indicated in the left half of
The right half of
Various combinations of individual components and circumferential flanges are possible.
The back face of the support unit 84 shows an abutting surface 88a by means of which the freewheel unit 20 rests on the shoulder 35 in the rotor. This achieves exactly defined conditions.
As a rule, the spring unit 32 stays on the freewheel component 20 without any further means due to the matching dimensions.
Alternatively, it may be planned or unintended in the case of unfavorable tolerances, that the spring unit 32 does not adhere unassisted to the freewheel component 20. In these cases the end of the spring unit 32 may be fastened or “stuck on” by means of some lubricant 34 e.g. prior to mounting following maintenance or when initially mounting.
The lubricant 34 such as grease or the like may be fed e.g. locally (preferably over at least one section) into the circumferential groove between the takeup flange 86 and the inner wall 23a of the tubular body section 23.
A suitable quantity of lubricant 34 may also be applied on the support unit 84 to connect the spring unit with, or fasten it to, the support unit on its other end. It is also possible to apply a suitable quantity of lubricant 34 (only) to one end, or to both ends, of the spring unit.
The lubricant 34 is exemplarily shown in hachure in
The support unit shows a safety device 84a extending axially in the direction of the freewheel component and the freewheel component shows a protective device extending axially in the direction of the support unit, each so as to prevent an end of the spring unit from side-slipping inwardly. Otherwise the axially outwardly end of the spring unit 32 could come to rest on the sealing unit 71 at the rotor bearing 6 from
The protective device 20a at the freewheel component 20 comprises a takeup flange 86 or multiple accommodating members 86a preventing the spring unit 32 from side-slipping inwardly at its other end.
The protective device 20a and a safety device each extend over an axial length that is larger than half the diameter, and preferably larger than the diameter, of the body of a coil 32a of the spring unit 32.
In all the configurations, the ratio of the axial length of a freewheel unit 81 to the axial length of a freewheel component of the freewheel unit in the mounted state in a hub 1 is preferably less than 3:2 and, in particular, less than 4:3 and particularly preferably less than 5:4 or less than 6:5. This is advantageous since the freewheel component needs a certain length for axial guiding and on the other hand a shorter overall length enables improved support of a hub.
A part of a coil 32a of the spring unit 32 is clamped to a longitudinal section 23b on the inner wall 23a of the tubular body section 23 of the freewheel component 20. This accommodation section 82 is provided by the inner wall 23a in the longitudinal section 23b having a slightly smaller inner diameter 23c.
Additionally, the sleeve body 41 is shown which is located radially inwardly of the freewheel unit 81 including in the completely assembled state of a hub 1. The sleeve body 41 shows two diameter sections with the diameters 41a and 41b. At the ends the wall thicknesses are slightly less for saving weight. In the central region, the wall thickness is slightly larger.
In
At the axially inwardly end, the front end 13d of the axial body section 13 abuts against the radial shoulder 36 in the hub shell 2 so as to obtain a defined seat of the hub-side freewheel component 10.
The roller bearings 14, 24 rest axially inwardly against the radial bulges 43, 44 of the hub axle 5. Accordingly, the outer rings of the roller bearings 14, 24 rest against radial shoulders in the hub shell.
The roller bearings 14, 24 are each provided with a separate seal to prevent dirt and water from penetrating into the roller bearings. Moreover, the interior of the roller bearings contains a lubricant supply to provide reliable lubrication of the rolling members 53 over the service life of the roller bearings 14, 24.
Therefore, the seals for sealing the roller bearings 14, 24 for one, retain the lubricant inside the roller bearings and for another, prevent dirt and water from penetrating into the roller bearing.
The roller bearings 14, 24 are configured as described above. The top portion of
Sealing and guiding the rolling members is provided by the modular units 70, each of which is provided with an annular sealing unit 71 for sealing the roller bearings and with guide units 72 for guiding the rolling members.
The modular units 70 are configured integrally and preferably consist entirely of one material.
The weight of the hub 1 configured as a front wheel hub may also be reduced. Moreover the structural stiffness of the front wheel can be increased since the axial distance of the roller bearings 14, 24 can be increased.
The hub 1 according to the invention illustrated in a schematic cross-section comprises a hub shell 2 and a hub axle 5, onto the ends of which limit stops 39 and 40 are pushed. Roller bearings 24 respectively 14 serve to rotatably support the hub shell, and roller bearings are employed as rotor bearings 6 and 7 to rotatably support the rotor. All the bearings are configured as roller bearings, each being provided with pairs of modular units 70 for guiding the rolling members 53 and for axially sealing the roller bearings. The axial distance of the hub bearings 14 and 24 ensues from the shoulders on the radial bulges on the hub axle 5. A sleeve body 42 is disposed between the rotor bearings 6 and 7, and a sleeve body 41 is disposed between the rotor bearing 6 and the rotor-side hub bearing 14.
In this embodiment of a rear wheel hub 1, the roller bearings for supporting the hub shell are again structured relative to the hub axle as it is described above with reference to the hub according to
The construction of the roller bearings 14, 24 enlarges the axial distance between the roller bearings 14, 24 so as to increase the stiffness of the hub. At the same time, the weight of the hub shell can be reduced by way of reduced wall thicknesses. Weight is also saved by way of the reduced axial width of each of the roller bearings.
Spoke flanges 17 serve to attach spokes.
This freewheel device 9 comprises two identical freewheel units 81. Each of these freewheel units 81 comprises a freewheel component 10 respectively 20, a spring unit 32 and a support unit 84.
The spring unit 32 is fastened to the freewheel component 10 and 20 respectively and to the support unit 84 with its respective ends so as to result in a preassembled assembly 83 each.
The preassembly of the assembly 83 allows to enhance the quantity already when the hubs 1 are initially mounted. Moreover, increased reproducibility and quality is enabled in later demounting and subsequent re-mounting.
The floating mounting of the two axial toothings 33 achieves particular flexibility in adapting the freewheel device 9.
The hub-side freewheel component 10 is accommodated non-rotatably and axially displaceably in the threaded ring 29 that is screwed into the hub shell. The enlarged detail on the bottom left shows the presently screw-connected, multiple threads 29c and 2c. The threaded ring 29 shows the thread grooves 29e and 29f of the presently double external thread screwed to the thread grooves 2e and 2f of the hub shell 2. Again, a lower axial force acts on the hub shell 2 than when using a single thread.
The rotor-side freewheel component 20 is non-rotatably and axially displaceably accommodated in the rotor 8. To this end, the threaded ring 29 and the rotor 8, or the freewheel components 10 and 20, each show a matching non-round outer contour 21 and inner contour 37.
In all the configurations, a freewheel unit 81 provides a clearly defined support on both of its sides. Due to the configuration and fixing, the conditions hardly change at all in operation or only slightly. Absent fixing to the spring unit, a conventional freewheel shows changes to the pertaining supporting surfaces in operation due to changing roughness or wear. Such changes are undefined. A freewheel unit 81 according to the present invention always provides defined conditions so as to also achieve a longer service life.
The large diameter spring unit allows reliable and sufficiently strong biasing. A circumferential spring unit offers considerable advantages since it always responds precisely over the entire circumference.
In all the configurations, the hub allows increased lateral stiffness, an increased bending stiffness, and a still safe operation, and easier maintenance. At the same time, the weight may be reduced which is of particular importance in the area of sports and for professional use.
Another advantage is the smaller cross-section of the hub body which is thus aerodynamically better. The quantity of parts is smaller so as to make servicing, assembly and disassembly easier. Manufacturing the hub is also easier.
Another advantage can be achieved by multiple threads so as to result in reduced loads on the hub shell and reduced self-retention.
In all the configurations, it is preferred to employ ground inner bearing rings in the roller bearings. A ground outer ring may also be employed so as to obtain very low frictional coefficients.
While a particular embodiment of the present hub for an at least partially muscle-powered bicycle has been described herein, it will be appreciated by those skilled in the art that changes and modifications may be made thereto without departing from the invention in its broader aspects and as set forth in the following claims.
| Number | Date | Country | Kind |
|---|---|---|---|
| 102016113731.6 | Jul 2016 | DE | national |
| 102016113733.2 | Jul 2016 | DE | national |
| 102017116954.7 | Jul 2017 | DE | national |
| 102017116960.1 | Jul 2017 | DE | national |
| 102018101720.0 | Jan 2018 | DE | national |
| 102018116465.3 | Jul 2018 | DE | national |
| 102019127374.9 | Oct 2019 | DE | national |
| 102020103129.7 | Feb 2020 | DE | national |
The present application a Continuation-in-Part of and claims 35 USC 120 priority from U.S. patent application Ser. No. 16/862,816 filed Apr. 30, 2020, which is a Continuation-in-Part of U.S. patent application Ser. No. 16/503,110 filed Jul. 3, 2019; is also a Continuation-in-Part of and claims 35 USC 120 priority from U.S. patent application Ser. No. 16/255,231 filed Jan. 23, 2019, which is a Continuation-in Part of U.S. patent application Ser. No. 15/882,423 filed Jan. 29, 2018, now U.S. Pat. No. 10,625,540, which is also a Continuation-in-Part of both U.S. application Ser. No. 15/659,830 now U.S. Pat. No. 10,442,245 and Ser. No. 15/659,850, now U.S. Pat. No. 10,549,578 both filed Jul. 26, 2017; and is also a Continuation-in-Part of and claims 35 USC 120 priority from U.S. patent application Ser. No. 16/039,831 filed Jul. 19, 2018, which is a Continuation-in Part of U.S. patent application Ser. No. 15/882,423 filed Jan. 29, 2018, which is also a Continuation-in-Part of both U.S. application Ser. No. 15/659,830 now U.S. Pat. No. 10,442,245 and Ser. No. 15/659,850 now U.S. Pat. No. 10,549,578, both filed Jul. 26, 2017 all of which are incorporated by reference herein.
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| 102009038794 | Mar 2011 | DE |
| 102017116960 | Feb 2018 | DE |
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|---|---|---|---|
| 20210023878 A1 | Jan 2021 | US |
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