TW201940380A - Rear wheel sprocket arrangement having two integral partial arrangements connected to each other for joint rotation - Google Patents

Abstract

A bicycle rear wheel sprocket arrangement (30) which is rotatable about a common sprocket rotation axis (RA) defining an axial direction and radial directions orthogonal thereto, comprising a plurality of sprockets (R1 R12) of different size and number of teeth arranged coaxially with respect to the sprocket rotation axis (RA) and connected to one another for joint rotation about the sprocket rotation axis (RA), wherein the sprocket arrangement (30) has a first partial arrangement (32) comprising the largest sprocket (R1), and a second partial arrangement (34) comprising a plurality of sprockets (R3 R12) formed integrally with one another. According to the invention, it is provided that a partial arrangement (34) consisting of first and second partial arrangements (32, 34) has a plurality of elastically deformable latching formations (60c) which are in latching engagement with a plurality of mating latching formations (40) of the respective other partial arrangement (32), wherein the latching engagement secures the two partial arrangements (32, 34) against removal from each other in the axial direction.

Description

Rear wheel sprocket configuration with two integrated partial configurations connected to each other for joint rotation

The invention relates to a bicycle rear wheel sprocket arrangement capable of rotating about a sprocket rotation axis. The rotation axis of the sprocket defines an axial direction and a radial direction orthogonal to the axial direction. The sprocket rotation axis also defines a peripheral direction surrounding the sprocket rotation axis. The rear wheel sprocket configuration includes a plurality of sprocket wheels having different sizes and number of teeth. The sprocket wheels are arranged coaxially about the sprocket rotation axis and are connected to each other for rotation around the sprocket rotation axis joint. It has a first partial configuration including the largest sprocket, and a second partial configuration including a plurality of sprockets integrally formed with each other.

The invention further relates to a bicycle drive assembly, which comprises a bicycle chain and a bicycle rear wheel sprocket arrangement capable of transmitting positive locking engagement with the bicycle chain by driving force transmission. The bicycle chain has a plurality of rollers which are connected to each other in a manner known per se by pairing the outer and inner link plates along the longitudinal direction of the chain thereof. The rear wheel sprocket arrangement is designed as described in this case.

The type of bicycle rear wheel sprocket configuration in question, that is, as described in the first paragraph, has been found in DE 10 2015 205 736 A1. The type of bicycle drive assembly in question, that is, as described in the first paragraph, is also found in this document.

It has been seen since DE 10 2015 205 736 A1 that the sprocket configuration has a great spread, ie there is a great difference in the number of teeth between the smallest and largest sprocket. This also results in very different diameters for the smallest and largest sprockets. When the bicycle chain is engaged with the largest sprocket, the largest sprocket is therefore subjected to a considerable mechanical load. Based on the oblique position of the bicycle chain and the largest sprocket in positive locking engagement with respect to a longitudinal center plane of the bicycle orthogonal to the rotation axis of the sprocket, the largest sprocket not only carries the periphery of the bicycle chain at its radially outer sprocket Forces in the direction, and also bear forces acting in the axial direction, and because they act radially on the sprocket away from the rotation axis of the sprocket, they can bend around a rotation orthogonal to the rotation axis of the sprocket The shaft produces a considerable bending effect.

The sprocket configuration already seen in DE 10 2015 205 736 A1 has a first part configuration including only the largest sprocket, and a second part configuration connected to the first part configuration, and as an integrated chain Wheel cover with all other sprockets from the second largest sprocket to the smallest sprocket. A fastening pin projecting axially from the sprocket cover penetrates the fastening surface of the first part configuration, and particularly a fastening opening formed on the first part configuration for this purpose. The fastening surfaces are arranged here across a pair of sprocket spokes adjacent to the first portion adjacent in the peripheral direction to provide sufficient material to form the fastening openings.

The fastening pins are manufactured to have an oversize relative to the fastening openings. The fastening pins are fitted into the fastening openings with a press-fit. By the sudden axial deformation of the free longitudinal ends of the fastening pins in a direction towards the second part configuration containing them, the longitudinal end regions of the fastening pins fitted into the fastening openings are diameter Unfolding (in the form of shiitake mushrooms), and therefore, in addition to the press-fit, a positive locking effect of maintaining the second part configuration on the first part configuration is generated. These two-part configurations are therefore inseparably connected to each other, that is, cannot be separated without damaging the components or component parts.

However, the result is that the weakening of the fastening surfaces by the fastening openings formed therein, passing therethrough in the thickness direction, and containing therein fastening pins in the form of shiitake mushrooms, may cause action on the chain The forces and moments on the wheel configuration reach stress peaks during operation and as a result cause the formation of cracks and / or similar damage zones.

Therefore, the object of the present invention is to increase the mechanical strength of the sprocket arrangement mentioned at the beginning, so that the sprocket arrangement has a higher stability during the intended operation than the conventional sprocket arrangement of the prior art.

This object can be achieved according to the present invention, wherein one of the first and second partial configurations has a plurality of elastically deformable latches formed, and the elastically deformable latches are formed with individual other parts A plurality of matching latches are configured to form a latching engagement, wherein the latching engagement stabilizes the two parts configuration to prevent each other from being removed in the axial direction.

The term "latch" as used herein refers to a positive locking engagement that can utilize the elasticity of the materials and components formed by the latches, and optionally the elasticity of the materials and components formed by the matching latches, by These shaped elastic deformations occur. The latch can therefore be distinguished from the first and the second part of the connection by screwing or by a bolt-closing connection, wherein the forming system is not involved in a joint allowing only by the temporary elastic deformation of the forming Join.

By latching the two-part configuration to each other, the configurations are connected to each other to transmit a force acting along the rotation axis of the sprocket. The axial forces that occur during the intended operation of the sprocket configuration are caused by the chain deflection, which is caused when the rear wheel sprocket configuration has more sprocket wheels and more pedal links are provided on the pedal crank For the bigger. The axial force acting on a rear wheel sprocket arrangement during this intended operation cannot be ignored and should not be underestimated.

These latch shapes and mating latch shapes can be formed on individual component configurations without weakening a component portion, such as by removing material through conventional fastening openings.

In addition, by the latching engagement between the first and second part configurations, the first and second part configurations may not use a connection member formed separately from the first and second part configurations. Connecting to each other, such as screws, nuts and rivets, not only reduces the expenditure on installation of the sprocket arrangement, but also increases the strength of the assembly, as it is not necessary to provide abutment forming for separate connection members.

In principle, it is conceivable that at least one set of forming systems consisting of a latch forming and a matching latch forming is formed on a corresponding latch component or a matching latch component, the corresponding latch component or the matching latch component system Installed on the first or / and second part configuration. For the reason that the strength of a component is higher, the sprocket configuration according to the present invention better manages fewer mounting points and components, the better. Therefore, it is preferred that the latch shapes or / and the mating latch shapes are formed integrally with the individual partial configurations containing them. The two forming systems are preferably each formed integrally with the partial configuration containing them.

Even in the case of complex configurations involving these partial configurations, this integrated forming can be achieved by a multi-stage processing process that includes a major forming or / and early deformation phase and A metal cutting post-processing phase. For example, a component blank that is first used for the individual partial configuration may be cast or / and forged, before the component blank obtained in this way is obtained by metal cutting processing such as turning and milling to obtain its final configuration .

The latch joint is intended to be used to place the two involved components, that is, the first and second partial configurations, fixed relative to each other, not only in the axial direction, but preferably also in the radial direction and on the periphery. In at least one direction. This can be achieved in a simple but effective way, where the latches are formed with axial protrusions that protrude from the part configuration that contains them. According to their orientation and configuration, the axial protrusions can serve as mechanical stops in the axial direction, and preferably also in a direction orthogonal to the rotation axis of the sprocket, and therefore prevent the first The second part is arranged in the axial direction and preferably also moves relatively in a direction orthogonal to the rotation axis of the sprocket.

In order to fix the first and second part configurations in the axial direction relative to each other, the axial protrusions, which are fixed protrusions, can be arranged from the axial protrusions to self-contain their parts. At a certain axial distance from a root region of the protrusion, a latching lug protrudes from the individual axial protrusion in a peripheral direction around the rotation axis of the sprocket or / and in a radial direction. The latching lug can then be engaged behind a corresponding mating latch formation, and thus can limit the relative axial movement of the first and second portions disposed in at least one axial direction.

The axial fixing protrusions are preferably deformable in a direction orthogonal to the rotation axis of the sprocket, that is, deformed in a radial direction or / and a peripheral direction, preferably relative to it by one. Bendable deforms from its root region where it protrudes. They are preferably rigid in the axial direction so as to provide high stability forces in the axial direction.

An axial fixing protrusion can even completely suppress the axial relative movement between the first and second partial configurations, and therefore when the axial fixing protrusion maintains a match in a holding space in an axially delimited manner When the latch forms a fixed part, it is clear enough to fix the two parts configuration relative to each other, and the holding space is in a first direction by the latch tab and one with respect to the first direction The second direction is delimited by a retaining profile, the retaining profile being configured to have an axial distance from the latching lug and extend parallel to the latching lug. The holding shape may be any desired shape. Preferably, it is present in any case and the axial fixing projection protrudes from its axial direction away from the root region of the portion configuration to carry him. For example, an outer surface of the root region facing the latching lug may form an associated contact surface against which the fixing portion of the latching latch abuts, which is stabilized by the latching lug without being lifted. Up. Preferably, the plurality of axially fixing projections, particularly preferably all of the axially fixing projections, are designed in such a manner that they provide the above-mentioned holding space.

In order to fix the first and the second portion configuration in the radial direction and / or the peripheral direction relative to each other, the first or / and the second portion configuration may further have an axial protrusion as a stop. Stop protrusions, the stop protrusions have a stop surface facing an action direction, and the action direction has a contour component that is orthogonal to the rotation axis of the sprocket and matches the stop formation in each case The ministry abuts against it. Depending on whether a stop protrusion is intended to prevent relative movement of the two parts in the radial direction or the peripheral direction, the action direction is a radial direction or a peripheral direction. The action direction preferably has a plurality of contour components in both the radial direction and the peripheral direction, and therefore a stop protrusion can prevent or restrict the two parts from being disposed in the radial direction and the Relative movement in the peripheral direction. In principle, it should not be ruled out that the action direction also has a contour component in the axial direction, but the contour components in the action direction are preferably uniquely orthogonal to the sprocket rotation axis. This avoids the axial force on the blocking protrusions, otherwise the axial force will act on the two-part configuration.

In order to assemble these parts in a structure as simple as possible, at least some of the stop protrusions, preferably all of the stop protrusions, are formed in such latches. Forming, especially the configuration of the same parts of the axial fixing protrusions. In this case, the mating stop forming system that is in contact engagement with a stop protrusion is preferably a mating latch forming. The action directions of the blocking protrusions disposed at different positions of a part of the configuration preferably point to different directions locally, and each direction has a contour component orthogonal to the rotation axis of the sprocket or orthogonal to the rotation of the sprocket. Axially.

Thereby, it is possible not only to prevent relative movement of one of the two partial configurations in a radial direction or / and not only in a peripheral direction. At least one of the partial configurations preferably has a matching stop projection The matching stop protrusions have a matching stop surface facing a reverse action direction, and the reverse action direction has a contour component orthogonal to the rotation axis of the sprocket and a matching stop formation of an individual match stop system. Adjacent abut on it. The radial and negative contour components or / and the contour components adjacent to the same matching stop in the peripheral direction of the action direction and the counter-action direction of the stop surface and the matching stop surface are facing opposite directions. . The direction of the reverse action without an axial component only runs orthogonally to the rotation axis of the sprocket. The mating stop formation may further be a mating latch formation.

The matching stop projections are also preferably effective in the radial direction and the peripheral direction. The above mentioned about the blocking protrusions and their action directions are also allowed to be used for the matching blocking protrusions and their reverse action directions.

As the first and second part configurations are fixed to each other, the blocking protrusions and mating blocking protrusions ensure that the latch engagement once formed cannot be released again by the relative movement of the part configurations. In order to increase the operational reliability of the sprocket arrangement, the latching engagement is preferably a substantially non-releasable latching engagement, for example because of the large number of axially fixed projections that must all deform simultaneously. It can be released again by unreasonably high force.

The combination of the first and second part configurations having the above-mentioned latching engagement is preferably by a coaxial arrangement of the two part arrangements with respect to the common sprocket rotation axis, and by the axial direction The upward and preferably only occur in the axial direction by applying forces towards each other on the two-part configuration. The combination in which the axial fixing protrusion can be elastically deformed due to the latching lug provided may be convenient, because at least some of the matching stopping protrusions match the stopping protrusions, and Preferably, all of the matching stop projections have an inclined surface at a freely protruding longitudinal end thereof, wherein the matching stop surface is axially disposed between the inclined surface and the root region, and the Equally matching stop projections protrude from there. The side of the oblique surface is inclined in such a way that a point thereon migrates axially in the direction of the root region in the radial direction or / and in the peripheral direction close to the matching stop surface. The matching stop projections are preferably formed on the same portion configuration as the axial fixing projections and particularly preferably also as the stop projections.

When the pair of stopper protrusions and the matching stopper protrusions, among which the axial fixing protrusions can also be stopper protrusions, are configured in the following manner, that is, the ready-made latches arranged in these parts In the locked state, they maintain a matching stop formation therebetween, optionally in the form of a matching latch formation, between their stop surface and the matching stop surface, orthogonal to the rotation axis of the sprocket. There is no way of play in the direction, and the unique axial bonding force on one of the two-part configuration is formed as the latches and the matching latches are formed into latches during the bonding operation with the inclined surface. One of the lock engagements is mechanically guided to meet the requirements. The deformation work of the axial joint protrusions can be reduced by the oblique surfaces. For example, the mating latches can be screwed to the above-mentioned oblique surfaces along the oblique surfaces by means of preliminary screw movement. In the retaining space of the axial protrusions, the result is that compared to the axial coupling protrusions, if they are simply placed in the radial direction or / and the peripheral direction (according to their configuration and orientation) The dimensions of the protruding latch lugs are pushed aside, and the axial coupling protrusions must be deformed less seriously orthogonal to the rotation axis of the sprocket, so that the holding space can be connected from a completely axial direction take.

The number of axial protrusions required for a stable latch engagement can be advantageously maintained to a small number due to at least some of the axially fixed protrusions of the axially fixed protrusions, preferably all axially fixed The protrusion is also the fact that the protrusion is stopped. A side vent of the axially fixed projection located axially between the latching lug and the holding profile, particularly in the root region, is then a stop surface or at least such a surface.

The axial protrusions are preferably formed on a sprocket in a closed manner around one of the sprocket rotation shafts of the sprocket that carries them and is axially protruding from the sprocket. The axial protrusions are arranged at a distance from each other in the peripheral direction. Due to the configuration of the sprocket, the radial distance between different axial protrusions is smaller than the distance between them in the peripheral direction.

The axial protrusion is preferably provided in the form of an axially fixed protrusion, such as a stop protrusion and a matching stop protrusion, to fix the two parts to each other relative to its cylindrical coordinate system. The cylindrical coordinate system includes an axial, a radial, and a peripheral coordinate with a clear positioning relationship with sufficient strength relative to the forces and moments occurring during operation. In order to ensure that the defined positioning is stable, the axial protrusions may form a plurality of protrusion groups, each of which has at least one axially fixed protrusion and a matching stop protrusion. This is sufficient if the axial fixing protrusion is also a stop protrusion. At least some of the protrusion groups, preferably all of the protrusion groups, may additionally have a stop protrusion. Each protrusion group, for its part, has preferably configured the two parts with respect to a cylindrical coordinate along the axial direction and at least another cylindrical coordinate, preferably along all three cylindrical shapes The movement of the coordinates is stable relative to each other.

The achievable maximum load supporting capacity of the latch engagement obtained by the protrusion groups as a whole is increased by providing a plurality of protrusion groups, but the two-part configuration is provided by a plurality of protrusion groups. The fastening of the groups to each other is mechanically over-determined. Each of the independent protrusion groups in the plurality of protrusion groups is configured with the two parts about the axial movement and another cylindrical coordinate or even about all three The linear independent cylindrical coordinates are fixed relative to each other. However, the effect of the mechanical overshoot can be reduced by the corresponding elasticity at the formation of the latches and / or the mating of the mating latches, because the forming involved can dissipate the mechanical overshoot produced by the elastic deformation stress. This principle applies to a mechanically loaded component that has internal stresses and then has little or no deformation, or that has deformation and then has only low internal stresses, if any. If the effect of this mechanical overshoot is alleviated, the effect of increasing the strength of the latch engagement that is achievable is maintained. This arrangement is therefore advantageous as a whole.

The clusters of protrusions preferably have the same design and are configured to be distributed along the entire perimeter of the portion containing them, particularly preferably equally spaced. The use of multiple protrusion groups, such as more than three or four protrusion groups, further ensures the actual non-releasability of the latch engagement described above. Although the engagement of a single axial fixing projection behind a part of a matching latch formation can be removed by the corresponding deformation of the latter, simultaneous deformation of a plurality of axial fixing projections becomes more difficult and as the number increases Becomes almost impossible. The latching lugs of the different axial fixing protrusions preferably protrude from the individual axial protrusions in different directions orthogonal to the rotation axis of the sprocket. In order to release the latching engagement, not only the plurality of axially fixed projections must then be deformed, but each projection from the plurality must then also be deformed in a different direction in each case. This is almost and practically not feasible.

Although it should basically not be ruled out that the axial protrusions involved in the latch engagement are also arranged on the first partial arrangement, these axial protrusions are preferably provided only on the second partial arrangement.

In order to avoid the sprocket configuration having unnecessary weight that the cyclist must constantly accelerate and decelerate, one of the sprocket from the first or / and the second part configuration preferably has a radial outer chain with sprocket teeth Wheel region and a radially inner hub region designed to transmit torque to the rear wheel hub, wherein the hub region and the sprocket region are arranged by a plurality of sprocket spokes at a distance from each other in the peripheral direction To connect with each other. The area of the sprocket placed further away from the rotation axis of the sprocket is used in a manner known per se to transmit force between a bicycle chain and the sprocket arrangement. The hub region disposed closer to the rotation axis of the sprocket is used in a manner known per se to transmit torque from the sprocket arrangement to a rear wheel hub, for example by a middle arrangement of a drive member.

In a highly efficient manner, such mating latch formations may include a plurality of sprockets spokes which are present in any case. As such, the mating latch formations need not be specifically formed.

Due to the configuration of the sprocket spokes, especially in the case of large-diameter sprocket wheels, the substantial weight savings compared to solid-designed sprocket wheels are promised, such sprocket spokes and therefore the matching latches The lock forming system is preferably formed on the first partial configuration of the largest sprocket having the sprocket configuration.

In principle, the sprocket spoke can go continuously from the hub region to the furthest to the sprocket region. However, since the radius exhibited by the rotation axis of the sprocket is highly divergent, one of the sprocket surfaces occupied by the sprocket spoke decreases with an increasing radial distance from the sprocket rotation axis. However, the force is introduced into the sprocket by the bicycle chain, especially at the radial maximum distance from the rotation axis of the sprocket. In order to thus be able to provide sufficient sprocket spokes for transmitting forces and the resulting torque between the sprocket region and the hub region, or even in a region located further radially outward, one advantageous development according to the invention, These sprocket spokes include a small number of inner sprocket spokes disposed on a radially inner side and a large number of outer sprocket spokes disposed on a radially outer side. Due to the interaction with the sprocket spokes, the latch forming configuration as the individual other part of the matching latch formation is also roughly arranged in the area of a sprocket with the part forming the latch formation. In most cases of practical relevance, these latch forming systems are instead arranged radially on the outer side rather than the inner side. The mating latches therefore preferably include a plurality of outer sprocket spokes. The mating latch shapes preferably include only outer sprocket spokes.

The aforementioned matching stop forming system is also preferably a sprocket spoke, and particularly preferably an outer sprocket spoke.

In order to be able to provide sufficient elasticity to reduce the stress caused by the over-deposition of the part, the fixed part of the sprocket spoke as one of the matching latches is preferably configured to be separated from the two longitudinal ends of the sprocket spoke. Some distance. The same reasoning applies to the stop portion or / and the matching stop portion of a sprocket spoke as a matching stop formation. The fixed portion or / and the stop portion or / and the mating stop portion are preferably located in a third of the longitudinal length of the center of the sprocket spoke, as measured along a contour that can be optionally bent, And it forms a batch of mating latches or / and a batch of mating stops. This is particularly true when the mating latch is formed or / and the mating stop is formed from an outer sprocket spoke.

A spoke region disposed between the sprocket region and the hub region preferably has a coupling ring region that surrounds in a closed manner in the peripheral direction, and the inner sprocket spoke ends Begin there (when viewed from the inside in the radial direction toward the outside in the radial direction) and the outer sprocket spokes start there. The coupling ring region is preferably in a radial region that reaches one-third to two-thirds of the radial length of the entire spoke region covered by the sprocket spokes. The coupling area is preferably in the range of one-third to 7/12 of the radial length of the spoke area.

In principle, an independent sprocket spoke can be used as a joint between the axial fixed protrusion and the matching stop protrusion (optionally also a stop protrusion), which is used to arrange the two parts relative to each other. The position is fixed in all cylindrical coordinates. However, the fact that the plurality of spoke groups each having at least two sprocket spokes can be formed by the sprocket spokes can achieve the independent sprocket spokes by the first and the second part of the configuration. A lower mechanical load engaged by the latch. Each spoke group is preferably assigned a protrusion group as described above, and therefore each spoke group interacts with a protrusion group to form another joint combination. The assembly of all of these joint combinations includes the above-mentioned latch joints and the contact joints that connect the two part configurations to each other in the peripheral direction for transmission of torque.

In order to be able to form as many joint combinations as possible in the peripheral direction and each involves a plurality of sprocket spokes, it is better to conceive that the sprocket spokes are directly connected to each other in the peripheral direction. Jia is exactly directly connected to each other followed by two sprockets, which form a spoke group. As has been established above, such sprocket spokes are preferably outer sprocket spokes, and therefore an even number of outer sprocket spokes are preferably provided.

In principle, it is conceivable that the sprocket spokes, especially the outer sprocket spokes, run exclusively from the hub region or from the coupling ring region to the sprocket region in the radial direction. However, this configuration is not properly loaded and is therefore not preferred. Due to the torque that occurs on the sprocket configuration during the intended operation, around the sprocket rotation axis between the sprocket area and the hub area, the sprocket spokes can be formed with a smaller cross section if the chain The spokes are arranged radially such that one of the same sprocket spokes in the driving rotation direction of the sprocket arrangement is positioned further on the inner side before the spoke part and the spoke part is positioned radially on the more outer side. In this way, the load outside of the radial contour assembly thereof suitably has a contour assembly in the peripheral direction. When viewed opposite to the driving rotation direction, the sprocket wheel train is particularly preferably curved convexly. This is better for the radially inner sprocket spokes and for the radially outer sprocket spokes.

A further advantage of sprocket spokes assembled as described in the previous paragraph and formed as mating latches is that if they run not only in the radial direction but also in the peripheral direction, not only the force can be transmitted to the In the peripheral direction, and in addition, a force can also be transmitted in the radial direction, between the latch shapes as the matching latch shapes and the sprocket spokes.

The latch formation preferably therefore acts in an area of the sprocket spokes which has a fixed portion and in which the sprocket spokes are inclined relative to the radial direction, preferably 35 ° and 60 ° Between °, particularly preferably between 40 ° and 50 °. A force or reaction force may then be transmitted in substantially the same portion in the radial direction and in the peripheral direction between the latch shapes and the sprocket spokes. The latch-shaped engagements on the sprocket spokes are preferably contact engagements of a stop surface or a mating stop surface on a flank that laterally delimits the sprocket spokes, and are also The sprocket spoke is engaged from behind by the latching lugs of the axially fixed projections. Similarly, a stop portion or / and a matching stop portion forming a sprocket spoke matching the stop formation is preferably disposed in an area of the sprocket spoke, and the sprocket spoke is relative to The radial direction is inclined, preferably between 35 ° and 60 °, and particularly preferably between 40 ° and 50 °.

The presence of the sprocket spokes, especially the outer boundary surfaces of the outer sprocket spokes under any circumstances, as the contact-engaging surface, preferably forms a stop surface with the stop protrusions and A contact engagement of the mating stop surfaces of the mating stop protrusions, and also of these form-keeping contact engagements of the latching lugs and optionally the axially fixed protrusions. The sum of these contact engagements acting in different directions results in a firm latch engagement because the latch engagement is a positive lock.

In order to promote the contact and positive lock engagements that form the latching engagement between the two part configurations, the sprocket spokes are viewed on a cross section orthogonal to the longitudinal direction of the individual partial spokes. At least, a polyhedron configuration is present in at least the area where the latches are engaged with the latches, and a spoke configuration having a rectangular cross section is particularly preferred. In the case of a preferred spoke configuration with a rectangular cross-section, the two parallel edges of the rectangular cross-section are formed by the sides of the two ends of the sprocket spokes, and the other two parallel edges are formed by the sprocket spokes. The flank is formed by connecting the sides of the two ends.

In the sprocket configuration already seen in DE 10 2015 205 736 A1, the first part configuration only includes the largest sprocket of the sprocket configuration. However, it is possible to obtain the better rigidity of such sprocket configurations, particularly the greater flexural rigidity relative to bending around a bending axis orthogonal to the sprocket's rotation axis, and particularly from the rotation of the sprocket. The shaft protrudes radially farther away from the larger rigidity of the first part configuration because the first part configuration includes the largest and second largest sprockets, where the largest and second largest sprockets are integral with each other form. Due to this advantageous effect, the present case, regardless of the latching engagement between the first and the second part configuration, is also related to the bicycle rear wheel sprocket configuration as described in the first paragraph, the first part of which The configuration includes the largest sprocket and the second largest sprocket formed integrally with it. The advantageous developments described in this case also apply to the sprocket configuration and can be implemented thereon.

Regardless of the configuration of the other sprocket areas, spoke areas, and hub areas, in order to increase strength, especially the flexural strength around a bending axis orthogonal to one of the sprocket rotation axes, the first part configuration is It is assembled in such a way that the hub region is arranged axially closer to the smallest sprocket than the sprocket region of the largest sprocket.

In order to further strengthen the first part configuration, the first part configuration may have an axis around the rotation axis of the sprocket in a radial strengthening area between the largest circle and the root circle of the second largest sprocket. Toward the bead. The axially rounded edge is formed as a depression on one side of the first partial arrangement and preferably as a protrusion on the opposite side. The axial rounded edge is preferably designed as an axial depression on the side of the reinforcing area facing the second large sprocket.

In order to obtain a uniform force ratio as much as possible at the first portion when the bicycle chain is engaged with the largest or second sprocket, and the low weight of the first portion, it is The best arrangement is such that the spokes of the sprocket wheels extend radially outward to the sprocket as far as the largest sprocket, wherein the first part is arranged at a diameter between the root circle and the top circle of the second largest sprocket. The number of sprocket spokes in the direction zone is almost half of the number of teeth of the second largest sprocket. Due to the highest level of effect of this configuration on the uniform load during operation of the first part configuration, this case regardless of the latch engagement between the first and the second part configuration is also relevant as in the first paragraph The first part of the bicycle rear wheel sprocket configuration described in the above configuration is designed according to this paragraph. The sprocket arrangement formed in this way may have further advantageous features as described in the present case.

It is particularly preferred here that when viewing the first portion configuration in the axial direction, each sprocket spoke and each second tooth train of the second largest sprocket are disposed at the same peripheral position. Each second tooth, that is, the teeth disposed at a peripheral position between the sprocket spokes, is therefore also accessible in a particularly simple and advantageous axial manner through the sprocket spokes, and Facilitates the manufacture of this first part configuration. In addition, when a sprocket spoke is disposed at the same peripheral position as one of the teeth of the second largest sprocket, the force transmission between the second largest sprocket and the largest sprocket then occurs directly when the force is transmitted from the bicycle chain To the point of the second largest sprocket. Whenever the second largest sprocket is engaged with the bicycle chain in a force-transmitting manner, the torque introduced by the bicycle chain into the first portion of the configuration can therefore be passed through the sprocket spokes in a particularly simple and stable manner. Into the hub area.

The first part is configured with at least the second largest sprocket, particularly preferably both the largest sprocket and the second largest sprocket, preferably having a stagger in the peripheral direction at least in a peripheral area The system has thicker axial and thinner teeth. This simplifies the assignment of the teeth of at least the second largest sprocket, especially the largest sprocket, to the inner link plate area and the outer link plate area of one of the bicycle chains that interact with the sprocket configuration, thereby assisting Prevent the chain from breaking. At least some teeth of the teeth of the second large sprocket which are disposed at the same peripheral position as the spokes of the sprocket wheels preferably have an axial ratio of teeth that are directly adjacent to the teeth in the peripheral direction. Thick design. A relatively small axial gap that accommodates the bicycle chain that is engaged with the second large sprocket, preferably only the outer link plates of the bicycle chain, has a small clearance, and therefore appears at the same peripheral location It rises between the axially thicker teeth and the sprocket spokes. If a sprocket spoke and a tooth system are arranged at the same peripheral position, the sprocket spoke and tooth will overlap when viewed in the axial direction. The sprocket spokes and teeth are formed in the same shape, and are formed in the peripheral direction with a larger size, and it is preferable to completely overlap the other shapes in the peripheral direction.

Regardless of the sprocket, the preferred tooth configuration of an axially thicker tooth disposed thereon may preferably appear in the following manner: the axially thicker staggered in a peripheral portion of a sprocket and the The transverse flanks of the same axially thin teeth face axially adjacent smaller sprockets on a common virtual envelope surface, and the common virtual envelope surface is preferably relative to the chain. One of the wheel rotation axes is formed in a rotationally symmetrical manner. Beginning on the common virtual envelope surface, the axially thicker teeth are closer to adjacent larger sprockets than the axially thinner teeth. The axially thicker tooth flank systems which are in the front in the driving rotation direction are preferably non-stepped, while the opposite trailing flanks have an axis on the side of the larger sprocket that is adjacent to it. Xiangjie. In other words, starting from a co-anterior tooth belly, an axially thicker tooth in the peripheral direction has a larger sprocket on the side facing the neighbor than a smaller sprocket on the side facing the neighbor. Smaller size. In view of a peripheral portion of an axially thick tooth along a lateral surface of a tangent cylinder coaxial with the rotation axis of the sprocket, the axially thick tooth therefore has an approximately L-shaped cross section. Because the teeth having an L-shaped cross-section are used to guide a bicycle chain in positive lock engagement with a sprocket supporting the teeth, the present application does not care about the difference between the first and the second part configurations. Regarding the latch engagement, there is also a sprocket configuration described in the first paragraph of this application, which has teeth having the L-shaped peripheral cross section in the area from the largest sprocket to the second small sprocket. . A plurality of sprocket wheels having an even number of teeth preferably have such teeth; particularly preferably, each sprocket wheel having an even number of teeth has such teeth. As described in this application, this type of sprocket arrangement can be advantageously developed.

Preferably, all the sprocket wheels of the rear wheel sprocket configuration having an even number of teeth have an axially thin tooth and an axially thick tooth in a staggered manner over at least one peripheral area in a peripheral direction, as previously As described in the paragraph. Only the smallest sprocket with preferably 10 teeth has axially thicker teeth, and the lateral flank facing the larger sprocket adjacent to it is placed on the same guide of the axially thinner teeth with the peripheral area On one common, virtual enveloping surface of one of the flank, the axially thicker teeth starting from the common enveloping surface extend more axially away from the adjacent larger ones than the axially thinner teeth disposed therebetween. Sprocket. The two lateral flank teeth also extend to have different distances in the peripheral direction on the smallest sprocket, wherein the lateral flank closest to the larger sprocket adjacent to it has a lateral flank in the peripheral direction that is greater than the opposite lateral flank. Larger size. Starting from other sprocket wheels with an even number of teeth, at the smallest sprocket, the lateral flank facing the larger sprocket adjacent to it protrudes above the lateral flank of the same tooth, which drives the drive in the peripheral direction. The longitudinal ends at the front of the direction of rotation and the trailing longitudinal ends point towards the larger sprocket away from the neighbor. On the axially outermost and smallest sprocket, space can thus be provided in the tooth area for receiving the chain link plate of the bicycle chain, especially the edge area of the outer link plate. With the different configuration of the smallest sprocket, the skew of the bicycle chain meshing with the smallest sprocket can be aroused and unwanted contact between the bicycle chain and the adjacent larger sprocket can be avoided. At least one axially thicker tooth, preferably more than a plurality of axially thicker teeth, and particularly preferably all axially thicker teeth, are shifted from the flank that is longer in the peripheral direction to the peripheral Those with a shorter flank in the direction are stepped at at least one peripheral longitudinal end of the tooth, preferably at the peripheral longitudinal ends of both, preferably in a single step, so as to pass through the step of the flank Shaped to form a receiving area for a chain link plate of one of the bicycle chains. Due to the beneficial effect of reducing the skew effect of the chain on the smallest sprocket, the present application, regardless of the latching engagement between the first and the second part configuration, is also relevant as described in the first paragraph of the case The sprocket configuration has a minimum sprocket set as described in this paragraph. At the sprocket configuration, independent development or plural development can be achieved, as described in this case.

Compared to the above-mentioned roughly L-shaped cross section, the axially thicker teeth on the smallest sprocket have a substantially T-shaped cross section in the above-mentioned peripheral section.

The second part configuration preferably has more sprockets than the first part configuration, and particularly preferably more than twice or at least three times or even four times the sprocket of the first part configuration. many. This second partial arrangement can therefore have between six and twelve axially continuous sprockets integrally formed with each other. This sprocket is equipped with about 7 or 8 sprocket wheels. The total number of sprocket wheels can be used here for E bikes and pedelecs, where axially adjacent sprocket wheels can be accepted because of the motorized assistance of cyclists. There is a large difference in the number of teeth.

The second partial configuration preferably includes a third largest sprocket of the sprocket configuration. This is further preferably the largest sprocket in the second part configuration.

The second partial configuration may also include the smallest sprocket. Particularly preferably, in addition to the first and the second partial configurations, the sprocket configuration does not have further partial configurations or does not have further independent sprocket wheels, which is considerably tolerated by a few purpose components Facilitates the installation of this sprocket configuration. However, it should not be excluded that, in addition to the first and second partial configurations, a further partial configuration or an independent sprocket train is provided on the sprocket configuration.

In order to save weight, the independent and integrally formed sprocket trains arranged in the second part are connected to each other by a web. The webs connecting the two axially adjacent sprocket wheels preferably do not extend beyond the smaller sprocket wheels of the two sprocket wheels that are radially facing the sprocket shaft. The favorable force transmission between the axially directly adjacent sprocket wheels that are integrally formed with each other in the second part configuration can be achieved, because the comparison of the second part configuration with a sprocket and its adjacent neighbors can be achieved. At least one pair of small sprocket wheels, preferably a plurality of pairs, particularly preferably all pairings, the sprocket is connected to the adjacent smaller chain by a web formed integrally with the two sprocket wheels wheel. In order to facilitate the cleaning of the second part configuration and to reduce its weight, the number of webs connecting a larger sprocket to a larger sprocket to an axially adjacent smaller sprocket is preferably smaller than that Number of teeth for smaller sprocket. Here, it is particularly preferred if the smaller sprocket has even teeth and the number of webs connecting the two sprocket wheels is exactly half of the even teeth of the adjacent smaller sprocket. The above is correspondingly applicable to half of the sprocket spokes relative to the number of teeth of the second large sprocket arranged in the first part. The number of the webs may also be less than half the number of teeth of the paired smaller sprocket. The number of the webs and the number of teeth of the pair of smaller sprocket wheels that are directly adjacent in the axial direction and are connected by the webs preferably have a common integer factor. This makes it possible to provide a web in a stiffening manner, always like a tooth, at the same peripheral position on the paired smaller sprocket. This condition is preferably applicable to the pairing of the two axially adjacent sprocket wheels of the second part of the configuration, preferably the smaller sprocket wheels of the two sprocket wheels have an even number of teeth. If a web and a tooth are arranged at the same peripheral position, the web and the teeth will overlap when viewed in the axial direction. The same forming system having the webs and teeth having a larger size in the peripheral direction preferably overlaps each other completely in the peripheral direction.

Also in order to save weight, the first partial configuration having the largest sprocket and preferably also the second largest sprocket formed integrally with the largest sprocket is produced from a low density material such as an aluminum alloy. This second part configuration having more than two, preferably about ten integrally formed sprocket wheels, for strength reasons, is preferably made of a high density and preferably also a high elastic modulus such as steel Material produced.

Contrary to the advantages of the first part configuration mentioned above, if the second part is arranged in the axial direction, it is better for one of the sprocket wheels that constitute the second part configuration and adjacent to it. At least one pair of adjacent smaller sprocket wheels with an even number of teeth, preferably for each pairing, each web of the adjacent smaller sprocket wheel and one tooth, preferably each second tooth, are placed on At the same peripheral location, these advantages can also be obtained in the second part configuration. This improves the transmission of force between the integrally formed sprocket wheels and promotes access to at least each second tooth of an even number of smaller sprocket wheels during manufacture and optionally during installation. Because it is integrally formed and has the highest level of force transmission in the second part configuration of one of the plurality of sprocket wheels and the accessibility of the teeth of the sprocket wheel, preferably even-numbered ones, this application does not care about the first and the first How the latching engagement between the two parts is also related to the bicycle rear wheel sprocket arrangement as described in the first paragraph, the second part of the arrangement is according to this paragraph or / and according to one of the previous two paragraphs While designing. This sprocket arrangement formed in this way may have further advantageous features as described in this application.

As described above for the first part, if for at least one pairing, at least some of the teeth of the adjacent smaller sprocket teeth disposed at the same peripheral position as the web have a direct ratio The thicker axial design of the teeth adjacent to the peripheral direction can also be configured in the second part to obtain improved chain guidance and reduce the risk of chain breakage. However, it should not be ruled out that a web is also disposed at the peripheral position of at least one axially thin tooth. It may be advantageous, for example, whenever the smaller sprocket is weakened by a lateral groove or recess in the peripheral area of one of its thinner teeth, such as by at least one of its multiple end surfaces When one of the surfaces is formed as a depression in one of the sprocket end sides, a chain rise assists weakening. The web may then strengthen or / and strengthen the peripheral area of the thinner teeth. The webs paired by a sprocket therefore do not need to be arranged at equal distances in the peripheral direction, even if this is preferred.

If the number of teeth of the paired smaller sprocket is not even, the number of webs may be the same as the number of teeth of the smaller sprocket. However, it is also true that the number of webs may be smaller than the number of teeth, even in the case where the number of webs and the number of teeth have a common integer factor.

The web is particularly preferably arranged only at a peripheral position where a tooth of the smaller sprocket is also located.

The configuration of the axially thicker and thinner teeth and the configuration of the second part has been described above.

In order to make the web and the torque transmission of the second part as efficient as possible, the webs are configured not only in the axially directly adjacent sprocket wheels connected by them. Between radial directions. The webs preferably also have a contour component in the peripheral direction, and in particular, it is particularly preferred that their radial inner ends follow their radial outer ends in the drive rotation direction.

The sprocket configuration preferably has 8 to 14 sprocket wheels, preferably 12 to 14 sprocket wheels, of which the smallest sprocket wheel has no more than 12, preferably no more than 10, and more preferably 10 The number of teeth, or the largest sprocket thereof, is not less than 50, preferably not less than 52, and particularly preferably accurate to 52 teeth. In order to make full use of the above-mentioned sprocket spokes and teeth of the second largest sprocket as well as the advantageous and coordinated spatial arrangement of the webs and teeth on the second part of the sprocket, the sprocket configuration is relatively It is preferred that no more than two sprocket wheels have non-even teeth. According to a preferred embodiment, the sprocket arrangement from the smallest to the largest two sprockets has the following number of teeth: 10, 12, 14, 16, 18, 21, 24, 28, 32, 38, 44, 52.

As already explained above, on a plurality of sprockets with an even number of teeth, preferably on all sprockets with an even number of teeth, an axially thicker tooth and an axially thinner tooth system are preferably continuously staggered They are respectively arranged on at least one peripheral portion, particularly preferably on a plurality of peripheral portions, and most preferably along the entire periphery in the peripheral direction.

Generally speaking, the sprocket arrangement discussed here is used in combination with a structurally common bicycle chain that has a pair of inner link plates and an outer link plate in the longitudinal direction of the chain along the longitudinal direction of the chain. Approximately equidistant rollers connected to each other in a staggered manner in the direction. The axially thicker teeth preferably have a thickness that is coordinated with the configuration of the mating bicycle chain, wherein the axial dimension of the thickness is greater than the clear width between the inner link plate pairs of an inner link plate pair. Therefore, the axially thicker teeth can completely enter only one tooth entry space as expected, and the tooth entry space is bounded by the link plate outside the bicycle chain. Whenever a bicycle chain engages a sprocket with an even number of teeth, it is therefore clearly positioned in the longitudinal direction of the chain relative to the sprocket. This also reduces the risk of chain breaks. Due to the above-mentioned preferred staggered arrangement achieved in the peripheral regions of at least the axially thicker and thinner regions, only one outer link plate of the chain is always arranged relative to a web or / and a sprocket spoke, especially Outer sprocket spokes, on multiple sprocket wheels with even teeth, preferably on all sprocket wheels except the smallest sprocket with even teeth, especially on all sprocket wheels with even teeth, In the case of a positive lock engagement of the chain along the positive lock area.

The net width between the outer link plates of one of the bicycle chain link pairs is greater than the net width between the inner link plates of an inner link plate pair.

This application is therefore also related to a bicycle drive assembly that includes the above-mentioned bicycle chain and further includes a sprocket arrangement as described and developed in this application.

The bicycle drive assembly preferably has a chain precisely on a pedal crank supporting one of the bicycles of the bicycle drive assembly, and therefore a change in the transmission ratio from the pedal crank to the rear wheel hub occurs uniquely in The rear wheel sprocket is placed.

FIG. 1 shows a schematic side view of a bicycle 10 having a bicycle drive assembly 12 according to the invention. The bicycle 10 has a frame 14 having an elastically operable front wheel 16 and an elastically operable rear wheel 18. The front wheel 16 can be controlled by the handle 20. The cyclist can sit on the saddle 22 of the bicycle 10 during his journey. The direction in which the bicycle 10 has been exemplified as standing on a flat bottom surface U is indicated by an arrow V.

In the illustrated preferred exemplary embodiment, the bicycle drive assembly 12 includes an independent front chain ring 24 that is directly coupled to the pedal crank 26 in a torque transmitting manner, and includes A rear wheel sprocket arrangement 30 is connected to one of the independent front chain rings 24 via a bicycle chain 28. The rear wheel sprocket arrangement 30 is coupled to the rear wheel 18 in a torque-transmitting manner, and thus the torque introduced into the front chain ring 24 via the pedal crank 26 is transmitted to the rear wheels via the bicycle chain 28 and the rear wheel sprocket arrangement 30 18.

The bicycle chain 28 may be force-transmitted into engagement with one of the twelve sprocket wheels R1 to R12 of the rear wheel sprocket arrangement 30 via a transmission 32 (not specifically described). The cyclist riding the bicycle 10 can thus select the speed and torque transmission ratio from the front chain ring 24 to the rear wheel 18 in a manner known per se.

2 to 6 illustrate details of the rear wheel sprocket arrangement 30 in various diagrams. FIG. 2 shows a perspective view of the sprocket arrangement 30 obliquely from the front and from the outside, that is, it is viewed from a position closer to the smallest sprocket R12 than the largest sprocket R1 of the sprocket arrangement 30 Depending on the position of the viewer. FIG. 3 shows a side view of a sprocket arrangement 30 whose viewing direction is orthogonal to the sprocket shaft RA. FIG. 4 shows a longitudinal cross-sectional view of the sprocket arrangement 30 along a radial half of a cross section including a sprocket rotation axis RA. FIG. 5 shows the sprocket arrangement 30 viewed from the outside along the sprocket rotation axis RA, that is, toward a longitudinal center plane of one of the sprocket axes RA orthogonal to the bicycle 10 of FIG. 1. FIG. 6 shows the sprocket arrangement 30 in the axial direction, but in a direction opposite to FIG. 5, that is, from the inside or away from this longitudinal center plane of the bicycle 10.

The sprocket arrangement 30 includes a first partial arrangement 32, which has a maximum sprocket R1 with 52 teeth and a second largest sprocket with 44 teeth R2. The integrally formed first part configuration 32 is preferably formed of an aluminum alloy so that the first part configuration 32 is formed with the lowest possible weight.

The sprocket arrangement 30 further has a second partial arrangement 34 which is fixedly connected to the first partial arrangement 32 and all further sprockets R1 to R12 of the sprocket arrangement 30 are integrally formed in On it. The sprocket R3 is the third largest sprocket, and the sprocket R12 is the twelfth largest or smallest sprocket of the sprocket configuration 30. This monolithic second part arrangement 34 is produced from steel for reasons of the highest possible strength. The third largest sprocket R3 of the sprocket arrangement 30 of the largest sprocket arrangement 34 of the second part preferably has 38 teeth. The smallest sprocket R12 preferably has 10 sprocket wheels.

The first part configuration 32 and the second part configuration 34 are connected to each other by latches and are secured to prevent axial removal from each other, as further described in the following details. The connection formed between the first partial arrangement 32 and the second partial arrangement 34 connects the partial arrangements 32 and 34 to each other in two opposite peripheral directions around the sprocket rotation axis RA and to rotate along the sprocket The two joints of the shaft RA move in opposite axial directions.

The sprocket arrangement 30 is driven by the pedal crank 26 and the driving rotation direction of the sprocket arrangement 30 which is rotated therein. In order to move the bicycle 10 in the forward travel direction V, it is indicated by the symbol DR in the drawing. In the axial view viewed from the outside according to FIG. 5, the driving rotation direction DR runs clockwise, and in the axial view viewed from the inside according to FIG. 6, the driving rotation direction DR accordingly runs counterclockwise.

As can be seen most clearly in the views of FIGS. 4 and 6, the first part arrangement 32 has a radially inner hub region 32 a which is designed for self-sprocket arrangement 30 or from first part arrangement 32 The torque is transmitted to a drive and therefore to a hub of the rear wheel 18. For this purpose, the hub region 32a has, for example, a spline tooth connection on the radially inner side.

In addition, the first partial arrangement 32 has a radially outer sprocket region 32b with teeth 36a and 36b of the largest sprocket R1. As can be seen particularly in Figure 4, the hub region 32 is configured to be axially offset relative to the sprocket region 32b toward the smallest sprocket R12, which provides the first portion of the configuration 32 with flexural rigidity that is The flat design increases the bending about a bending axis orthogonal to the sprocket rotation axis R.

The teeth 36a of the largest sprocket R1 are thicker in the axial direction than at least some peripheral portions of the sprocket R1 compared to the teeth 36b adjacent to the teeth in the peripheral direction. . The axial thickness of the thicker teeth 36a is selected here in such a way that the thickness is greater than the net width between the pair of link plates in one of the chains 28. On the bicycle chain 28, equidistant rollers are connected to each other along the longitudinal direction of the chain by means of an outer link plate pair 28a and an inner link plate pair 28b instead of interleaving in a known manner, wherein the inner link plate pair 28b The net width between them is smaller than the net width between the outer link plate pairs 28a. In FIG. 1, the net width of the outer link plate pair 28a and the inner link plate pair 28b should be measured parallel to the sprocket rotation axis RA. The roller shafts of the rollers of the bicycle chain 28, whose rollers are connected to each other equidistantly by the inner link plate pair 28b and the outer link plate pair 28a, are also parallel to the sprocket rotation axis RA in FIG. In FIG. 1, the sprocket rotation axis RA is orthogonal to the plane of the drawing in FIG. 1.

A spoke region 32c connecting the hub region 32a to the sprocket region 32b is disposed radially between the hub region 32a and the sprocket region 32b.

As can be easily seen from the axial inner view of the sprocket arrangement 30 of FIG. 6, but even more clearly in the axial view of the first partial arrangement 32 of FIGS. 9 and 10, the spoke region 32c includes a radially inner The sprocket spokes 38 and the radially outer sprocket spokes 40. The radially inner sprocket spokes 38 extend farthest from the hub region 32a to the coupling ring region 42 that surrounds in a closed manner. The radially outer sprocket spoke extends as far as the coupling ring region 42 to the tooth region 32b. The inner and outer sprocket spokes 38 and 40 preferably do not overlap in the radial direction. The number of the outer sprocket spokes 40 is greater than the number of the inner sprocket spokes 38, and is preferably more than two times based on the reason for the uniform force distribution around the sprocket rotation axis RA in the peripheral direction.

In the illustrated embodiment of the first partial configuration 32, in a particularly advantageous manner, as much as half of the outer sprocket spokes 40 are provided as the teeth of the second largest sprocket R2, which teeth are axially The ground is arranged adjacent to the outer sprocket spoke 40.

In order to stably transmit torque from the sprocket region 32b to the hub region 32a in size and have the smallest spoke cross-section, the inner sprocket spoke 38 and the outer sprocket spoke 40 are strengthened to drive the direction of rotation DR. The individual radially inner ends of the upper sprocket spokes 38 or 40 are positioned before the radially outer ends of the same sprocket spokes 38 or 40 in such a manner that a contour component is formed in the peripheral direction around the sprocket rotation axis RA. In addition, the sprocket spokes 38 and 40 are designed to be wound in such a manner that the sprocket spokes 38 and 40 are curved in a concave shape when viewed in the driving rotation direction DR and viewed in a direction opposite to the driving rotation direction DR. A curvature axis parallel to the sprocket rotation axis RA is curved.

The radial length 44 of the coupling ring region 42 with respect to the spoke region 32c is disposed between a radial inner third of the length 44 and a half of the length (see FIG. 10).

As can be seen particularly easily in FIG. 10, each second tooth of the second large sprocket R2 (these teeth are labeled 46 a) is located at the same peripheral position as an outer sprocket spoke 40. Therefore, the teeth 46b disposed between the teeth 46a are easily axially accessible through the outer sprocket spokes 40 and can be processed in a simple manner by a milling tool with high-precision metal cutting.

The teeth 46a which are coincident with the outer sprocket spokes 40 with respect to their peripheral positions are axially thicker than at least some of the peripheral parts of the second largest sprocket R2 than the adjacent teeth 46b in the peripheral direction. Teeth. With this axially thick design of at least some of the teeth 46a, the body connection of the second largest sprocket R2 and one of the largest sprocket R1 can occur particularly simply and stably.

The sections of Figs. 4 and 8 do not run through the peripheral positions of an outer sprocket spoke 40 and one of the axially thicker teeth 46a of the second large sprocket R2 relative to each other. Nevertheless, Figures 4 and 8 show that by this axial relative position, the axial gap 48 between an outer sprocket spoke 40 and the tooth 46a of the sprocket R2 has a relatively small axial dimension, and therefore when used as a bicycle When the chain 28 and the sprocket R2 are engaged with the positive lock, it can be accommodated with a small axial play.

As can be particularly understood from FIGS. 4 and 8, the sprocket region 32 b of the largest sprocket R1 has an axial rounded edge 50 for strengthening the sprocket R1, and the axial rounded edge 50 surrounds the sprocket rotation axis RA in a circular manner. The largest sprocket R1 is introduced from the side facing the second part configuration 34. The largest sprocket R1 therefore has a recess 50a on its side facing the second largest sprocket R2. The axially rounded edge 50 is a protrusion 50b designed on the opposite side facing away from the second largest sprocket R2. The axially rounded edge 50 is in a radial position in a reinforced area 51, which is placed between the root circles of the first sprocket R1 and the second sprocket R2, or even preferably in the second sprocket R2. Between the top circle and the root circle of the first sprocket R1.

11 to 13 show the second partial configuration 34 itself. FIG. 11 shows the second partial arrangement 34 in a perspective view obliquely from the outside. FIG. 12 shows a second partial arrangement 34 in a side view orthogonal to the sprocket rotation axis RA. Figure 13 shows the second partial arrangement 34 in an axial view from the inside.

FIG. 13 shows the formation of one of the second partial arrangements 34. Each sprocket R3 to at least R9 has a sprocket supporting a sprocket tooth and a web, the sprocket teeth and the web protruding radially inward from the sprocket and the second part is configured with one of the sprocket 34 and The axially adjacent and adjacent smaller sprockets are integrally connected.

For example, and for the sake of clarity, only the sprocket train of the largest sprocket R3 of the second part configuration 34 is marked with the component symbol 52 and projects radially inward toward the smaller sprocket R4 adjacent to it. The web is designated by the component symbol 54. The webs 54 do not protrude radially inward beyond the sprocket of a smaller adjacent sprocket (here, the sprocket R4), and the webs are formed directly and integrally with it.

In the present exemplary embodiment, the number of teeth of all sprocket wheels except the sprocket R7 having 21 teeth is an even number. For each pairing of the axially directly adjacent sprocket wheels of the second part configuration 34, each second toothing of the paired smaller sprocket wheel is located at the same peripheral position as a web. For sprocket pairing R3 / R4, this can be seen in Figure 13. The number of webs 54 connecting the larger sprocket (here R3) to the smaller sprocket (here R4) is half the number of teeth of the smaller sprocket. Each second gear train of the smaller sprocket is thus equally accessible axially from both sides of the second partial arrangement 34.

A plurality of teeth 56 of the sprocket R4 located at the same peripheral position as the web 54, and the web 54 is a person who integrally connects the sprocket R3 and the sprocket R4 to each other, rather than being provided between the teeth The teeth 56b in the peripheral direction are thicker in the axial direction. Furthermore, because of the axially thick design of the teeth 56a that coincide with the web 54 with regard to their peripheral positions, the integral connection of the sprocket wheels R3 and R4 can be formed in a stable manner and can be formed on a web 54 and a An axial gap 58 having a relatively small gap width is formed between the axially adjacent teeth 56a. When the bicycle chain and the sprocket R4 are in positive lock engagement, the axial gap 58 can then accommodate the bicycle chain 28 with a small play.

For the sprocket R6 and R7, the sprocket R7 has a non-even number of teeth, so the above is not applicable. At each peripheral position of one tooth of the sprocket R7, a web is guided there from the sprocket R6 to the adjacent smaller sprocket R7 and integrally connects the two sprocket wheels to each other. Due to the large number of webs, individual webs have a shorter design in the peripheral direction compared to those of the sprocket pairs, and the smaller sprocket has an even number of teeth.

It can also be seen in FIG. 13 that the webs (such as web 54) between the axially directly adjacent sprocket wheels are inclined in the peripheral direction and their radial lengths, especially In a manner opposite to the inclined direction of the sprocket spokes 38 and 40 arranged in the first part. The webs connecting the axially directly adjacent sprocket wheels of the second part configuration 34 are inclined in the peripheral direction in such a manner that their radial inner ends follow the radial outer ends in the driving rotation direction DR. This is suitable because the sprocket R3 to R12 of the second part configuration 34 will transmit the torque directly transmitted to it by the sprocket 28 to the first part configuration 32, and the first part configuration 32 This torque is transmitted to the hub region 32a and finally to the rear wheel hub.

As shown in FIGS. 11 to 13, three types of axial protrusions 60 a, 60 b and 60 c of different structures protrude from the sprocket 52 of the largest sprocket R3 of the second part configuration 34 toward the first part configuration 32. In each case, the combination of the axial protrusions 60a, 60b, and 60c forms a protrusion group 62 that acts on a portion 64 of the outer sprocket spoke 40. This portion 64, which is also a fixed portion such as a stop portion and a matching stop portion, completely surrounds the sprocket rotation axis RA in the peripheral direction. Due to its nature as a fixed part and as a stop part and also as a matching stop part, this part 64 is hereinafter referred to as a "engaging part". For purely understandable reasons, the component symbols 64 in the figure are only placed on some outer sprocket spokes 40 to identify the joint portion of the protrusion group 62 on the first partial arrangement 32.

The protrusion group 62 is distributed around the sprocket rotation axis RA in the peripheral direction over the entire length of the sprocket 52 and thus reaches the sprocket 52, and by the latter, the second part configuration 54 is tied to the sprocket 52 Is uniformly connected to the first part configuration 32 over its entire length.

It can be seen in FIG. 16 how the axial protrusions 60a, 60b and 60c interact with the sprocket spokes 40 outside the first part configuration 32 to connect the first and second part configurations 32 and 34 to each other for joint rotation. And in an axially immovable manner. The axial protrusions 60a, 60b, and 60c are periodically repeated in the peripheral direction.

The latches between some configurations 32 and 34 will be described below with reference to FIGS. 14 to 16. FIG. 14 shows a perspective view of the second partial arrangement 34 obliquely from the inside. FIG. 15 shows an enlarged detail of one of the two largest sprocket wheels R3 and R4 of the second part configuration 34 in FIG. 14. FIG. 16 shows a perspective view of the sprocket arrangement 30 with the two-part arrangements 32 and 34 obliquely from the inside.

The axial protrusion 60a is shorter in design than the other two types of axial protrusions 60b and 60c. The axial protrusion 60a is a matching stop protrusion, which is arranged such that its matching stop surface 66 abuts one of the engaging portions 64 (which functions as a matching stop portion) a lateral delimiting surface 68 of the outer sprocket spoke 40 .

In the joint portion 64, the lateral limit surface 68 abutted by the matching stop surface 66 is inclined approximately 45 ° with respect to the reference plane containing the sprocket rotation axis RA. Therefore, by matching the stop surface 66 and the lateral limit surface, The contact bonding between 68, the force acting on both the peripheral direction and the radial direction can be transmitted between the component parts 40 and 60a involved.

In addition, the axial protrusion 60a has an oblique surface 70 that is adapted to match the stop surface with a point on which the axial region 60a migrates and is axially close to the root region 70a of the axial protrusion 60a on the sprocket 52. The radial direction and the peripheral direction of 66 are inclined in such a manner that they approach each other.

The axial protrusion 60b is a stop protrusion, which faces the stop surface 74 in the opposite direction of the matching stop surface 66 of one of the same protrusion group 62 matching stop protrusion 60a. One of the lateral delimiting surfaces 76 of the outer sprocket spokes 40 is in contact engagement in the engaging portion 64 (which now acts as a stop portion). The delimiting surface 76 is here opposite the delimiting surface 68. The delimiting surface 76 is therefore also inclined 45 ° with respect to the above-mentioned reference plane. In the contact engagement between the stop surface 74 and the limiting surface 76, both the force in the radial direction and the force in the peripheral direction can therefore also be applied to the axial protrusion 60b and the outer sprocket spoke 40. Passing between.

Two surfaces: the stop surface 74 and the matching stop surface 66 delimit the outer sprocket spoke 40 and are accommodated in one of the receiving spaces 78. The distance between the matching stop surface 66 and the stop surface 74 of the same protrusion group 62 substantially corresponds to the thickness of the outer sprocket spoke 40, and thus the latter can be in a direction orthogonal to the rotation axis of the sprocket It is arranged in the receiving space 78 so as to have substantially no play. The oblique surface 70 facilitates the introduction of the associated outer sprocket spokes 40 into the receiving space 78.

The entirety of the matching stop surface 60a and the stop surface 60b of the second partial arrangement 34 thus fixes the two partial arrangements 32 and 34 to each other in the radial direction and the peripheral direction.

The axial protrusion 60c is an axially fixed protrusion. It has a latching lug 80 protruding from the axial protrusion 60c in both the peripheral direction and the radial direction with respect to the sprocket rotation axis RA.

A retaining space 82 is formed between the latching lug 80 and the root region 70c. More specifically, it is formed between the latching lug 80 and an outer surface 71 of the root region 70c facing the latching lug 80. In the meantime, the axial projection 60c projects axially from the sprocket 52 from the beginning, and the size of the holding space defined by the latch lug 80 and the root region 70 in the axial direction substantially corresponds to the region 64 One of the outer sprocket spokes 40 has an axial thickness, and thus the engaging portion 64 of the outer sprocket spoke 40 (which now acts as a fixed portion) can be accommodated in the holding space 82 in a direction without play as much as possible in the axial direction.

The entirety of all the axial protrusions 60c fixes the two-part arrangements 32 and 34 to each other in an axially immovable manner relative to each other. The oblique surface 66 of the matching stop protrusion 60a also facilitates the introduction of the engaging portion 64 of an outer sprocket spoke 40 into the individual holding space 82 of the axially fixed protrusion 60c.

The axial protrusion 60c is also a stop protrusion because it has a stop surface disposed between the latch lug 82 and the root region 70c, or between the axial protrusion 60c and the outer surface 71 of the axial protrusion 60c. 84. The blocking surface 84 is designed to contact against a lateral delimiting surface 86 of an outer sprocket spoke 40. In contrast, the latch lugs 82 are designed for contact engagement against one end-side delimiting surface 86 of an outer sprocket spoke 40.

The axial protrusion 60c thus forms a plurality of latch shapes of the second partial configuration 34, which are formed in the form of outer sprocket spokes 40 in the engaging portion 64 and interact with a plurality of matching latch shapes to form An almost non-releasable latch engages.

The same protrusion group 62 interacts here with a spoke group 41 formed from two outer sprocket spokes 40, and the two outer sprocket spokes 40 are directly adjacent to each other in the peripheral direction for use. To reduce or limit the force exerted on a different sprocket spoke 40.

In the region of the engaging portion 64, in order to be able to sufficiently provide the elastic deformability of the actual mechanical over-connection of the first and second portion configurations 32 and 34, the engaging portion 64 on each outer sprocket spoke 40 It is arranged at a distance from its two longitudinal ends in a central area of one of the outer sprocket spokes 40, which contains the longitudinal center of the sprocket spoke 40. The length of the central region is not more than one third of the entire length of the sprocket spoke 40, and preferably not more than one quarter.

The axially thicker teeth of the sprockets R1 to R6 and R8 to R11, that is, the teeth 36a, 46a, and 56a, which have been mentioned by way of example, will be described in more detail below with reference to their configuration and with reference to FIG. 17 Instructions.

FIG. 17 shows the end sides of any of the sprockets R1 to R6 and R8 to R11, which end faces face the longitudinal center plane of the bicycle 10 described above. If the sprocket, part of which is shown in FIG. 17, is not the largest sprocket R1, then this view is a larger sprocket with the end side facing individually adjacent.

The axially thicker teeth formed on the sprocket wheels and having the component symbols 36a, 46a, and 56a start from a common flank 88 that is forward in the driving rotation direction DR, and first have a nearly constant in the peripheral direction. Axial thickness and a constant radial coordinate. However, the lateral flank facing the viewer of FIG. 17 is shorter in the peripheral direction than the lateral flank facing the viewer of FIG. 17. In the region following the flank 90 in the driving rotation direction, the axial thickness of the exemplified tooth has an axial step 92 abruptly reduced on the lateral flank facing the viewer. The axial step 92 runs away from the viewer of FIG. 17.

The dimensions of the axially thicker teeth 36a, 46a, and 56a in this peripheral direction start from the common front flank 88 on the side facing the viewer of FIG. 17, and therefore are on the opposite, distant side It is shorter. The axially thicker teeth therefore have a roughly L-shaped peripheral cross section.

The axial step portion 92 may be a part of a recessed portion for receiving an outer link plate of a bicycle chain 28 in space.

FIG. 18 is a perspective view illustrating the smallest sprocket R12 of the sprocket arrangement 30 as viewed obliquely from the outside. Because the chain 28 has a particularly pronounced skew about the longitudinal center plane when it is engaged with the smallest sprocket R12, and the longitudinal center plane is orthogonal to the sprocket rotation axis RA of the bicycle 10 and is formed on the smallest sprocket R12 The axially thicker teeth 96a have a different configuration compared to the axially thicker teeth formed on other sprockets (except for the sprocket R7).

On the smallest sprocket R12, the size of the lateral flank of the larger sprocket or the largest sprocket R1 facing the neighbor is larger than that of the lateral flank of the largest sprocket R1. size. The latter lateral flank is the lateral flank of the viewer facing away from FIG. 18.

Secondly, the lateral flank facing the viewer of FIG. 18 protrudes on both sides in the peripheral direction beyond the lateral flank facing the viewer of FIG. 18. The axially thicker teeth 96 of the smallest sprocket R12 therefore have a roughly T-shaped peripheral cross section.
The following preferred examples are intended to facilitate a better understanding of the present invention.

1. A bicycle rear wheel sprocket arrangement (30) rotatable about a common sprocket rotation axis (RA) defining an axial direction and a radial direction orthogonal thereto, comprising a plurality of sprocket wheels having different sizes and number of teeth (R1-R12), the sprockets are coaxially arranged about the sprocket rotation axis (RA) and connected to each other for rotation around the sprocket rotation axis (RA) joint, wherein the sprocket configuration (30) has an inclusion The first part configuration (32) of the largest sprocket (R1), and the second part configuration (34) including a plurality of sprockets (R3-R12) integrally formed with each other,
One of the first and second partial configurations (32, 34) has a plurality of elastically deformable latches (60c), which are different from the others. The plurality of matching latches of the partial configuration (32) are formed (40) into a latch engagement, wherein the latch engagement stabilizes the two partial configurations (32, 34) to prevent each other from being removed in the axial direction .

2. The bicycle rear wheel sprocket configuration (30) according to Example 1, wherein the latch formation (60c) or / and the matching latch formation (40) are related to the individual partial configuration (32, 34) containing them ) Is integrally formed.

3. The bicycle rear wheel sprocket arrangement (30) according to example 1 or 2, wherein the latch shapes (60c) have axial fixing protrusions (60c), and the axial fixing protrusions are self-contained by the portion The partial arrangement (34) protrudes axially and has an axial distance from a part area (70c). The axial fixing protrusions protrude from the root area from the part arrangement (34) containing them. The fixing protrusion has a latching lug (80) protruding from the individual axial protrusion (60c) in a peripheral direction of the sprocket rotation axis (RA) or / and in a radial direction.

4. According to the bicycle rear wheel sprocket configuration (30) of Example 3, at least one of the axial fixing protrusions (60c), preferably all of the axial fixing protrusions (60c), is formed with a matching latch ( 40) A fixed portion (64) is held in a holding space (84) in an axially delimited manner, the holding space (84) is tied in a first direction by the latching lug (80) and relative to One of the first directions and the second direction are delimited by a holding profile (71), preferably the root region (70c), the holding profile is configured to have an axial distance from the latch lug and parallel to the latch The locking lug (80) extends.

5. The bicycle rear wheel sprocket arrangement (30) according to example 3 or 4, wherein the axial fixing protrusions (60c) are deformable in a direction orthogonal to the rotation axis (RA) of the sprocket, and are relatively It is preferably rigid in the axial direction.

6. The bicycle rear wheel sprocket arrangement (30) according to one of the preceding examples, wherein it has an axial protrusion (60b, 60c) preferably orthogonal to the sprocket rotation axis (RA) as a stop Protrusions (60b, 60c), the stop protrusions have a stop surface (74, 82) facing an action direction, and a contour component of the action direction is orthogonal to the sprocket rotation axis (RA), and In each case, one stop portion (76, 84) of the matching stop formation (40), and preferably a matching latch formation (40), abuts against it.

7. The bicycle rear wheel sprocket arrangement (30) according to Example 6, wherein it has an axial protrusion (60a) preferably orthogonal to the sprocket rotation axis (RA) as a matching stop protrusion (60a) The matching stop protrusions have a matching stop surface (66) facing a reverse action direction, and the reverse action direction has a contour component orthogonal to the sprocket rotation axis (RA), and matches in each case. The stop formation (40), and in particular a stop portion (68) of a matching latch formation (40), abuts against it, wherein the action direction and the counter-action of the stop surface and the matching stop surface In the peripheral direction of the direction, the radial contour components or / and the contour components adjacent to the same matching stop are formed facing opposite directions.

8. The bicycle rear wheel sprocket configuration (30) according to example 7, wherein at least some of the matching stop projections (60a), preferably all of the matching stop projections (60a), Both have an oblique surface (70) at its freely protruding longitudinal end, wherein the matching stop surface (66) is axially disposed between the oblique surface (70) and a partial area (70a), The matching stop projections (60a) protrude from the root region (70a) from the portion configuration (34) that includes them, and the inclined surface (70) is inclined in the following manner, i.e., at its A point of axial migration upward in the direction of the root region (70a) is near the matching stop surface (66) in the radial direction or / and in the peripheral direction.

9. According to one of Examples 3 to 8, including the bicycle rear wheel sprocket arrangement (30) of Example 6, wherein at least some of the axial fixing protrusions (60c) of the axial fixing protrusions (60c) are preferably all The axially fixed projection (60c) is also a blocking projection.

10. According to one of Examples 3 to 9, including the bicycle rear wheel sprocket arrangement (30) of Examples 3, 6, and 7, the axial protrusions (60a, 60c) form a plurality of protrusion groups ( 62), each of which has at least one axially fixed projection (60c) and a matching stop projection (60a).

11. The bicycle rear wheel sprocket arrangement (30) according to the preamble of Example 1 or one of the foregoing examples, wherein the mating latch shapes (40) have a hub region (32a) connected to a sprocket A plurality of sprocket spokes (38, 40) in the area (32b), the hub area being arranged radially closer to the sprocket rotation axis (RA) and designed for transmission from the sprocket configuration (30) Torque to a rear wheel hub, the sprocket area is located radially away from the sprocket rotation axis (RA) and is designed for transmission between a bicycle chain (28) and the sprocket arrangement (30) force.

12. The bicycle rear wheel sprocket arrangement (30) according to example 11, wherein the sprocket spokes (38, 40) include a smaller number of inner sprocket spokes (38) radially disposed on a more inner side. And a larger number of outer sprocket spokes (40) radially disposed on the more outer side, wherein the matching latch shapes (40) include a plurality of outer spokes (40) and preferably only the outer spokes (40) .

13. The bicycle rear wheel sprocket arrangement (30) according to example 11 or 12, including example 10, wherein the sprocket spokes (38, 40) form a plurality of spokes each having at least two sprocket spokes (40) Group (41), where each spoke group (41) interacts with a protrusion group (62) to form another joint combination.

14. The bicycle rear wheel sprocket arrangement (30) according to Example 13, wherein the sprocket spokes (40) are directly connected to each other in the peripheral direction, and preferably, the two sprocket spokes are directly connected to each other. (40), which forms a spoke group (41).

15. The bicycle rear wheel sprocket arrangement (30) according to one of Examples 11 to 14, wherein the sprocket spokes (38, 40) make the driving rotation direction (DR) of the sprocket arrangement (30) One of the same sprocket spokes (38, 40) on the radial portion is placed on the more inner side before the spoke portion and the spoke portion is placed radially on the outer side in such a way that The radial contour component has a contour component in the peripheral direction. The sprocket spokes (38, 40) are particularly preferably curved convexly when viewed opposite to the driving rotation direction (DR).

16. The bicycle rear wheel sprocket configuration (30) according to the preamble of Example 1 or one of the foregoing examples, wherein the first part configuration (32) includes the largest sprocket (R1) and the second largest sprocket (R2), wherein the largest sprocket (R1) and the second largest sprocket (R2) are integrally formed with each other.

17. The bicycle rear wheel sprocket arrangement (30) according to example 16, wherein in a radial strengthening region (51) between a root circle of the largest sprocket (R1) and the second largest sprocket (R2) The first partial configuration (32) may have an axial rounded edge (50) around the rotation axis of the sprocket, and the axial rounded edge is preferably designed to face the second large sprocket ( R2) is an axial depression (50a) on the side of the reinforcing area (51).

18. The bicycle rear wheel sprocket arrangement (30) according to example 16 or 17, including one of examples 11 to 15, wherein the sprocket spokes (40) extend radially outwardly as in the largest sprocket ( R1) is as far as the sprocket area (32b), where the first part is arranged (32) in a radial area of the chain between the root circle and the top circle of the second large sprocket (R2) The number of spokes (40) is almost half of the number of teeth of the second largest sprocket (R2).

19. The bicycle rear wheel sprocket configuration (30) according to example 18, wherein when the first part configuration (32) is viewed in the axial direction, each sprocket spoke (40) and the second largest chain Each second tooth (46a) of the wheel (R2) is disposed at the same peripheral position.

20. The bicycle rear wheel sprocket arrangement (30) according to example 19, wherein the second largest sprocket (R2) in at least one peripheral area is disposed at least in the same peripheral position as the spokes of the sprocket (40). The teeth (46a) have a thicker axial design than the teeth (46b) directly adjacent to the teeth in the peripheral direction.

21. The bicycle rear wheel sprocket arrangement (30) according to the preamble of Example 1 or one of the foregoing examples, wherein the second partial arrangement (34) has between 6 and 12 integrally formed with each other The formation of the axial continuous sprocket (R3-R12).

22. The bicycle rear wheel sprocket configuration (30) according to example 21, wherein the second partial configuration (34) includes the third largest sprocket (R3) of the sprocket configuration (30).

23. The bicycle rear wheel sprocket configuration (30) according to example 21 or 22, wherein the second partial configuration (34) includes the smallest sprocket (R12).

24. The bicycle rear wheel sprocket arrangement (30) according to one of Examples 21 to 23, wherein for the second part arrangement (34), it is composed of a sprocket and a smaller sprocket adjacent to it. For at least one pairing, preferably for each pairing, the sprocket is connected to the adjacent smaller sprocket by a plurality of webs (54) integrally formed with the two sprocket wheels, wherein the sprocket is connected to the The number of webs (54) of the second sprocket is smaller than the number of teeth of the smaller sprocket of the pair.

25. The bicycle rear wheel sprocket configuration (30) according to Example 24, wherein the number of the webs and the number of teeth of the paired smaller sprocket that are directly adjacent in the axial direction and are connected by the webs Have a common integer factor.

26. The bicycle rear wheel sprocket arrangement (30) according to example 24 or 25, wherein in a pair consisting of two sprocket wheels that are axially directly adjacent and integrally connected to each other, each web is connected to the smaller chain One tooth of the wheel is arranged at the same peripheral position on the paired smaller sprocket.

27. The bicycle rear wheel sprocket arrangement (30) according to one of examples 24 to 26, wherein whenever the smaller sprocket has an even number of teeth and the number of mating webs is exactly the smaller sprocket of the neighbor As many as half of the even number of teeth.

28. The bicycle rear wheel sprocket configuration (30) according to example 27, wherein when the second part configuration (34) is viewed in the axial direction, the second part configuration (34) is controlled by a chain At least one pair consisting of a wheel and an adjacent smaller sprocket with an even number of teeth, preferably for each pair, each web (54) of the adjacent smaller sprocket and each second tooth ( 56a) are placed at the same peripheral location.

29. The bicycle rear wheel sprocket arrangement (30) according to example 26 or example 28, wherein, for the at least one pair, at least in a peripheral area, the same is disposed at the same peripheral position as the web (54) The teeth (56a) of the adjacent smaller sprocket have a thicker axial design than the teeth (56b) of the teeth directly adjacent to the peripheral direction.

30. A bicycle rear wheel sprocket arrangement (30) according to one of the preceding examples, wherein it has 8 to 14 sprocket wheels (R1-R12), wherein the smallest sprocket wheel (R12) has no more than 12 wheels, It is preferably not more than 10, preferably more accurate is 10 teeth, or / and the largest sprocket (R1) thereof is not less than 50, preferably not less than 52, and particularly preferably accurate is 52 tooth.

31. The bicycle rear wheel sprocket arrangement (30) according to one of the preceding examples, wherein on a plurality of sprocket wheels (R1-R6, R8-R12) with even teeth, preferably on all chains with even teeth On the wheels (R1-R6, R8-R12), an axially thicker tooth (36a, 46a, 56a) and an axially thin tooth (36b, 46b, 56b) are continuously arranged in a staggered manner on the periphery, respectively. The direction is at least in a peripheral area.

32. The bicycle rear wheel sprocket arrangement (30) according to the preamble of Example 1 or according to one of the foregoing examples, wherein the smallest sprocket has at least one peripheral region in the peripheral direction, preferably along the entire The circumferentially staggered axially thicker and axially thinner teeth, where the axially thicker and axially thinner teeth face the adjacent larger sprocket's transverse tooth belly is disposed on a common virtual envelope surface. In the peripheral region, the axially thicker teeth starting from the common envelope surface are axially farther away from the adjacent larger sprocket than the axially thinner teeth disposed therebetween in the peripheral direction.

33. The bicycle rear wheel sprocket arrangement (30) according to example 32, wherein for a plurality of axially thicker teeth, preferably for all thicker teeth of the smallest sprocket, the larger sprocket closest to the neighbor The lateral flank has a larger size in the peripheral direction than the opposite lateral flank. The flank face is away from the adjacent larger sprocket, and the lateral flank facing the larger sprocket facing the adjacent sprocket. Extending above the transverse flank, the transverse flank faces the larger sprocket from the adjacent at its longitudinal end in the peripheral direction in front of the driving rotation direction and at its trailing longitudinal end.

34. The bicycle rear wheel sprocket arrangement (30) according to example 33, wherein at least one axially thicker tooth is preferable to a plurality of axially thicker teeth, and particularly preferably to all of the axially thicker teeth. Where the transition from the flank that is longer in the peripheral direction to the flank that is shorter in the peripheral direction is stepped at at least one longitudinal end of the tooth, preferably at both longitudinal ends, It is preferably a single stage.

35. A bicycle drive assembly (12) consisting of a bicycle chain (28) and a bicycle rear wheel sprocket arrangement (30), the bicycle chain (28) having paired by outer and inner link plates (28a 28b) rollers connected to each other in a staggered manner along the longitudinal direction of the chain, the bicycle rear wheel configuration (30), according to one of the foregoing examples, including example 29, can be driven with the bicycle chain (28) Force-transmitting positive-locking engagement, where the axially thicker teeth (36a, 46a, 56a) have a dimension in the axial direction that is greater than the clear width between the inner link plate pairs (28b), and therefore the The equal axially thicker teeth (36a, 46a, 56a) can completely enter only one tooth entry space as expected, and the tooth entry space is bounded by the link plate outside the bicycle chain.

36. The bicycle rear wheel sprocket configuration (12) according to Example 35, wherein for at least some of the sprocket wheels (R2-R6, R8-R12), especially those with even number of teeth, When a sprocket (R2-R6, R8-R12) with an even number of teeth is positively locked and engaged with the bicycle chain (28), a web (54) or a sprocket spoke (40) is axially oppositely disposed. In the axial direction of the larger chain wheels (R1-R5, R7-R11) adjacent to a plurality of outer link plates of the longitudinal portion of a chain, and preferably all of the outer link plates, the longitudinal portion of the chain and The sprockets (R2-R6, R8-R12) are positively locked in engagement.

10‧‧‧ Bicycle

12‧‧‧ Bicycle drive assembly

14‧‧‧frame

16‧‧‧ front wheel

18‧‧‧ rear wheel

20‧‧‧handle

22‧‧‧ Saddle

24‧‧‧ front chain ring

26‧‧‧ pedal crank

28‧‧‧ Bicycle chain

28a‧‧‧ Outer link plate pairing

28b‧‧‧Internal link plate pairing

30‧‧‧ rear wheel sprocket configuration

32‧‧‧Part 1 configuration, transmission

32a‧‧‧ Radial inner hub area

32b‧‧‧Radial outer sprocket area

32c‧‧‧Spoke area

34‧‧‧ Part II configuration

36a, 36b, 46a, 46b, 56a, 56b‧‧‧tooth

38‧‧‧Inner sprocket spokes

40‧‧‧ Outer sprocket spokes

41‧‧‧Spoke Group

42‧‧‧ coupling ring area

44‧‧‧ radial length

48‧‧‧Axial clearance

50‧‧‧Axial rounded edge

50a‧‧‧ sunken

50b‧‧‧ prominent

51‧‧‧Enhanced area

52‧‧‧Sprocket

54‧‧‧ Web

58‧‧‧Axial clearance

60a, 60b, 60c ‧‧‧ axial protrusion

62‧‧‧ Burst Group

64‧‧‧ Junction

66‧‧‧ matching stop surface

68, 76, 86‧‧‧ bounded surfaces

70‧‧‧ oblique surface

71‧‧‧outer surface

70a, 70c‧‧‧Root area

74, 84‧‧‧ Stop surfaces

78‧‧‧Receiving space

80‧‧‧ latch lug

82‧‧‧ keep space

88, 90‧‧‧ Tooth

92‧‧‧ axial step

96, 96a‧‧‧Axial thicker teeth

R1 ~ R12‧‧‧Sprocket

RA‧‧‧Sprocket rotation shaft

DR‧‧‧Drive rotation direction

The present invention will be explained in more detail with reference to the accompanying drawings, in which:

FIG. 1 shows a schematic diagram of a bicycle having a bicycle driving assembly according to the present invention,

FIG. 2 shows a perspective view of a bicycle rear wheel sprocket arrangement according to the invention of the bicycle drive assembly of FIG. 1 viewed obliquely from the outside,

FIG. 3 shows a side view of a sprocket arrangement viewed from FIG. 2 orthogonal to the rotation axis of the sprocket,

FIG. 4 shows a longitudinal cross-sectional view of the sprocket arrangement of FIGS. 2 and 3 along a radial half of a section containing a rotation axis of the sprocket,

Fig. 5 shows the sprocket arrangement of Figs. 2 to 4 along the axis of rotation of the sprocket on the outside of the bicycle of Fig. 1, that is, an axial view in a direction orthogonal to the longitudinal center plane of the axis of rotation of the sprocket,

FIG. 6 shows an axial view of the sprocket arrangement of FIGS. 2 to 5 in a relative viewing direction compared to FIG. 5,

FIG. 7 shows a perspective view of the first part of the sprocket arrangement of FIGS. 2 to 6 obliquely from the outside,

FIG. 8 shows a cross-sectional view of the first part of FIG. 7 arranged along a section including a sprocket rotation axis RA,

Fig. 9 shows an axial view of the first part of Figs. 7 and 8 arranged from the outside,

Fig. 10 shows an axial view of the first portion of Figs. 7 to 9 arranged from the inside,

FIG. 11 shows a perspective view of the second part of the sprocket arrangement of FIGS. 2 to 6 obliquely from the outside,

Fig. 12 shows a side view of the second part of the sprocket arrangement of Figs. 2 to 6 whose viewing direction is orthogonal to the rotation axis of the sprocket,

FIG. 13 shows an axial view of the second part of the sprocket arrangement of FIGS. 2 to 6 from the inside,

FIG. 14 shows a perspective view of the second part disposed from the inside,

FIG. 15 shows an enlarged detail of an area of one of the two largest sprockets configured in the second part of FIG. 14,

Figure 16 shows a perspective view of the sprocket configuration with these two parts arranged obliquely from the rear,

FIG. 17 shows an axial view of the end side of any sprocket other than the smallest sprocket arrangement of the sprocket arrangement, the end side facing away from the smallest sprocket arrangement of the sprocket arrangement of FIGS. 2 to 6, and

FIG. 18 shows a perspective view of the smallest sprocket in a sprocket arrangement obliquely from the outside.

Claims (16)

A bicycle rear wheel sprocket configuration capable of rotating about a common sprocket rotation axis defining an axial direction and a radial direction orthogonal thereto, comprising a plurality of sprocket wheels having different sizes and number of teeth, and the sprocket wheels are about the chain The wheel rotation axis is coaxially arranged and connected to each other for rotation around the sprocket rotation axis joint, wherein the sprocket configuration has a first partial configuration including a largest sprocket, and a plurality of sprocket including one integrally formed with each other. The second part of the configuration, It is characterized in that one of the first and second partial configurations has a plurality of elastically deformable latches formed, and the elastic deformable latches are formed with a plurality of matching latches of the individual other parts. Locking to form a latching engagement, wherein the latching engagement stabilizes the two parts configuration to prevent each other from being removed in the axial direction. For example, the bicycle rear wheel sprocket configuration of claim 1, wherein the matching latch forming includes a plurality of sprocket spokes connecting a hub region to a sprocket region, and the hub region is arranged in a radial direction. Close to the sprocket rotation axis and designed to transmit torque from the sprocket configuration to a rear wheel hub, the sprocket area is positioned radially away from the sprocket rotation axis and is designed for a bicycle Force is transmitted between the chain and the sprocket arrangement. If the bicycle rear wheel sprocket configuration of claim 1 or 2 is characterized in that the first part configuration includes the largest sprocket and the second largest sprocket, wherein the largest sprocket and the second largest sprocket are integrated with each other地 Forming. A bicycle rear wheel sprocket configuration capable of rotating about a common sprocket rotation axis defining an axial direction and a radial direction orthogonal thereto, comprising a plurality of sprocket wheels having different sizes and number of teeth, and the sprocket wheels are about the chain The wheel rotation axis is coaxially arranged and connected to each other for rotation around the sprocket rotation axis joint, wherein the sprocket configuration has a first partial configuration including a largest sprocket, and a plurality of sprocket including one integrally formed with each other. The second part of the configuration, It is characterized in that the first part configuration includes a largest sprocket and a second largest sprocket, wherein the largest sprocket and the second largest sprocket train are integrally formed with each other. The bicycle rear wheel sprocket arrangement according to any one of claims 1 to 4, characterized in that the second part configuration has a row of 6 to 12 axially continuous sprocket formed integrally with each other. . A bicycle rear wheel sprocket configuration capable of rotating about a common sprocket rotation axis defining an axial direction and a radial direction orthogonal thereto, comprising a plurality of sprocket wheels having different sizes and number of teeth, and the sprocket wheels are about the chain The wheel rotation axis is coaxially arranged and connected to each other for rotation around the sprocket rotation axis joint, wherein the sprocket configuration has a first partial configuration including a largest sprocket, and a plurality of sprocket including one integrally formed with each other. The second part of the configuration, It is characterized in that the second part arrangement has a row of axially continuous sprockets formed integrally with each other between 6 and 12. If the bicycle rear wheel sprocket configuration of claim 5 or 6 is characterized in that, for at least one pair of the second part configuration consisting of a sprocket and a smaller sprocket adjacent to it, preferably For each pairing, the sprocket is connected to the adjacent smaller sprocket through a plurality of webs integrally formed with the two sprocket wheels, where the number of webs connecting the two sprocket wheels is less than The number of teeth of the paired smaller sprocket. The bicycle rear wheel sprocket arrangement of claim 7, characterized in that, for the at least one pairing, at least in a peripheral area, the teeth of a smaller adjacent sprocket placed at the same peripheral position as the web It has a thicker axial design than the teeth directly adjacent to the peripheral direction. For example, the bicycle rear wheel sprocket arrangement of any one of claims 1 to 8, characterized in that it has 8 to 14 sprocket wheels, wherein the smallest sprocket wheel has no more than 12 and preferably no more than 10 Preferably, it is more accurate to 10 teeth, or / and the largest sprocket does not have less than 50, preferably not less than 52, and particularly preferably accurate to 52 teeth. For example, a bicycle rear wheel sprocket arrangement according to any one of claims 1 to 9, characterized in that, on a plurality of sprocket wheels with even teeth, preferably on all sprocket wheels with even teeth, one axially thicker The teeth and an axially thin tooth system are continuously arranged in a staggered manner in at least one peripheral region in the peripheral direction, respectively. The bicycle rear wheel sprocket arrangement according to any one of claims 1 to 10, characterized in that the smallest sprocket has at least one peripheral area in the peripheral direction, preferably along the axial direction of the entire peripheral stagger. Thicker and axially thinner teeth, where the axially thicker and axially thinner teeth of the adjacent larger sprocket are located in the peripheral area on a common virtual envelope surface, where the The axially thicker teeth starting from the common envelope surface extend more axially away from the adjacent larger sprocket than the axially thinner teeth disposed therebetween in the peripheral direction. A bicycle rear wheel sprocket configuration capable of rotating about a common sprocket rotation axis defining an axial direction and a radial direction orthogonal thereto, comprising a plurality of sprocket wheels having different sizes and number of teeth, and the sprocket wheels are about the chain The wheel rotation axis is coaxially arranged and connected to each other for rotation around the sprocket rotation axis joint, wherein the sprocket configuration has a first partial configuration including a largest sprocket, and a plurality of sprocket including one integrally formed with each other. The second part of the configuration, It is characterized in that the smallest sprocket has axially thicker and axially thinner teeth that are staggered along the entire periphery in at least one peripheral area, preferably along the entire periphery, wherein the axially thicker and axially thinner teeth The transverse flank of the larger sprocket facing the two adjacent teeth is disposed in the peripheral area on a common virtual envelope surface, wherein the axially thicker teeth from the common envelope surface are proportional to the peripheral direction The axially thinner teeth disposed therebetween extend more axially away from the adjacent larger sprocket. For example, the bicycle rear wheel sprocket configuration of claim 11 or 12, characterized in that, for a plurality of axially thicker teeth, it is preferable for all the thicker teeth of the smallest sprocket to be placed closer to the nearest neighbor. The lateral flank of the sprocket has a larger size in the peripheral direction than the opposite lateral flank of the same tooth. The flank of the sprocket is away from the larger sprocket of the neighbor, and the larger sprocket facing the adjacent is The transverse flank protrudes above the transverse flank, and the transverse flank is located in the peripheral direction with its longitudinal end in front of the driving rotation direction and its trailing longitudinal end face away from the adjacent larger sprocket. For example, the bicycle rear wheel sprocket arrangement of claim 13 is characterized in that at least one axially thicker tooth is preferable to a plurality of axially thicker teeth, and particularly preferably to all of the axially thicker teeth. The transition from the longer flank in the peripheral direction to the shorter flank in the peripheral direction is stepped at at least one longitudinal end of the tooth, preferably at both longitudinal ends, preferably It is a single order. A bicycle drive assembly is composed of a bicycle chain and a bicycle rear wheel sprocket arrangement. The bicycle chain has rollers connected to each other in a staggered manner along the longitudinal direction of the chain by pairing the outer and inner link plates. The bicycle rear wheel configuration, according to one of the aforementioned claims, including claim 8, can be positively locked into engagement with the bicycle chain by driving force transmission, It is characterized in that the dimension of the axially thicker teeth in the axial direction is larger than the net width between the pair of inner link plates, and therefore the axially thicker teeth can be completely as expected only A tooth enters the space, and the tooth enters the space is bounded by a link plate outside the bicycle chain. If the bicycle drive assembly of claim 15 is characterized in that for at least some of the sprocket wheels, particularly those with even number of teeth, whenever a sprocket train with particularly one of the even number of teeth is formed with the bicycle chain When the force transmission is positively locked and engaged, a web or a sprocket spoke is axially oppositely disposed on a plurality of outer link plates, preferably all adjacent ones of the outer link plates, toward a longitudinal portion of a chain. In the axial direction, the longitudinal portion of the chain is in positive lock engagement with the sprocket.