Multi-layer pinion arrangement and modular system for forming multi-layer pinion arrangement

Abstract

The utility model discloses a multi-layer pinion configuration (Ap) which is used for being installed on a bicycle rear wheel transmission device (Dd) in a mode of transmitting torque to a bicycle rear wheel shaft (Ar), and a modular system forming the multi-layer pinion configuration (Ap). The pinion arrangement (Ap) comprises an inner final-stage pinion arrangement (Pti), a first pinion set (Sc1) which can be connected to the inner final-stage pinion arrangement (Pti) in a connection region (Ca) of the inner final-stage pinion arrangement (Pti), and an outer final-stage pinion arrangement (PTo). The first pinion set (Sc1) is rotatably mounted on the outside relative to the transmission device (Dd) by means of a rotary bearing device (Db) of the multi-layer pinion arrangement (Ap).

Description

Technical Field

[0001] The present disclosure relates to a multi-layer pinion configuration, and a modular system for forming a multi-layer pinion configuration.

[0002] Multi-layer pinion arrangements of the same type are also synonymously referred to in the bicycle industry and in the following description as pinion freewheels or flywheels, which on bicycles form part of a drive train for transmitting drive from a toothed disc on the bottom bracket of the bicycle to the rear wheel.

[0003] Unless expressly stated otherwise, directional terms such as "left," "right," "front," "rear," "up," and "down" used in this disclosure correspond to the perspective of a rider of a bicycle. The same is true for industry-conventional directional terms such as "inboard" (left or to the left or toward a larger cog on a pinion cassette) and "outboard" (right or to the right or toward a smaller cog on a pinion cassette) that relate to the shifting process or direction or pinion position on a pinion cassette on the rear wheel of a bicycle. Background Art

[0004] Bicycles are usually equipped with a transmission system, such as a chain transmission system. Such bicycle transmission systems are used to transfer a transmission torque from the rider to the rear drive wheel of the bicycle, thereby driving the bicycle in this way. Such bicycle transmission systems can, for example, transfer torque from a front sprocket arrangement via a chain to a rear pinion, such as a pinion of a multi-speed pinion cassette, thereby driving the rear drive wheel.

[0005] The front sprocket arrangement of a bicycle drivetrain may have one or more front sprockets, also referred to in the industry as chainrings.

[0006] The rear sprocket on a bicycle is usually referred to as a pinion. A plurality of rear sprockets or pinions may be referred to as a flywheel, a pinion flywheel or a pinion set. Such a pinion flywheel is usually configured in such a way that it can be fastened to a one-way freewheel element of a rear driving wheel. For this purpose, the pinion flywheel can be fastened to the one-way freewheel body of the rear driving wheel, for example, by means of a multi-gear groove connection or a transmission profile and / or by means of a threaded connection.

[0007] The pinion cassette of a bicycle comprises a plurality of pinions spaced axially about the rear wheel axle, these pinions having different numbers of teeth in stages. Depending on the specific gear ratio selected by the rider, the bicycle chain is placed on one of the pinions by means of the rear derailleur, thereby determining the gear ratio in conjunction with the number of teeth on the chainring on the bottom bracket and the parameters applied by the rider, such as torque and cadence.

[0008] In recent years, the bicycle industry, primarily in the mountain bike sector, has gradually reduced the number of bottom bracket chainrings from the traditional three chainrings of different sizes to first two and, at least in the high-end market segment, mostly to a single chainring. With this bicycle transmission, which is also often known in the industry as "1x" or "1×", the drive train is greatly simplified and its reliability and low maintenance are increased. In addition, the shifting operation and the shifting logic are greatly simplified for the rider, which is reduced to only one gear lever.

[0009] Furthermore, the front derailleur and its control device as well as the devices required for fastening them to the bicycle frame and the bicycle handlebars can also be omitted in the area of ​​the bottom bracket. Without a front derailleur, additional chainrings and shift levers and accessory devices, the weight of the bicycle is also significantly reduced.

[0010] In bicycles with an electric auxiliary drive, for example for reasons of space and to simplify the drive train, in most cases, instead of using a plurality of shiftable toothed discs, only one toothed disc is provided.

[0011] But without providing a certain sub-factor of the gear ratio range on the bicycle, which is previously provided by multiple chainrings on the bottom bracket and is usually in the range of 180% to 200%, it is necessary to significantly increase the gear ratio range provided by the pinion cassette.

[0012] This necessity has led to the development of pinion cassettes that have not only very small pinions on the outside with as few as 11 teeth or less, and in particular as few as 9 teeth, but also very large pinions on the inside with up to 50 teeth and more. As a result, these cassettes achieve a gear ratio range of up to or exceeding 500%, thereby providing the appropriate gear ratio in almost all riding conditions.

[0013] However, a pinion flywheel with such a large pinion on the inner side would cause weight problems, especially since the pinion flywheel is traditionally mostly composed of several disc-shaped pinions, each of which is directly connected to the one-way freewheel transmission of the rear hub.

[0014] In order to solve the weight problem of such pinion flywheels in particular, there are two basic main solutions so far. One of the solutions is to use a so-called pinion star wheel (Ritzel-Spidern), in which a plurality of adjacent pinion rings are arranged on a common carrier.

[0015] The pinion ring is defined in that, unlike a disk-shaped flywheel pinion or plug-in pinion, it is not arranged directly on the transmission of the rear wheel hub and is not connected to the transmission in a torque-transmitting manner, but is designed as a relatively narrow ring in the radial direction.

[0016] Thus, for a pinion flywheel with a spider structure (typically, for two or more adjacent pinion rings that are both fastened to a pinion spider), the connection to the transmission and the torque transfer from the pinion teeth to the transmission occur in combination.

[0017] However, the current flywheel has a large number of pinions, usually in the range of ten or more pinions. Therefore, it is necessary to set up a plurality of relatively flatter star wheels and fasten usually 2 to 4 pinions to each of the flat star wheels, or it is necessary to provide a single pinion star wheel with a larger thickness or extension in the axial direction in three dimensions, so that multiple pinion rings can be placed side by side on the star wheel.

[0018] Therefore, both known approaches to star wheel pinion flywheels are not optimal with respect to the desired weight reduction and also result in a complex structure of the flywheel with a large number of components that are difficult to manufacture and install.

[0019] Another known approach to reducing the weight of a pinion flywheel with a very wide transmission ratio range is to construct the pinion flywheel at least partially as a self-supporting pinion set, which is also referred to in the industry as a dome flywheel.

[0020] In this case, either all pinions except the largest inner pinion are milled out of a solid piece of material, or as many intermediate pinions as possible are constructed between the largest and smallest pinions as a pinion ring, which is usually connected to form a conical or truncated cone-shaped, self-supporting, three-dimensional load-bearing structure by connecting elements such as rivets or pins. The latter solution is also known in the industry as a pinion set.

[0021] In general, a self-supporting gear set can be defined in a manufacturing-independent manner as consisting of three or more pinions, with an inner final pinion and an outer final pinion, wherein the inner and outer final pinions can be connected to a connecting element such as a star wheel, a carrier pinion, a miniature pinion set (minicluster) or a transmission, respectively. The third pinion, usually a plurality of intermediate pinions arranged between the inner and outer final pinions of the pinion set, is arranged in a cantilevered manner, i.e., it is not connected or directly connected to the star wheel, the carrier pinion or the transmission. Alternatively, these intermediate pinions are only directly connected to the inner and / or outer final pinions, or indirectly connected to the inner and / or outer final pinions via other adjacent pinions, as the case may be.

[0022] However, this concept for pinion sets also reaches its limits with increasing numbers of gears and pinion sizes. Pinion sets milled from solid require increasingly larger blanks and increasingly difficult and therefore more expensive manufacturing steps, while pinion sets with multiple pins or rivets arranged in a row become increasingly more expensive to manufacture, primarily due to the tolerance chains associated with them.

[0023] Prior art

[0024] In view of this, pinion flywheels with self-supporting pinion gear sets of smaller size have been developed, wherein one or more other pinion gear sets are connected on the outside, such as in the form of multi-component or one-piece miniature pinion gear sets. Publication DE 10 2010027 228 A1 discloses such a pinion flywheel, for example.

[0025] In this type of pinion flywheel, the outer final pinion of the pinion gear set is clamped axially and fixedly between adjacent components of the pinion flywheel, for example, between a micro pinion gear set and a tubular spacer.

[0026] However, when a high torque is applied to the smaller pinions of the pinion set, this clamping can lead to uncontrolled micro-rotations of the clamped outer final pinion due to the torsional elasticity of the pinion set. This micro-rotation can in turn lead to vibrations and thus to undesirable clicking or creaking noises. If this micro-rotation occurs frequently, it can also affect the fatigue strength of the pinion set. Utility Model Content

[0027] Based on the aforementioned prior art, the purpose of the present invention is to provide a pinion flywheel or a multi-layer pinion configuration, and a modular system for forming a pinion flywheel or a multi-layer pinion configuration, wherein the pinion flywheel and the modular system can overcome the aforementioned shortcomings.

[0028] Utility Model Specification

[0029] The solution of the present invention to achieve the above-mentioned object is a multi-layer pinion configuration and a modular system for forming the multi-layer pinion configuration according to the present disclosure.

[0030] Generally speaking, the multi-layer pinion arrangement is suitable for being mounted on a bicycle rear wheel transmission in a manner that transmits torque to the bicycle rear wheel axle. Suitable transmissions for accommodating the pinion arrangement usually have a toothing transmission profile arranged on the outer periphery of the transmission, while the pinion arrangement has a meshing profile on the inner periphery that corresponds to the shape of the transmission profile of the transmission so as to mesh with the transmission profile of the transmission in a form-fitting manner in a torque-transmitting manner.

[0031] The pinion arrangement comprises a plurality of pinion gears, wherein each pinion gear has at least one pinion gear having corresponding pinion gear teeth adapted to mesh with a bicycle chain in a torque-transmitting manner. The pinion gears of the pinion arrangement have an inner final pinion gear, a first pinion gear set, in particular a self-supporting pinion gear set, having a plurality of pinions, which is (can be) connected to the inner final pinion gear in a connection region of the inner final pinion gear, and an outer final pinion gear.

[0032] The pinion arrangement according to the disclosure is characterized by a rotary bearing arrangement, by means of which the first pinion set is rotatably supported in its outer region relative to the gear mechanism.

[0033] In contrast, the first pinion set in the prior art, as described at the outset, is usually accommodated on the outside in a clamped manner in the force flow extending axially along the rear wheel axle between adjacent pinions, pinion devices or spacing elements of the pinion arrangement and is therefore supported in a non-rotatable manner.

[0034] When a transmission torque is applied to the pinions of the first pinion gear set of such a pinion gear arrangement according to the prior art, in particular when a torque is applied to the smaller outer pinion gear of the first pinion gear set, the first pinion gear set itself attempts to twist elastically. When a certain limiting torque is exceeded, this leads to the clamping start torque being exceeded when the first pinion gear set is clamped on the outside, so that the first pinion gear set, which is clamped on the outside, suddenly starts to rotate by a small angular value.

[0035] This outwardly clamped start-up of the first pinion gear set and the subsequent rotation of the outwardly clamped first pinion gear set often results in undesirable noises such as rattling and creaking. Due to the uncontrolled occurrence of the start-up effect and the correspondingly sudden change in the force flow in the first pinion gear set, and due to the vibrations that occur in the process, this disadvantage can also affect the fatigue strength of the first pinion gear set.

[0036] Since the first pinion gear set is supported on the rotary bearing device on the outside so as to be rotatable relative to the transmission device according to the disclosure, this undesirable effect is avoided. When a transmission torque is applied to the pinions of the first pinion gear set, in particular the smaller pinions on the outside of the first pinion gear set, the rotatable support of the first pinion gear set on the outside causes the first pinion gear set to rotate controlled on the outside, so that it can deform elastically itself, and no strong starting effects or vibrations will occur in the first pinion gear set. This can improve the fatigue strength of the first pinion gear set and prevent the undesirable generation of noises, such as clicks and creaks. Based on the fatigue strength improved thereby, the first pinion gear set is also inclined to adopt a thin-walled and lightweight embodiment.

[0037] According to a preferred embodiment, the bearing device is formed by a spacing unit which is also suitable for determining the relative distance between at least two pinion devices of the pinion arrangement in the axial direction of the rear wheel axle when the pinion arrangement is mounted on the transmission.

[0038] In which, the bearing device is preferably suitable for transmitting installation tension force between at least two pinion devices of the pinion configuration along the axial direction of the rear wheel axle, wherein when the pinion configuration is mounted on the transmission device, the installation tension force is part of a closed force flow extending substantially parallel to the rear wheel axle through the transmission device and the pinion configuration.

[0039] Particularly preferably, the bearing arrangement is adapted both to determine the relative distance between the inner and outer final pinion arrangement in the axial direction of the rear wheel axle and to transmit the mounting tensioning force between the inner and outer final pinion arrangement.

[0040] The advantageous multifunctionality of the bearing device formed by means of the aforementioned embodiment is not only used to support the first pinion set rotatably on the outside, but also serves as a tensioning element to mount the pinion configuration on the transmission device, and also serves as a spacing element to determine the relative distance between at least two pinion devices of the pinion configuration.

[0041] The bearing arrangement is preferably adapted to determine the axial relative distance between the inner final pinion arrangement and the outer pinion of the first pinion gear set. Thus, the bearing arrangement serves as a distance arrangement in a dual function solution for determining the correct width of the first pinion gear set.

[0042] Particularly preferably, the bearing device is suitable for determining relative distances in the axial direction of the rear wheel axle in a multifunctional scheme, and is suitable for transmitting installation tension forces between the inner and outer final pinion devices and the outer pinion of the first pinion set along the axial direction of the rear wheel axle. In other words, it is suitable for determining all relevant relative distances between the inner and outer final pinion devices and the outer pinion of the first pinion set and for transmitting all basic installation tension forces.

[0043] Likewise, the bearing device is preferably made of a non-metallic material, for example an organic polymer. This saves manufacturing costs, prevents corrosion, and simplifies the micro-movements of the pinion arrangement of the pinion gear, in particular the elastic rotation of the outer final pinion of the first pinion gear set, without generating undesirable noise or vibrations.

[0044] According to a preferred embodiment, the outer final pinion arrangement comprises a further pinion set, which is preferably designed as a substantially integrally formed module. A substantially integrally formed module is understood to mean that the pinion set is either integral in material, for example milled from solid material, or the pinion set is composed of a plurality of pinion arrangements or pinions, for example by welding, laser welding or by pinning or riveting.

[0045] Preferably, the further pinion gear set has an engagement contour on the inner circumference that meshes with the transmission contour of the transmission in a torque-transmitting manner, wherein the engagement contour of the further pinion gear set corresponds in shape to the transmission contour of the transmission.

[0046] According to another preferred embodiment, the pinion arrangement comprises a screw plug device adapted to mesh with an outer internal thread of the transmission device in order to mount and fasten the pinion arrangement on the transmission device. By means of the screw plug device, the further pinion gear set can be pushed or pressed onto the transmission device in the axial direction of the rear wheel axle relative to the bearing device. In the process, a closed force flow is formed which extends through the transmission device and the pinion arrangement substantially parallel to the rear wheel axle and connects the pinion arrangement to the transmission device.

[0047] According to another preferred embodiment, the further pinion gear set comprises at least one pinion gear having a root diameter which is smaller than the outer diameter of the transmission in the transmission contour region. The pinion center plane of the at least one pinion gear, preferably the pinion center planes of the two pinions of the further pinion gear set, extends on the outside outside the axial end face of the transmission when the pinion gear arrangement is mounted on the transmission.

[0048] This makes it possible to fit pinions with a particularly low number of teeth into the pinion arrangement, thereby advantageously increasing the transmission ratio range of the pinion arrangement. The further pinion set can thus in particular comprise one or more pinions whose root circle diameter and the largest possible inner diameter are smaller than the outer diameter of the transmission in the region of the transmission contour of the transmission.

[0049] Nevertheless, the fastening of these extremely small pinions and the transmission of torque from these pinions to the transmission are ensured in the following way: the other pinion set has a meshing profile on the inner circumference that corresponds to the transmission profile shape of the transmission, in particular on the inside, and in particular in the area of ​​at least one pinion of the pinion set whose root circle diameter is greater than the outer diameter of the transmission.

[0050] The above-mentioned embodiments in connection with the further pinion can also be realized independently of the presence of the above-mentioned rotary bearing device or the spacing unit.

[0051] According to another preferred embodiment, the pinion is configured to have at least three axial sections spaced apart from each other in the axial direction of the rear wheel axle when mounted on the transmission device, and these sections each have a meshing contour corresponding to the transmission contour shape of the transmission device on the inner circumference so as to mesh with the transmission contour in a shape-fitting manner in order to transmit torque.

[0052] For this purpose, preferably, at least one further pinion gear is arranged axially between the first pinion gear set and the further pinion gear set. The further pinion gear has a meshing profile corresponding to the transmission profile shape of the transmission device on the inner circumference so as to mesh with the transmission profile of the transmission device in a form-fitting manner in a torque-transmitting manner.

[0053] This results in a triple torque-transmitting connection between the pinion arrangement and the transmission, i.e. at three locations spaced apart from one another in the axial direction of the rear wheel axle. This triple torque-transmitting connection is preferably provided at the inner final pinion arrangement, at the further pinion arrangement arranged between the first pinion set and the further pinion set, and at the further pinion set. This triple torque-transmitting connection is a preferred embodiment. It is also possible to provide more than one further pinion arrangement, for example two or more further pinion arrangements, thereby forming a quadruple or multiple torque-transmitting connection between the pinion arrangement and the transmission.

[0054] This helps to form module-dependent optimized load paths between the inner final pinion arrangement and the transmission, between the further pinion arrangement and the transmission, and between the further pinion set and the transmission. By virtue of the load paths which can thus be optimized for each of these modules and their load conditions, in particular their typical torque loads, the fatigue strength and operational safety of the pinion arrangement are increased and its mass is correspondingly reduced.

[0055] According to another preferred embodiment, the teeth of at least one even-numbered pinion of the pinion configuration, preferably multiple or all even-numbered pinions, correspond alternately to narrow tooth groups or wide tooth groups in the circumferential direction, wherein the teeth of the narrow tooth group are narrow teeth, and wherein the wide tooth group includes at least one wide tooth, preferably multiple wide teeth.

[0056] Narrow teeth refer to teeth with a width smaller than the clear width or the gap between inner plates of the inner link plate link of a bicycle chain corresponding to a pinion gear configuration, i.e., suitable for being driven by a pinion gear configuration, i.e., such narrow teeth can be completely immersed in or meshed with the gap between inner plates of the inner link plate link of the bicycle chain. Wide teeth refer to teeth with a width larger than the clear width or the gap between inner plates of the inner link plate link of a bicycle chain corresponding to a pinion gear configuration, so that although the wide teeth can mesh with the gap between outer plates of the outer link plate link of the bicycle chain, they cannot mesh with the gap between inner plates of the inner link plate link of the bicycle chain.

[0057] The design of an even number of pinions alternatingly having narrow teeth and wide teeth, which is known in the industry as a coarse and fine sprocket or a sprocket or pinion with coarse and fine teeth, greatly improves the stability of the chain running on the corresponding pinions, that is, the generally straight chain running, when no gear shifting process is performed.

[0058] The reason for this improvement in the stability of chain operation due to the alternating arrangement of wide and narrow pinion teeth is that the chain is not guided transversely on the sprocket or pinion only in the area of ​​the inner link plates, as in conventional sprockets or pinions with only narrow teeth, but is also guided transversely in the area of ​​the outer link plates due to the presence of at least one, preferably a plurality of wide teeth.

[0059] With the help of the pinion configuration according to the present disclosure, the latest coarse and fine pinion pinion technology can be combined with a standard transmission or a standard flywheel hub that has been known for decades, thereby being compatible with almost all bicycles or rear wheels having such a standard transmission or a standard flywheel hub.

[0060] The above embodiments related to the coarse and fine pinion gears can also be realized independently of the presence of the above-mentioned rotary bearing device or the spacing unit.

[0061] Another preferred embodiment of the pinion arrangement according to the disclosure is characterized in that at least one pinion of the pinion arrangement has at least one stabilizing tooth corresponding to a narrow tooth set and / or at least one stabilizing tooth corresponding to a wide tooth set in the region of at least one outer shifting channel of the pinion and / or in a region adjacent to the at least one outer shifting channel, preferably in the region of an inner shifting channel of the pinion adjacent to the outer shifting channel. The inner chain guiding surface of the at least one stabilizing tooth protrudes in the inner direction relative to the inner chain guiding surface of the widest tooth of the same tooth set, so that when the chain runs on the pinion, in particular in normal chain operation, the chain is deflected inwardly by the inner chain guiding surface of the at least one stabilizing tooth protruding inwardly.

[0062] Normal chain operation or normal chain operation is the chain operation when the chain and the pinion arrangement move in the transmission direction of the drive train of the bicycle or counter to the transmission direction and when no gear shifting process or gear change is currently taking place, i.e. the chain is not shifting from one pinion of the pinion arrangement to another adjacent pinion of the pinion arrangement.

[0063] Therefore, when the chain runs normally on the pinion, the chain is deflected inwardly due to the effect of the at least one stabilizing tooth, wherein the stabilizing tooth is preferably arranged in the region of the outer shifting channel of the pinion of the pinion arrangement. As an alternative or supplementary solution, when the chain runs normally, the deflection of the chain inwardly can also be carried out in the region of the pinion adjacent to the outer shifting channel, in particular in the region of the inner shifting channel adjacent to the outer shifting channel, wherein a stabilizing tooth is arranged in this region instead of or in addition to the aforementioned stabilizing tooth.

[0064] When the chain is running normally, the deflection of the chain towards the inside caused by the at least one stabilizing tooth can stabilize and improve the straight running of the chain, in particular in the region of the inner shifting channel on the pinion of the pinion arrangement. In other words, due to the action of the stabilizing tooth, the chain is slightly deflected towards the inside in the region of the inner shifting channel, thereby preventing the chain from shifting towards the outside in the region of the inner shifting channel (which, like the outer shifting channel, has, in particular, outer grooves in the region of the pinion teeth), which would affect the uniformity and smoothness of the shifting process, disrupt the synchronous running of the chain on the coarse and fine teeth of the pinion arrangement, and at least when shifting under load, could also lead to damage to the pinion arrangement and / or the chain.

[0065] A further advantage of the inner chain guiding surface of the stabilizing tooth which is shifted inwards is that the stabilizing tooth thus has a larger tooth width, thereby increasing the deformation resistance and wear resistance of the stabilizing tooth. This is particularly advantageous if the stabilizing tooth is preferably located in the region of the shifting channel and therefore has an outer recess or a tooth width which is reduced on the outer side, which would otherwise impair the stability of the toothing.

[0066] As an alternative or in addition, a stabilizing tooth with the same features as the inner chain guiding surface is also characterized by an increase in the chain guiding dimension across the tooth, which will be explained below, and the inner chain guiding surface is shifted inwardly relative to the inner chain guiding surface of the widest tooth of the same tooth group, so that the chain is deflected inwardly by its inner chain guiding surface protruding inwardly during normal chain movement.

[0067] In the fine teeth or narrow teeth of the coarse and fine pinion gears, the chain guiding dimension across the teeth is equivalent to the distance between the inner chain guiding surface of the first narrow tooth and the outer chain guiding surface of another narrow tooth adjacent to the first narrow tooth, that is, the distance between the outer chain guiding surface of the next narrow tooth of the coarse and fine pinion gear before or after the first narrow tooth.

[0068] The width of the chain guiding dimension across the teeth of adjacent narrow teeth and in particular the position (in the axial direction of the rear wheel axle) determines the relative axial position of the chain on the pinion gear, at least in the area of ​​these teeth, because the outer inner surface of the inner chain link plate of the chain is guided by the outer chain guiding surface of the first narrow tooth, while the inner inner surface of the adjacent inner chain link plate is guided by the inner chain guiding surface of the other narrow tooth adjacent to the first narrow tooth.

[0069] That is, if the chain guide size of the span of two narrow teeth is changed along the rear wheel axle axial direction relative to the pinion center plane, the relative position of the chain relative to the pinion center plane along the rear wheel axle axial direction will also change accordingly.

[0070] Since the stabilizing tooth is characterized in that its inner chain guiding surface moves inwardly relative to the inner chain guiding surface of the widest tooth of the same tooth group, the chain guiding dimension of the span corresponding to the stabilizing tooth, that is, the position of the chain guiding dimension of the span in the axial direction of the rear wheel axle will also change. The stabilizing tooth together with the next tooth of the chain along the circumference of the pinion gear forms the chain guiding dimension of the span.

[0071] As a result, in particular, the position of the chain guide dimension of this span in the region of the stable tooth is also shifted inwards. In addition, the chain guide dimension of the span corresponding to the stable tooth is optionally also increased relative to the chain guide dimension of the span of the remaining teeth of the tooth set of the stable tooth, which leads to a slight tilting of the chain in the region of the chain guide dimension of this span, thereby contributing to the desired inward displacement of the chain.

[0072] A person skilled in the art recognizes that the aforementioned examples of narrow stabilizing teeth, i.e. stabilizing teeth corresponding to narrow tooth groups of coarse and fine teeth, can be similarly applied to wide stabilizing teeth while maintaining the same principle. In the wide stabilizing teeth, the chain guide dimensions of the span teeth can also be similarly defined, which are shifted inwardly relative to the chain guide dimensions of the span teeth of another wide tooth in the area of ​​the wide stabilizing teeth. The chain guide dimensions of the span teeth of a wide tooth can also be constructed to be wider than the chain guide dimensions of the span teeth of other wide teeth, which also causes the chain to be slightly skewed in the area of ​​the chain guide dimensions of the span teeth of the stabilizing teeth, thereby helping the chain to achieve the desired inward displacement in the stabilizing area.

[0073] As a result, the chain running in the region of the wide stabilizing teeth is also deflected inwards, with the same effects and advantages as described above with respect to the narrow stabilizing teeth.

[0074] Those skilled in the art can also understand that the wide and narrow stabilizing teeth according to the present disclosure can be combined with each other, so that in the area of ​​the outer shift channel and / or in the area of ​​the coarse and fine teeth adjacent to the outer shift channel, especially in the area of ​​the inner shift channel adjacent to the outer shift channel, both at least one narrow stabilizing tooth and at least one wide stabilizing tooth can be provided, and these two stabilizing teeth together realize the desired inward movement of the chain, thereby preventing undesired outward shifting from occurring in the area of ​​the inner shift channel.

[0075] Those skilled in the art also recognize that the principle of using wide stabilizing teeth or narrow stabilizing teeth to allow the chain to move inwardly within the area of ​​the outer shift channel to prevent the chain from shifting inwardly undesirably within the area of ​​the outer shift channel can also be similarly applied to using wide stabilizing teeth or narrow stabilizing teeth to allow the chain to move outwardly within the area of ​​the inner shift channel to prevent the chain from shifting outwardly undesirably within the area of ​​the inner shift channel.

[0076] For this purpose, the outer chain guiding surface of the stabilizing tooth is shifted outward relative to the outer chain guiding surfaces of the other teeth of the same tooth set, so that the chain guiding dimension corresponding to the tooth span of the stabilizing tooth is also shifted outward and optionally widened. In this way, the chain run is displaced outward in the area of ​​the stabilizing tooth, so that undesired inward shifting in the area of ​​the outer shifting channel can be prevented.

[0077] Finally, it is also obvious to a person skilled in the art that the principle of a stabilizing tooth that allows normal operation of the chain to be moved outwardly or inwardly in certain specific areas of the pinion, depending on the specific position of the moved chain guide surface of the stabilizing tooth, can also be realized independently of the presence of coarse and fine teeth. In other words, a stabilizing tooth with an inner chain guide surface that moves inwardly or an outer chain guide surface that moves outwardly can also be used for a standard pinion that does not include coarse and fine technology, i.e. a pinion in which substantially all teeth are fine gear teeth, i.e. these fine gear teeth can mesh with the inner interspace of the inner link plates of the inner link plate links of a bicycle chain.

[0078] Based on the background that stabilizing teeth are used on pinions that do not include coarse and fine teeth and / or on odd-numbered pinions, another preferred embodiment of the pinion configuration (hereinafter referred to as technical variants 1 and 2) is that at least one pinion of the pinion configuration has at least one stabilizing tooth in the area of ​​at least one outer shift channel of the pinion and / or in the area adjacent to the at least one outer shift channel, preferably in the area of ​​the inner shift channel of the pinion adjacent to the outer shift channel (technical variant 1: to prevent shifting to the outside at an undesired position), alternatively, in the area of ​​at least one inner shift channel of the pinion and / or in the area adjacent to the at least one inner shift channel, preferably in the area of ​​the outer shift channel of the pinion adjacent to the inner shift channel (technical variant 2: to prevent shifting to the inside at an undesired position). In which, the inner chain guiding surface (technical variant 1) or the outer chain guiding surface (technical variant 2) of the at least one stabilizing tooth protrudes in the inner direction (technical variant 1) or the outer direction (technical variant 2) relative to the inner chain guiding surface (technical variant 1) or the outer chain guiding surface (technical variant 2) of other teeth of the pinion or the widest tooth of the pinion, so that when the chain runs on the pinion, especially in normal chain operation, it is deflected inwardly (technical variant 1) or outwardly (technical variant 2) by the inner chain guiding surface (technical variant 1) protruding on the inner side of the at least one stabilizing tooth, or by the outer chain guiding surface (technical variant 2) protruding on the outer side.

[0079] As an alternative to a protruding inner chain guiding surface (technical variant 1) or outer chain guiding surface (technical variant 2) of at least one stabilizing tooth, the stabilizing tooth is also characterized in that it forms a chain guiding dimension across the teeth together with the adjacent teeth, and the chain guiding dimension across the teeth is greater than the width of the other teeth of the pinion or greater than the widest tooth of the pinion, and / or the chain guiding dimension across the teeth is moved inwardly (technical variant 1) or outwardly (technical variant 2) relative to the chain guiding dimension across the teeth of the other teeth of the pinion or the widest pinion tooth.

[0080] For definitions and descriptions of chain guide dimensions across teeth, see the introduction to the instructions and Fig.11A Description.

[0081] The above embodiments in connection with the at least one stabilizing tooth can also be realized independently of the presence of a rotary bearing arrangement or a spacing unit of the above-mentioned pinion flywheel.

[0082] The disclosure also relates to a modular system for forming a multi-layer pinion arrangement. The modular system comprises at least modularly replaceable components "inner final pinion arrangement", "first pinion set" and "outer final pinion arrangement". At least one of the modularly replaceable components belongs to a component family comprising at least two series members, or may correspond to such a component family and may be replaced with another member of the component family while retaining the remaining components, which member is, for example, made of a different material or has a different manufacturing quality than at least one other member of the same component family.

[0083] This means that a component family is defined or definable for the at least one component, which component family comprises at least two family members, ie at least two different and interchangeable technical variants of the at least one component.

[0084] Taking the outer final pinion gear device, which may be formed by another pinion gear set, as an example, a component series may refer to a series or batch of other pinion gear sets having different structures, being formed by different materials or having different manufacturing qualities. For example, another pinion gear set assembled by laser welding of a single pinion gear and another pinion gear set made by pinning or riveting of a single pinion gear may form a component series of the outer final pinion gear device.

[0085] Taking the inner final stage pinion gear device of the pinion gear configuration according to the present disclosure as an example, for example, one carrier pinion formed of steel and one carrier pinion formed of aluminum may form a component series of the inner final stage pinion gear device.

[0086] For example, different star wheel pinions, pinion star wheels, ring pinions or carrier pinions made of different materials, for example steel, aluminum and titanium, and / or with different surface treatments can be provided within the component series of the inner final pinion arrangement. As long as the connection interface with the adjacent modular components, that is, with the first pinion set, is identical on both the pinion star wheel and the star wheel pinion, it is also possible to form a component series of, for example, a pinion star wheel and a pinion ring that can be fastened thereto, and a star wheel pinion and at least one pinion ring fastened thereto, so that the first pinion set can be selectively connected to the pinion star wheel or the star wheel pinion, for example.

[0087] While retaining the remaining components, in the example shown here, namely the first pinion set and the outer final pinion arrangement, a plurality of pinion arrangements for different applications and qualities can be provided in this way with little development and manufacturing effort.

[0088] This also applies analogously to other components of the pinion arrangement, ie, for example, to the modularly replaceable outer final pinion arrangement or the modularly replaceable first pinion set.

[0089] Therefore, based on the modular system, pinion configurations with different functions and values ​​for different target groups and target markets can be provided in a simple manner, specifically by selecting materials of different density and strength, or different manufacturing methods or surface qualities for different modular components of the modular system.

[0090] The modular system overall forms a plurality of variants of the pinion arrangement according to the disclosure, which can be adapted or optimized for different price ranges or market segments and associated purposes of use, for example for occasional leisure time use in one market segment and for extreme use in sports in another different market segment. This can be achieved without departing from the modular basic structure of the pinion arrangement and without having to redevelop the entire pinion arrangement and manufacture all individual components separately. BRIEF DESCRIPTION OF THE DRAWINGS

[0091] The following is an exemplary description of the implementation of the present utility model in conjunction with the accompanying drawings.

[0092] in:

[0093] Figure 1 : shows a bicycle with a chain drive train and a pinion gear configuration;

[0094] Figure 2 : shows a partially cut-away isometric exploded view of a pinion arrangement and a corresponding transmission, the pinion arrangement having a first pinion set rotatably supported on the outside on a bearing arrangement;

[0095] Figure 3 : Shows Figure 2 An axial longitudinal section through the pinion arrangement and the transmission is shown, wherein the bearing arrangement is designed as a spacer unit;

[0096] Figure 4 : Shows Figure 2 and Figure 3 an enlarged axial longitudinal section through the components of the transmission and pinion arrangement shown, in which the bearing arrangement designed as an axial tensioning element is depicted;

[0097] Figure 5 : Shows Figures 2 to 4 An axial longitudinal section of the transmission and pinion arrangement shown;

[0098] Figure 6 : Shows Figures 2 to 5 A partially cutaway longitudinal section of the transmission and pinion arrangement shown with another pinion set removed;

[0099] Figure 7 : Shows Figure 6 An isometric perspective view of the transmission and another pinion set shown to illustrate the diameter ratios;

[0100] Figure 8 : Shows Figure 6 and Figure 7 The transmission and another pinion set are shown to illustrate the axial position of certain pinions relative to the transmission;

[0101] Fig. 9 : shows a partially cut-away isometric exploded view of a transmission and pinion arrangement and a corresponding transmission, for illustrating the torque transfer between the pinion arrangement and the transmission;

[0102] Fig.10 : Shows Figures 2 to 9 a partially cut-away perspective view of a portion of an outer pinion of the illustrated pinion arrangement;

[0103] Fig.11A : Shows Figure 2 to Figure 1 1 is a partial plan view of a pinion of the pinion arrangement and a bicycle chain running thereon;

[0104] Fig. 11B : Shows Figure 1 a schematic diagram of a bicycle chain of the drive train shown;

[0105] Fig. 12A : Shows Fig.11A An oblique back view of the pinion shown;

[0106] Fig. 12B : Shows Fig.11A and Fig. 12A a front side view of the pinion shown;

[0107] Fig.13 : Shows the Figures 2 to 10 or an overview diagram of a modular system of multi-layer pinion configurations as shown in FIG14 ;

[0108] Fig.14A : shows another embodiment of a pinion arrangement with a first pinion gear set rotatably supported on the outside on a bearing device, and a corresponding transmission;

[0109] Fig. 14B : Shows Fig.14A Alternative embodiments of bearing arrangements for the pinion arrangement shown;

[0110] Fig.15A -C: shows Figure 2 to Figure 1 4 is an alternative embodiment of the first pinion gear set of the pinion gear arrangement shown in FIG.

[0111] Fig.16 : Another embodiment of the transmission and pinion arrangement is similar to Fig. 9 A partially cutaway isometric exploded view of

[0112] Fig.17A : Fig.16 An axial longitudinal section of the pinion arrangement shown;

[0113] Fig. 17B : Fig.16 and Fig.17A Multifunctional spacer element for the pinion configuration shown;

[0114] Fig. 17C : A highly perspective sectional view of the arrangement formed by the multifunctional spacing element, the intermediate pinion, the outer final pinion of the first pinion set and the bearing arrangement;

[0115] Fig.18A -C: Figures 2 to 17C Schematic cross-sectional views and detailed views of the pinion teeth of the illustrated pinion configuration;

[0116] Fig.19A : Similar to Figures 2 to 17C A pinion of another embodiment of a pinion gear configuration;

[0117] Fig.19B : Fig.19A A schematic cross-sectional view of a tooth top of a tooth of the pinion shown;

[0118] Fig. 20A +B: Fig.19A +B shows the pinion tooth top shape and Fig.18A or Fig.10 Schematic comparison diagram of the tooth top shape of the pinion teeth shown;

[0119] Fig.21A +B: Fig.19A +B shows the pinion tooth top shape and Fig.18A or Fig.10 or Fig.18B Schematic comparison of the tooth addendum shapes of the pinion teeth shown. DETAILED DESCRIPTION

[0120] Figure 1 A bicycle 1 is shown with a transmission system Td, wherein the transmission system Td includes a crank arrangement Dc with a sprocket Cr rotatably supported on a bottom bracket device Ab, a pinion arrangement Ap rotatably supported on a rear wheel axle Ar with a rear wheel Wr, a transmission chain Cn, and a rear derailleur Rd for shifting gears. The arrow Rdd represents the transmission rotation direction of the rear wheel Wr or the pinion arrangement Ap under the transmission load applied by the bicycle chain Cn.

[0121] Figure 2 A pinion arrangement Ap according to the present disclosure is shown, as well as a transmission Dd. The transmission Dd is usually suitable for being mounted on the rear wheel hub of the bicycle 1 together with a unidirectional freewheel device (not shown) in such a way as to transmit torque in the transmission direction. The transmission Dd comprises in particular a conventional toothing transmission profile Pd arranged at the periphery. The transmission Dd may in particular be a standard transmission Dd, such as the standard transmission of the so-called standard freewheel hub that has been widely used in the bicycle market for decades.

[0122] The pinion arrangement Ap comprises at least one meshing profile Pe which corresponds in shape to the transmission profile Pd of the transmission Dd, so that the pinion arrangement Ap meshes with the transmission Dd in a torque-transmitting manner.

[0123] The modular structure of the pinion arrangement Ap can be seen, which comprises an inner final pinion arrangement Pti, a cantilevered first pinion gear set Sc1 and an outer final pinion arrangement Pto. The inner final pinion arrangement Pti and the first pinion gear set Sc1 together define a flywheel module Mc1.

[0124] The pinion set Sc1 can be connected to the inner final pinion set Pti in the connection region Ca of the inner final pinion set Pti, for example by means of a pin or a rivet Cp. Alternatively, the connection between the inner final pinion set Pti and the pinion set Sc1 can also be implemented in the connection region Ca by screwing and / or gluing.

[0125] Also visible are the screw plug device Sd, which is used to mount and fasten the pinion arrangement Ap on the transmission device Dd, and the bearing device Db, on which the first pinion set Sc1 is rotatably supported on its outer side relative to the transmission device Dd in a substantially cylindrical supporting area Sb of the bearing device Db.

[0126] In this embodiment, the outer side of the first pinion gear set Sc1 that is suitable for being rotatably supported on the bearing device Db is the outer final pinion gear Z7. In order to rotatably support the first pinion gear set Sc1 on the outside, the outer pinion gear Z7 of the first pinion gear set Sc1 has an inner peripheral area Ic (see FIG. 1 ) on its inner circumference that corresponds to the shape of the support area Sb of the bearing device Db, which is also a cylindrical surface (see FIG. 1 ). Fig.10 , Fig.13 and Fig.15A ).

[0127] The advantages resulting from the rotatable outer support of the first pinion set Sc1 on the bearing device Db, in particular with regard to noise reduction and increased fatigue strength, have been described in detail in the introduction to the specification above.

[0128] Figure 3The pinion configuration Ap is shown mounted on the transmission. For clarity, Figure 3 The screw plug device Sd is omitted.

[0129] The inner final pinion gear arrangement Pti, the self-supporting first pinion gear set Sc1 and the outer final pinion gear arrangement Pto can be seen. In the embodiment shown, the inner final pinion gear arrangement Pti comprises a pinion star wheel Sp, on which two pinion rings Rp1 and Rp2 are arranged and connected to the pinion star wheel Sp by means of rivets Jr.

[0130] exist Figure 3 In the figure, the first pinion Sc1 is only shown in dashed lines to illustrate the bearing device Db. The bearing area Sb of the bearing device Db, which is in the form of a cylindrical surface here, can also be seen, which is used to rotatably support the first pinion Sc1 on the outside, with the advantages already described above.

[0131] The bearing device Db here simultaneously forms a spacing unit which is suitable for determining a relative distance Da1 between at least two pinion arrangements of the pinion arrangement in the axial direction Da of the rear wheel shaft when the pinion arrangement Ap is mounted on the transmission device Dd.

[0132] In the embodiment shown, the bearing device Db is suitable for determining the relative distance Da1 between the pinion star wheel Sp and the outer final pinion device Pto. This means that the bearing device Db performs a dual function here, in that it is used, on the one hand, as described above, to rotatably support the first pinion set Sc1 on the outside, and on the other hand, to set and maintain the relative distance Da1 between the pinion star wheel Sp and the outer final pinion device Pto. Precise maintenance of the axial relative distance, such as the relative distance Da1, is particularly important with the aid of Figure 1 This is very important for the long-term reliability and precision of the rear derailleur Rd when shifting gears.

[0133] Figure 4 The transmission Dd and the Figure 2 and Figure 3 Components of the pinion configuration Ap shown.

[0134] It can be seen that the bearing device Db has the two functions mentioned above, namely, rotatably supporting the first pinion gear set Sc1 (see FIG. Figure 2 ) and the function of setting and maintaining the relative distance Da1 between the pinion star wheel Sp and the outer final pinion device Pto, it also performs the function of an axial tensioning element for mounting the pinion arrangement Ap on the transmission device Dd.

[0135] In this embodiment, the bearing device Db is used in particular to transmit a mounting tension force between the inner final pinion device Pti and the outer final pinion device Pto in the axial direction Da of the rear wheel shaft, wherein the mounting tension force is part of a closed clamping force flow Ff extending through the transmission device Dd and the pinion device Ap substantially parallel to the rear wheel shaft in the state where the pinion arrangement Ap is mounted on the transmission device Dd.

[0136] The tightening force flow Ff is generated by the screw plug device Sd (see Figure 2 ), specifically, a screw plug device Sd having an external thread Te for this purpose is screwed into the internal thread Ti of the transmission device Dd. As a result, the outer final pinion device Pto is pushed or pressed onto the transmission device Dd via a surrounding flange of the screw plug device Sd, for example, in the form of a retaining ring Rs, and correspondingly onto the bearing device Db, which, as described above, simultaneously forms a spacing unit. The bearing device Db in turn presses against a corresponding axial stop on the inner final pinion device Pti, Figure 4 That is, it is pressed against the pinion star wheel Sp, which in turn presses against the corresponding axial stop Fa of the transmission device Dd, see Figure 7 and Figure 8 .

[0137] As a result, a closed force flow Ff is generated overall, extending approximately parallel to the rear wheel axle through the pinion arrangement Ap and the transmission device Dd, which force flow presses the pinion arrangement Ap axially together on the one hand and ensures that the pinion arrangement Ap is fastened to the transmission device Dd on the other hand.

[0138] Figure 5 Other multifunctional features of the transmission Dd are shown.

[0139] It can be seen that the transmission device Dd is not only suitable for determining and maintaining the relative distance Da1 between the inner final pinion device, here the pinion star wheel Sp and the outer final pinion device Pto, but also for determining and maintaining the relative distance Da2 between the inner final pinion device (here the pinion star wheel Sp) and the outer final pinion Z7 of the first pinion group Sc1.

[0140] This means that the transmission Dd also has the task of determining and maintaining the width Da2 of the first pinion set Sc1. For this purpose, the first pinion set Sc1 is preferably manufactured with a width slightly exceeding the width Da2. Thus, when the pinion arrangement Ap is mounted on the transmission Dd, based on the force flow Ff (see Figure 4 ) The first pinion set Sc1 is elastically pressed together at least slightly in the axial direction Da of the rear wheel shaft, so that it is fixed without clearance in the axial direction Da in the pinion arrangement Ap and on the transmission device Dd.

[0141] also, Figure 5 The bearing arrangement Db shown is also suitable for determining and maintaining a relative distance Da3 between the outer side of the first pinion set Sc1 and the inner side of the outer final pinion arrangement, which is formed here by the second pinion set Sc2 (cf. Figures 2 to 4 ). The relative distance Da3 is ensured by the action and width of the flange-shaped stop St, which in this embodiment is integrally formed on the bearing device Db.

[0142] In other words, in the illustrated embodiment, the bearing device Db is suitable for determining all relative distances Da1, Da2, Da3 on the axial direction Da of the rear wheel shaft in an advantageous multifunctional scheme, and is also suitable for transmitting all tensioning forces along the axial direction Da of the rear wheel shaft between the inner final pinion device Pti, the outer final pinion device Pto, the outer final pinion Z7 of the first pinion set Sc1 and the transmission device Dd.

[0143] However, unlike the prior art described at the beginning of this article, the outer final pinion Z7 of the first pinion set Sc1 is not tensioned on Figure 4 In the axial force flow Ff shown, which in the prior art could lead to the disadvantages described at the outset, in particular with regard to noise generation and fatigue strength of the pinion arrangement, an elastic rotation relative to the transmission Dd can instead be maintained with virtually no force.

[0144] Figure 6 Shows Figures 2 to 5 The semi-disassembled state of the pinion arrangement is shown, in which in particular the outer final pinion arrangement Pto is removed from the transmission Dd. It can be seen that the outer final pinion arrangement Pto is constructed as a further pinion set Sc2 here.

[0145] The further pinion gear set Sc2 can be constructed as a substantially integrally formed module, for example, milled from a whole block. Alternatively, the further pinion gear set Sc2 can be composed of a plurality of pinion gears or pinions Z8-Z12, wherein the plurality of pinion gears or pinions are preferably welded together, for example, by laser. The following embodiment of the further pinion gear set Sc2 can also be adopted: the pinion gears or pinions Z8-Z12 of the further pinion gear set Sc2 are connected by riveting or pinioning.

[0146] from Figure 6 The meshing profile Pe arranged on the inner circumference of the further pinion set Sc2 can also be seen. The meshing profile Pe corresponds in shape to the transmission profile Pd of the transmission device Dd and is arranged in the axial region of at least one pinion of the further pinion set Sc2, here in the axial region of the pinion Z10 of the further pinion set Sc2. In the axial region of the pinion Z10, there is sufficient radial structural space on the inner circumference of the pinion Z10 to arrange the meshing profile Pe there.

[0147] In this regard, the advantage of constructing the further pinion set Sc2 as a substantially integral module is that the further pinion set Sc2 can have pinions whose inner diameter, in particular the root circle diameter Dr, is smaller or much smaller than the outer diameter Do of the transmission Dd. This makes it possible to realize a pinion arrangement Ap with particularly small outer pinions, here for example with the pinions Z11 and Z12, in particular with pinions having a number of teeth equal to or less than 10.

[0148] This results in a pinion arrangement Ap with a particularly wide transmission ratio range, which is particularly suitable for the 1× drive train on the bicycle mentioned at the beginning, in which only one sprocket Cr is present in the region of the bottom bracket device Ab, cf. Figure 1 .

[0149] Figure 7 The arrangement of particularly small pinions with a number of teeth equal to or less than 10 on a standard transmission Dd is shown again. It can be seen that the 10-tooth pinion Z12 in particular has a root diameter Dr which is significantly smaller than the outer diameter Do of the transmission Dd in the region of the transmission profile Pd of the transmission Dd. However, due to the substantially one-piece design of the further pinion set Sc2, the transmission torque can still be transmitted from the smallest pinion, in particular the 10-tooth pinion Z12, in the axial direction Da to the inside through the pinion Z11 and from there to the pinion Z10. Finally, the transmission torque of the pinion Z12 can be transmitted from the pinion Z10 to the transmission profile Pd of the transmission Dd by means of the meshing profile Pe.

[0150] The aforementioned technical solution, i.e., the other pinion set Sc2 is constructed as a substantially integrally formed module and has an engagement profile Pe arranged in the region of at least one of the larger pinions Z10 of the other pinion set Sc2 for engaging with the transmission profile Pd of the transmission device Dd, also enables or results in the following Figure 8 As shown, a pinion center plane Pc11, Pc12 of at least one of the smallest pinions Z11, Z12 is positioned at a distance from the outer end surface Fe of the transmission device Dd on the outside.

[0151] In addition to the use of particularly small pinions, this also allows for efficient use of the structural space between the transmission Dd of the bicycle 1 and the frame dropout end (not shown but known to a person skilled in the art) on the outside next to the outer end face Fe of the transmission Dd. This makes it possible to realize a pinion arrangement Ap with a larger number of pinions or gears, or to position the pinion arrangement Ap further outwards on the rear wheel Wr in the outer direction.

[0152] The structural space thus freed up inside the pinion arrangement Ap can be used, for example, to increase the spacing of the spoke flanges of the rear wheel hub of the bicycle 1 , thereby increasing the stability of the rear wheel Wr.

[0153] also, Figure 8 The structural details of the screw plug device Sd and its external thread Te are shown again, which is suitable for standard transmission devices, such as Figures 2 to 9 The internal thread Ti of the transmission device Dd shown is engaged.

[0154] In particular, it can be seen that in order to accommodate a particularly small pinion, that is, in particular to accommodate the smallest pinion Z12 having 10 teeth, the screw plug device Sd has a rod diameter Ds which is significantly smaller than the root circle diameter Dr of the pinion Z12 and smaller than the thread diameter Dt of the internal thread Ti of the standard transmission device Dd.

[0155] Based on this technical solution of the screw plug device Sd and on the embodiment of the screw plug device Sd with the above-mentioned smaller rod diameter and with the retaining ring Rs arranged in the annular groove in the outer area on the rod of the screw plug device Sd, the screw plug device Sd can be removed from the inside (with the retaining ring Rs removed). Figure 8 That is, insert the pinion set Sc2 from the left side.

[0156] Subsequently, the retaining ring Rs is arranged in the annular groove of the screw plug device Sd, so that when the screw plug device Sd is later screwed into the internal thread Ti of the transmission device Dd, a substantially axial force flow Ff is formed through the pinion arrangement Ap and the transmission device Dd, as described above in conjunction with Figure 4 As described, this force flow fixes the pinion arrangement Ap on the transmission Dd. This allows very small pinions with a number of teeth equal to or less than 10 to be used with a standard transmission Dd with a minimum number of parts and minimum design difficulty.

[0157] Figure 8 Also schematically shown is a method of assembling the further pinion set Sc2 as a substantially integral module formed of individual pinions Z9-Z12. Preferably, this is carried out by laser welding, wherein Figure 8 The direction of the welding laser beam is shown by the block arrow Bl in an exemplary manner. In other words, this means that the laser welding of the individual pinions Z9-Z12 to form the pinion set Sc2 in the embodiment shown is carried out obliquely from the inside, so that a fillet weld Wf is formed in the area indicated by dots. In this way, the individual pinions Z9-Z12 can be fixedly connected to each other to form an integral pinion set Sc2, wherein an optimal weld can be formed due to the geometry of the fillet weld Wf, which can be easily approached from the radial inside.

[0158] Fig. 9Another embodiment of a pinion arrangement Ap is shown. Here again, the above-mentioned rotatable support Sb for the first pinion set Sc1 on the outside can be seen first. Figure 2 The pinion arrangement shown generally consists of the modules "inner final pinion device Pti" (e.g. pinion star wheel Sp and ring pinions Z1, Z2 fastened thereto), "first pinion set Sc1", "outer final pinion device Pto" (e.g. another pinion set Sc2), Fig. 9 The pinion arrangement Ap shown has an additional pinion arrangement Pi, which is designed here as a single pinion Z8. It can be seen that the single pinion Z8 can be accommodated in a clamped manner in the axial direction Da between a flange-shaped stop St of the bearing arrangement Db and an annular stop Sr in the area of ​​the outer pinion set Sc2.

[0159] The annular stop Sr may be, for example, a stop surface which is arranged directly or integrally on the outer pinion set Sc2 , or a stop surface Sr on a separate annular spacer element Ae which is preferably formed of plastic.

[0160] The advantage of arranging the single pinion Z8 between the first pinion set Sc1 and the second or outer pinion set Sc2 is in particular that the single pinion Z8 can be replaced simply and cost-effectively in the event of wear. This is also important for the single pinion Z8 with 18 teeth in the pinion arrangement shown, because according to statistical research by the applicant, this pinion is the most commonly used pinion and is therefore particularly prone to wear.

[0161] This applies in particular to electric bicycles or pedelecs in which the drive train Td and in particular the pinions of the pinion arrangement Ap are loaded more than a bicycle without an electric auxiliary drive.

[0162] exist Fig. 9 In the embodiment shown, the arrangement of the single pinion Z8 between the first pinion set Sc1 and the second or outer pinion set Sc2 also makes the pinion arrangement Ap suitable for transmitting the transmission torque to the transmission in three axial areas Pa1, Pa2, Pa3 spaced apart from each other in the axial direction Da. The positions Pa1, Pa2, Pa3 refer to the axial area Pa1 of the meshing profile Pe arranged on the pinion star wheel Sp, then to the axial area Pa2 of the meshing profile Pe arranged on the outer pinion set Sc2, and finally to the axial area Pa3 on the inner circumference of the single pinion Z8, which for this purpose also has a meshing profile Pe for meshing with the transmission Dd in a torque-transmitting manner.

[0163] Fig.10 Shows Figures 2 to 9A partially cutaway perspective view of a portion of the outer pinions Z6 to Z12 of the pinion arrangement Ap shown. The number of teeth of the pinions of this exemplary embodiment is given in brackets after the reference numerals Z6 to Z12. The pinions Z6 to Z12 are not shown in their actual rotational relative position relative to one another, but are twisted relative to one another for the sake of illustration, so that in particular the design of the coarse and fine teeth can be seen.

[0164] The even-numbered pinions Z6 and Z8 to Z12 refer to the coarse and fine pinions described above, and therefore, their teeth correspond alternately to narrow tooth groups or wide tooth groups having different tooth widths, respectively. The teeth of the narrow tooth group are narrow teeth whose width is smaller than the inner link plate gap Wci of the inner link plate link Li of the bicycle chain Cn corresponding to the pinion configuration, and the wide tooth group includes at least one wide tooth whose width is larger than the inner link plate gap Wci of the inner link plate link but smaller than the outer link plate gap Wco of the outer link plate link Lo (see Fig. 11B Bicycle chain Cn).

[0165] The coarse and fine pinion gears ensure stable chain running on the pinion gear occupied by the chain Cn when no shifting process is performed, and mainly prevent the chain from being lifted off the pinion gear unintentionally, for example, in the case of strong vibrations or chain shocks. In addition, the coarse and fine pinion gears also ensure synchronization between the chain Cn and the pinion gear occupied by the chain Cn, so that the inner chain plate link Li is engaged exclusively with the corresponding narrow teeth of the pinion gear, and the outer chain plate link Lo is engaged exclusively with the corresponding wide teeth of the pinion gear. In this way, it is possible to achieve a design of wide teeth and narrow teeth of the pinion gear that is optimized specifically for meshing with the outer chain plate link Lo or the inner chain plate link Li.

[0166] exist Fig.10 In the diagram, the wide pinion teeth Tw visible in the foreground, i.e. the pinion teeth adapted to mesh with the outer plate link Lo, are provided with small circle markings for easy identification. Similarly, the narrow pinion teeth Tn visible in the foreground, i.e. the pinion teeth adapted to mesh with the inner plate link Li, are provided with small square markings for easy identification.

[0167] It should be noted that not every tooth Tw of the wide pinion tooth Tw group belonging to the coarse and fine pinion of the multi-layer pinion flywheel actually has a substantially equivalent Fig. 11B The width of the clear width Wco of the outer link plate link Lo of the corresponding chain Cn is shown. The reason for this is that the coarse and fine pinions of the multi-layer pinion flywheel usually have shift grooves Ri, Ro on one or both end faces in the shift channels Ci, Co area. In the shift channels Ci, Co or shift grooves Ri, Ro area, the width of the pinion teeth there, especially the width of the teeth Tw in the two pinion tooth groups Tw, is usually reduced (see Fig.11A and Figure 12 and corresponding description).

[0168] exist Fig.10 In the pinion Z7 with an odd number of teeth and 21 teeth, there are also teeth of different widths. However, the width of all teeth of the pinion Z7 is no greater than Fig. 11B The clear width of the inner link plate link Li or the inner link plate gap Wci is shown. The reason for this is that in principle, the above-mentioned synchronization with the chain Cn cannot be achieved in an odd-numbered pinion, such as the pinion Z7, because when the pinion rotates each time, all the pinion teeth of the odd-numbered pinion mesh alternately with the inner link plate link Li and the outer link plate link Lo.

[0169] Fig.10 The pinions Z6 to Z12 shown are pinions manufactured by stamping and pressing. It can be seen that the different widths of the teeth, especially the different widths of the wide teeth Tw and the narrow teeth Tn in the even-numbered pinions, are caused by the embossing Di usually on the outer end face of the pinion. When the pinion is stamped and pressed, the embossing causes material displacement and produces a corresponding protrusion Dp on the opposite, usually inner end face of the corresponding pinion.

[0170] This is reversed only in the case of the smallest pinion Z12, since the impression Di printed there is arranged on the inner end face of the pinion Z12 and the corresponding projection Dp is arranged on the outer end face of the pinion Z12.

[0171] The embossing Di and the protrusion Dp may be arranged substantially centrally on the pinion teeth with respect to the circumference of the corresponding pinion, e.g. Fig.10 This is the case with the pinions Z6, Z7 and Z8 shown. Alternatively, the embossing Di and the projection Dp can also be arranged on the pinion tooth flank relative to the circumferential direction of the corresponding pinion, for example, this is the case with the pinions Z9 to Z12. The embossing Di and the projection Dp are arranged on the pinion tooth flank. Fig.10 In the example case, i.e. the scheme of being arranged on the corresponding non-load tooth surface Fn of the corresponding pinion tooth has advantages in terms of manufacturing the embossing Di and the protrusion Dp by stamping and embossing process, and in terms of the load capacity and wear resistance of the load tooth surface Fl of the pinion teeth, which are less weakened due to the arrangement of the embossing Di and the protrusion Dp on the non-load tooth surface Fn.

[0172] Fig.11A A highly schematic diagram shows a portion of a planar development of the circumference of an even-thickness pinion Z3 of the pinion configuration Ap of the present disclosure, including a bicycle chain Cn running on the pinion Z3. Fig.11A It is represented by a double dashed line, and its direction is roughly equivalent to Fig. 11B The direction of the inner surface of the outer link plate link Lo is shown.

[0173] exist Fig.11AIn the figure, the base body Bm of the pinion Z3, which has a thickness Dm, can first be seen in the background as a bright spot. The thickness Dm of the base body Bm of the pinion corresponds here also to the fact that the pinion has no shifting channel, that is, neither an inner shifting channel Ci nor an outer shifting channel Co (see Figure 2 , Fig. 9 and the tooth width Ww of the “normal” wide tooth Tw0 in the area of ​​the inner shift channel Ci and the outer shift channel Co in the examples of Figures 12 to 14). Fig.11A The pinion Z3 shown can be a milled pinion in particular, wherein the thickness Dm of the base material generally corresponds to the width Ww of the wide teeth. In the case of a pinion produced by a stamping process, the thickness of the base material generally corresponds to the width of the narrow teeth, see for example Fig.10 and the corresponding description. But Fig.11A and Fig. 11B The geometric design is fundamental and can therefore be applied to both milled and stamped / coined pinions.

[0174] Fig.11A The areas of the pinion Z3 shown without shift channels Ci, Co are in the left and right areas of the pinion development of the pinion Z3, with "normal" wide teeth Tw0 and normal narrow teeth Tn0 visible in these areas.

[0175] The "normal" wide teeth Tw0 have the characteristic that these wide teeth Tw can be Fig. 11B The tooth width of the outer link plates Lo of the bicycle chain Cn shown is meshed, wherein the outer link plates Lo have a clear width or an outer link plate gap Wco.

[0176] The “normal” narrow teeth Tn0 have a tooth width that enables these narrow teeth Tn to mesh with the inner link plate links Li of the bicycle chain Cn. Fig. 11B The inner link plate links Li are shown to have a clear width or inner link plate gap Wci.

[0177] exist Fig.11A In the middle area of ​​the pinion development shown, the pinion Z3 has two (originally known per se) shift channel areas, i.e., two shift channel areas for shifting the chain Cn from Fig.11A The inner shift channel area Ci of the pinion Z3 is used to shift the smaller pinion gear adjacent in the outer direction (not shown), and the outer shift channel area Co of the pinion Z3 is used to shift the chain Cn from the pinion Z3 to the smaller pinion gear adjacent in the outer direction (not shown) during the shifting process.

[0178] During the outer shifting process, it is important that the chain Cn actually passes only in the outer shift channel area Co through the special pinion shifting components there, such as the inner groove Ri and the outer groove Ro as well as the bevel and support edge of the teeth (see Figure 2 , Fig. 9 12 to 14) to the next smaller adjacent pinion. If the above process is not successful and the chain is shifted to the next smaller adjacent pinion in the area outside the outer shift channel Co, it may cause chain running problems, noise, chain jumping, and shifting under load may also cause damage to the chain and / or pinion.

[0179] In the case of coarse and fine pinions, such as the pinion Z3 shown in FIG11A, the switching of the chain Cn to the adjacent pinion is more important only in the outer shift channel area Co, Ci than in the case of pinions without alternating coarse and fine teeth Tw and Tn, because switching the chain Cn outside the shift channel area Co, Ci may also lead to asynchronous operation of the chain on the corresponding pinion. In this case, the inner plate link Li abuts against the wide pinion tooth Tw, wherein the wide pinion tooth Tw cannot enter the inner plate link Li with the clear width Wci due to its width Dm. In this case, the chain Cn may slip on the coarse and fine pinion Z3, and corresponding unfavorable or harmful or even dangerous consequences may occur in the operation of the bicycle.

[0180] In view of this, Fig.11A The pinion Z3 shown has stabilizing teeth Ts1, Ts2, Ts3, which are arranged in the outer shift channel area Co or in the inner shift channel area Ci adjacent to the outer shift channel area Co of the pinion Z3. Stabilizing teeth Ts1 and Ts3 belong to the tooth group of the narrow teeth Tn of the coarse and fine pinion, that is, they belong to the narrow teeth Tn, while stabilizing teeth Ts2 belongs to the wide tooth group of the coarse and fine pinion, that is, they belong to the wide teeth Tw. Fig.11A In the figure, the teeth Tw of the wide tooth group are also marked with small circles, and the teeth Tn of the narrow tooth group are also marked with small squares.

[0181] In each of the two stabilizing teeth Ts1 and Ts3 belonging to the narrow tooth set Tn, an inner chain guiding surface Gi1n and Gi3n projects in the inner direction relative to the inner chain guiding surface Gi0n of the remaining “normal” narrow tooth Tn0 of the narrow tooth set.

[0182] Thus, in the illustrated embodiment, in the narrow stabilizing tooth Ts1 or Ts3, a chain guiding dimension Dcn1 or Dcn3 across the teeth is formed together with the nearest adjacent narrow tooth Tn1 or Tn3, respectively, as shown in FIG. Fig.11A As shown, it is enlarged and moved inwardly relative to the "normal" chain guiding dimension Dcn0 across the teeth without the shifting channels Ci, Co in the area of ​​the adjacent narrow tooth Tn0.

[0183] Similarly, in the illustrated embodiment, in the wide stabilizing tooth Ts2, here also together with the tooth Tn3, a chain guiding dimension Dcw1 across the teeth is formed which is enlarged and shifted inwards relative to a "normal" chain guiding dimension Dcw0 across the teeth without shifting channels Ci, Co in the area of ​​the wide tooth Tw0.

[0184] Generally speaking, the chain guide dimension across the teeth (for example, the chain guide dimension across the teeth Dcn1) is, for example, the chain guide dimension or effective chain guide width formed by the combined action of the inner chain guide surface of the pinion tooth (for example, the inner chain guide surface Gi1n of the pinion tooth Ts1) and the outer chain guide surface (for example, the outer chain guide surface Go1n of the pinion tooth Tn1) that is in close contact with the inner surface of the chain Cn in the circumferential direction of the pinion Z3.

[0185] Another example of a chain guiding dimension across teeth is the effective chain guiding width or chain guiding dimension Dcw1 formed by the interaction of the inner chain guiding surface Gi2w of the pinion tooth Ts2 and the outer chain guiding surface Go3n of the pinion tooth Tn3 in close contact with the chain Cn in the circumferential direction of the pinion Z3.

[0186] Therefore, this cross-tooth chain guiding dimension Dcw1 is generated in the following manner: the inner surface of the outer chain plate link Lo of the chain abuts against the inner chain guiding surface Gi2w of the pinion tooth Ts2, and in the circumferential direction of the pinion Z3, the inner surface of the inner chain plate link Li abuts against the outer chain guiding surface Go3n of the pinion tooth Tn3.

[0187] Therefore, through this inner side (on Gi2w) and adjacent outer side abutment (on Go3n) of the chain Cn, and the chain guiding dimension Dcw1 across the teeth thereby formed in this area, the position of the chain Cn on the pinion Z3 is fixed in the area of ​​the pinion teeth Ts2 to Tn3 in the axial direction Da of the rear wheel axle.

[0188] That is, the chain guiding dimensions Dcn, Dcw across the teeth determine the position of the chain Cn on the pinion Z3 in the observed circumferential section of the pinion Z3 along the rear wheel axle axial direction Da.

[0189] For further information on the chain guide dimensions across the teeth and their influence on the chain operation, refer to the above explanations in the introduction to the description.

[0190] exist Fig.11A In the pinion shown, the "normal" cross-tooth chain guiding dimension Dcn0 in which there are no shift channels Ci and Co in the region of the narrow teeth Tn is approximately equivalent to the width of the narrow teeth Tn (viewed in the axial direction Da of the rear axle).

[0191] What has been said above for the two stabilizing teeth Ts1 and Ts3 of the narrow teeth Tn group applies analogously to the stabilizing tooth Ts2 belonging to the wide teeth Tw group. Fig.11A It can also be seen that in the wide stabilizing tooth Ts2 there is also an inner chain guiding surface Gi2w which projects in the inner direction relative to the inner chain guiding surface Gi0w of the other “normal” wide tooth Tw0 of the wide tooth set.

[0192] The chain guiding dimensions Dcn1, Dcw1 and Dcn3 of the cross teeth thus enlarged and moved inwardly, or the inner chain guiding surfaces Gi1n, Gi2w and Gi3n of the stabilizing teeth Ts1, Ts2 and Ts3 moved inwardly, cause the chain Cn to be slightly displaced inwardly at Cd along the axial direction Da of the rear wheel axle in the area of ​​the stabilizing teeth Ts1, Ts2 or Ts3. Fig.11A The direction of the chain Cn is indicated by a double dashed line.

[0193] When the chain is running normally, the deflection Cd of the chain Cn towards the inside caused by one or more of the stabilizing teeth Ts1, Ts2 and Ts3 in the above-described manner stabilizes the running of the chain Cn on the pinion Z3 of the pinion arrangement Ap, for example, in particular in the region of the inner shifting channel Ci, cf. Figure 2 , Fig. 9 Figure 12 Fig.13 and Fig.14A The shift channel Ci in.

[0194] In other words, the chain Cn is slightly deflected Cd inwards, in particular in the region of the inner shift channel Ci, by one or more of the stabilizing teeth Ts1, Ts2 and Ts3. As a result, the chain Cn is prevented from shifting unintentionally in the region of the inner shift channel Ci, which like the outer shift channel Co has in particular outer recesses Ro on the pinion teeth. Such shift errors can affect the uniformity and smoothness of the shifting process, disrupt the synchronous running of the chain Cn on the coarse and fine teeth Tw, Tn of the pinion arrangement Ap and, at least when shifting under load, can also lead to damage to the pinion arrangement Ap and / or the chain Cn.

[0195] The deflection Cd of the stabilizing teeth Ts1, Ts2, Ts3 and the chain Cn does not affect the normal outer shifting in the area of ​​the outer shift channel Co, because before the chain reaches the stabilizing teeth Ts1, Ts2, Ts3, Figure 1 The rear derailleur Rd is shown to have started to perform an outward shift in the area of ​​the outward shift path Co. In other words, when shifting outward, the chain has adopted an inclined chain path through the areas Ri2 and Ro2 of the outward shift path Co (see FIG. Fig. 12B ), so it is no longer caught on the inside by the stabilizing teeth Ts1, Ts2, Ts3, and thus will not deflect inwardly.

[0196] Another advantage of the inner chain guiding surface Gi1n, Gi2w and Gi3n of the at least one stabilizing tooth Ts1, Ts2, Ts3 that is shifted inwards is that the corresponding stabilizing tooth Ts1, Ts2, Ts3 thereby obtains a larger tooth width, thereby enhancing the wear resistance of the stabilizing tooth Ts1, Ts2, Ts3. This is particularly advantageous when the at least one stabilizing tooth Ts1, Ts2, Ts3 is preferably located in the area of ​​the shifting channel Ci, Co and therefore has an outer groove at Ro or a tooth width that is reduced on the outside.

[0197] It needs to be pointed out again that Fig.11A The figures are highly schematic and in particular not drawn to scale and do not correspond to the actual scale on the pinion Z3. Fig. 11B The chain Cn in FIG. 1 is also merely schematic, wherein for the sake of convenience of explanation, in particular, the width of the chain Cn is increased relative to the width of an actual bicycle chain.

[0198] Fig. 12A and Fig. 12B Shows the Fig.11A Two different views of the pinion Z3 showing the stabilizing teeth Ts1 , Ts2 and Ts3 . Fig. 12A The pinion Z3 is shown from the oblique rear, that is, from the inside, while Fig. 12B The pinion Z3 in the figure is viewed from the front, that is, from the outside. Arrow Rdd shows that the pinion Figure 1 The transmission rotation direction under the transmission load applied by the bicycle chain Cn is shown.

[0199] Since the pinion Z3 is an even-numbered pinion, Fig. 12A and Fig. 12B In the figure, the pinion teeth belonging to the wide pinion teeth Tw group are also marked with circle marks, and the pinion teeth belonging to the narrow teeth Tn group are also marked with square marks.

[0200] The outer shift channel is provided in the area indicated by Co, and the inner shift channel is provided in the area indicated by Ci (see Fig.11A The shift channels Ci and Co in Figure 2 , Fig. 9 and Fig.13 For example, the shift channel areas Co and Ci are marked on the pinion Z1).

[0201] like Fig. 12A As shown, in the shift channel areas Co and Ci, grooves are provided at the inner Ri1 and Ri2, or narrowed teeth Tw1, Tn1 and Tw3, Tn3 are provided at the back, see Fig.11A .exist Fig. 12BIn the embodiment, shift channel grooves Rc are provided at the outer sides Ro1 and Ro2, and narrowed teeth Ts1, Tw2 and Ts2, Ts3 are provided at the front side, see Fig.11A .

[0202] As described above, in order to maintain the shifting performance and to prevent shifting errors, the chain Cn needs to be switched to the next smaller pinion Z4 (outer gear) only in the area of ​​the outer shift channel Co. Fig. 12A and Fig. 12B Not shown, see e.g. Figure 2 ). To prevent the chain Cn from shifting to the next smaller pinion Z4 on the outside in the area of ​​the inner shift channel Ci, the pinion Z3 has stabilizing teeth Ts1, Ts2 and Ts3. The stabilizing teeth Ts1, Ts2 and Ts3 make the chain running displacement range in the area of ​​the stabilizing teeth Ts1, Ts2 and Ts3 smaller, preferably by one tenth of a millimeter, such as Fig.11A As shown in the operation of the chain Cn shown by the double dashed line at Cd, for example, it is displaced about 0.25 mm to the inside.

[0203] By means of this enhanced linear guidance of the chain Cn based on the stabilizing teeth Ts1, Ts2 and Ts3, it is prevented that, in particular after the chain Cn has passed through the outer shifting channel Co but has not shifted to the next smaller pinion Z4 there when the pinion Z3 is rotating, the chain Cn is prevented from being shifted to the outside in the area of ​​the inner shifting channel Ci, in particular in the area Ri1 with the teeth Tn1 and Tw1 which are narrowed at the back and which weaken the linear guidance of the chain on the pinion Z3.

[0204] Fig. 12A The thickening of the back or inner side of the stabilizing teeth Ts1 and Ts3 belonging to the narrow tooth group Tn and the associated displacement of the inner chain guide surfaces Gi1n and Gi3n to the inside can be clearly seen in FIG. Fig.11A In the stabilizing tooth Ts2 belonging to the wide tooth group Tw, there is also a thickening on the back or inside, which is associated with a displacement of the inner chain guiding surface Gi2w of the stabilizing tooth Ts2 to the inside and a correspondingly enhanced linear guidance of the chain Cn in this area.

[0205] The role of the stabilizing teeth Ts1, Ts2 and Ts3, and in particular the "wide" stabilizing tooth Ts2, is also very important when pedaling backwards. Figure 1 ) When the rider moves backward by pedaling backward with the pedal crank Dc, there is a risk that the chain, especially on a larger pinion, such as one of Z1 to Z3, will fall inward from the corresponding pinion due to the large chain deflection in this case, which may cause damage to the transmission system, especially the rear derailleur Rd.

[0206] This risk exists in particular in the area of ​​the shifting channels Ci and Co, where the narrowing teeth Tn1, Tw1 and Tw3, Tn3 are located on the back, ie on the inside, of these shifting channels (see FIGS. 11 and 12 ). Fig. 12A The regions Ri1 and Ri2 in the figure and the teeth Tn1, Tw1, Tw3, Tn3 which are narrowed at the back there. Even in this case of pedaling backwards, the stabilizing teeth Ts1, Ts2 and Ts3 with thickened backs will also enhance the linear guidance of the chain Cn, thereby reducing the tendency to jump out when pedaling backwards. This also applies in particular to the two shifting channel teeth Tw3 and Tn3 which are narrowed at the back in the region Ri2 and which are also provided with inclined ramps on the front (see Fig. 12B ), which makes the chain particularly easy to jump off when pedaling backwards, especially when the stabilizing tooth Ts2 with thickened back side does not play a compensating role.

[0207] The stabilizing teeth Ts1, Ts2 and Ts3 can also be arranged on other pinions than the pinion Z3 of the pinion arrangement Ap. In addition, the stabilizing teeth Ts1, Ts2 and Ts3 can also be used independently of each other, that is, for example, only one or two of the stabilizing teeth Ts1, Ts2 and Ts3 can be arranged on the pinion.

[0208] The application of the stabilizing teeth Ts1, Ts2 and Ts3 is also not limited to coarse and fine pinion gears. Specifically, the stabilizing teeth, such as the stabilizing teeth Ts1, Ts2 and / or Ts3, can also be used for standard pinion gears that do not include coarse and fine technology, that is, pinion gears in which substantially all teeth are fine gear teeth, that is, these fine gear teeth can mesh with the inner link plate middle gap of the inner link plate link of the bicycle chain.

[0209] In addition, the application of the stabilizing tooth is not limited to the aforementioned function of preventing outside shifting at an undesired position on the pinion. In addition to the aforementioned stabilizing tooth having an inside chain guide surface moved inwardly or having a chain guide size with a correspondingly increased and inside-moved span, in order to prevent outside shifting at an undesired position, the stabilizing tooth may also have an outside chain guide surface moved outwardly or a chain guide size with a correspondingly increased and outside-moved span, and be used to prevent inside shifting at an undesired position on the pinion of the multi-layer pinion cassette Ap.

[0210] The application of the stabilizing tooth is also not limited to the pinion flywheel or rear wheel pinion configuration Ap, but can also be used in Figure 1 The multi-layer sprocket Cr of the bicycle transmission system Td shown is applied.

[0211] Fig.13 A modular system for forming a multi-layer pinion configuration is illustratively shown, which can be implemented in accordance with the pinion configuration according to the present disclosure.

[0212] You can see the pinion configuration in Fig.13 In the embodiment shown, three modular components B1, B2 and B3 are defined by vertical surface areas, wherein in the embodiment shown, component B1 is formed by the inner final pinion device Pti, component B2 is formed by the first pinion set Sc1 and component B3 is formed by the further pinion set Sc2.

[0213] The assembly B1 formed by the inner final pinion arrangement Pti in the illustrated embodiment is present in this embodiment as a pinion star wheel Sp, which has two pinion rings Z1 / Rp1 and Z2 / Rp2 which can be fastened to the pinion star wheel Sp and can be screwed, riveted or pinned thereto, for example, cf. Figure 2 , Figure 3 and Fig. 9 , and the unit shown therein formed by the pinion star wheel Sp and the pinion rings Z1 / Rp1 and Z2 / Rp2 that can be riveted to the pinion star wheel Sp.

[0214] The assembly B2 formed by the first pinion set Sc1 in this embodiment of the modular assembly consists of five individual pinions Z3-Z7, see Figure 2 , Figure 5 , Figure 6 and Fig. 9 .

[0215] The assembly B3, in this case in the form of another pinion set Sc2, comprises pinions Z8 to Z11 in this embodiment of the modular assembly, thus corresponding, for example, to Figure 8 The other pinion gear set Sc2 is shown.

[0216] Furthermore, the modular system shown comprises a spacing unit Db which serves as a bridging connecting element between the components B1 , B2 and B3 and for this purpose assumes an advantageous multifunctional function. Fig.13 The spacer unit Db in Figure 2 and Fig. 9 Similarly, it is shown in a quarter section. The function of the spacer unit Db as a cross-linking element and the multifunctional function described in detail below should be Fig.13 The horizontal surface area F is used to represent it.

[0217] As mentioned above, especially in conjunction with Figures 2 to 5 As described, the spacer unit Db initially serves as a rotary bearing arrangement, by means of which the first pinion set Sc1 is rotatably supported in its outer region relative to the gear mechanism.

[0218] The first pinion gear set Sc1 is adapted to be rotatably supported on a bearing region Sb of a bearing device Db (see Figures 2 to 6 and Fig. 9) is formed by the outer final pinion Z7, which for this purpose has on its inner circumference an inner circumference region Ic which is designed in a shape corresponding to the bearing region Sb of the bearing device Db, i.e., also substantially in the form of a cylindrical surface (cf. Fig.10 And the inner peripheral area Ic in Figure 15). Fig.13 The double arrow A indicates the rotatable support of the first pinion set Sc1 on the inner circumferential region Ic of its outer final pinion Z7.

[0219] Of course, the outer final pinion Z7 never rotates during operation through such a large angular range as indicated by the double-headed arrow A. Rather, the outer final pinion Z7 usually rotates only through a small angular range due to the elastic rotational deformation of the first pinion set Sc1 that occurs when a transmission torque is applied to the outer pinion, in particular, of the first pinion set Cp1, for example when a transmission torque is applied to the pinion Z6 or Z7.

[0220] In contrast, the first pinion gear set Sc1 in the prior art is usually accommodated in a clamped manner on the outside in the force flow of the pinion gear arrangement extending axially along the rear wheel axle and is therefore not rotatably supported as in the pinion gear arrangement Ap here. The associated starting effect in the prior art leads to the disadvantages described in the introduction to the specification, for example to undesirable noises such as clicking and creaking, especially when a torque is applied to the first pinion gear set on the outside. Due to the uncontrolled occurrence of the starting effect in the prior art and due to the correspondingly sudden change in the force flow in the first pinion gear set and due to the strong vibrations that occur in the process, the above-mentioned disadvantages may also affect the fatigue strength of the first pinion gear set.

[0221] Since the first pinion gear set Sc1 is rotatably supported on the outer side on the rotary bearing device Db, this undesirable effect is avoided. When the transmission torque is applied to the pinions of the first pinion gear set Sc1, especially the outer pinions of the first pinion gear set Sc1, such as Z6 and Z7, the outer rotatable support of the first pinion gear set Sc1 causes the first pinion gear set Sc1 to rotate a small angle value on the outer side in a controlled manner, and it can deform elastically, and no strong starting effect or vibration will be generated in the first pinion gear set Sc1. This can improve the fatigue strength of the first pinion gear set Sc1 and prevent the undesirable generation of noise, such as clicking and creaking. Based on the improved fatigue strength, the first pinion gear set Sc1 also tends to adopt a thin-walled and lightweight implementation scheme.

[0222] In an advantageous functional combination, in addition to the aforementioned externally rotatably mounted further pinion set Sc1, the spacing unit Db also serves to determine the relative distance Da1 between the pinion star wheel Sp and the further pinion set Sc2. This can be achieved, for example, in Figure 3and are described in the corresponding figure description above. Fig.13 In FIG. 1 , the relative distance Da1 between the pinion star wheel Sp and the further pinion set Sc2 is indicated by the respective spacing arrow Da1 between the two vertical surface areas B1 / Pti and B3 / Sc2 .

[0223] In another advantageous functional combination, the spacing unit Db is used not only for the outer rotational support of the first pinion set Sc1 and for determining and maintaining the relative distance Da1 between the pinion star wheel Sp and the further pinion set Sc2, but also for determining and maintaining the relative distance Da2 between the pinion star wheel Sp and the outer final pinion Z7 of the first pinion set Sc1. This can be achieved in particular in Figure 5 It is clearly seen in the figure and is explained in the corresponding figure description. Fig.13 In FIG. 1 , the relative distance Da2 between the pinion star wheel Sp and the outer final pinion Z7 of the first pinion set Sc1 is indicated by the respective spacing arrow Da2 between the respective boundaries of the two vertical surface areas B1 / Pti and B2 / Sc1 .

[0224] This means that the spacing unit Db also assumes the task of determining and maintaining the width Da2 of the first pinion set Sc1 in an advantageous functional combination (see Figure 5 ).

[0225] In addition, the spacing unit Db also has the task of determining and maintaining the relative distance Da3 between the outer side of the first pinion gear set Sc1 and the inner side of the second pinion gear set Sc2. Figures 2 to 4 And especially clearly in Figure 5 and described in the corresponding figure description above. Fig.13 , the relative distance Da3 between the outer side of the first pinion set Sc1 and the inner side of the second pinion set Sc2 is indicated by the respective spacing arrow Da1 between the two vertical surface areas B1 / Pti and B3 / Pto.

[0226] As mentioned above Figure 4 As explained in the description, in addition to the aforementioned functions of rotatably supporting the first pinion gear set Sc1 on the outside and setting and maintaining the relative distances Da1, Da2, Da3 between the pinion star wheel Sp, the first pinion gear set Sc1 and the second pinion gear set Sc2, the spacing unit Db also performs the function of an axial tensioning element for mounting the pinion configuration Ap on the transmission device Dd.

[0227] The bearing device Db is used in particular to transmit the mounting tension force between the pinion star wheel Sp and the further pinion gear set Sc2 in the axial direction Da of the rear wheel shaft. In the state where the pinion gear arrangement Ap is mounted on the transmission device Dd, the mounting tension force is part of a closed clamping force flow Ff extending substantially parallel to the rear wheel shaft through the transmission device Dd and the pinion gear arrangement Ap, see Figure 4 and the corresponding description.

[0228] Unlike the prior art described at the outset, the outer final pinion Z7 of the first pinion set Sc1 is not tensioned in the axial force flow Ff, which in the prior art could lead to the disadvantages described at the outset, especially with regard to noise generation and fatigue strength of the pinion arrangement, but remains rotatable relative to the transmission Dd with a friction force that is extremely low compared to the prior art and is independent of the axial preload force Ff. This is the case in particular when the spacer unit Db is preferably made of plastic.

[0229] To summarize, the spacing unit Db is suitable for rotatingly supporting the first pinion gear set Sc1 on the outside, for determining all relative distances Da1, Da2, Da3, and for transmitting all rear wheel axle axial tensioning forces between the pinion star gear Sp, the outer final pinion gear Z7 of the first pinion gear set Sc1 and the second pinion gear set Sc2.

[0230] Therefore, based on this multifunctional Fig.13 In the modular system shown as the pinion arrangement Ap, the spacer unit Db also plays a crucial role in the long-term reliability of the pinion arrangement Ap and the precision when shifting with the help of the rear derailleur Rd. In addition, it is also the central connecting element of the modular system's modularly replaceable components B1, B2 and B3.

[0231] for Fig.13 It is also important to note that the modular system shown Fig.13 The embodiment shown refers to a pinion configuration Ap in which all pinions Z1-Z11 are coarse and fine pinions. Fig.13 The modular system shown here can be combined with the latest coarse and fine pinion pinion technology with the standard transmission Dd or the corresponding standard cassette hub that has been known for decades and can thus be adapted to almost all bicycles or rear wheels with such a standard transmission Dd or the corresponding standard cassette hub. This also applies analogously to Figures 2 to 12B and FIG. 14A to FIG. 15C Pinion configuration Ap.

[0232] Fig.14A A further embodiment of a multi-level pinion arrangement Ap with a spacing unit Db for rotatably supporting Sb the first pinion set Sc1 on the outside is shown.

[0233] First of all, the standard transmission Dd with the transmission profile Pd can also be seen. The pinion arrangement Ap also includes an inner final pinion arrangement Pti, which is in the form of a final pinion Z1 in this case, which is also referred to in the industry as a star wheel pinion, because it performs both the functions of a pinion and a load-bearing star wheel. Here, the star wheel pinion carries both its own toothing Z1 and the inner final pinion Z2 of the self-supporting first pinion set Sc1.

[0234] The pinion configuration Ap also includes a first pinion set Sc1 and an outer final pinion device Pto, which also exists here in the form of another pinion set Sc2. In particular, when the pinion set refers to an integrated pinion set, for example, welded from multiple individual pinions, it is also referred to as a micro pinion set in the industry.

[0235] The screw plug device Sd, also known in the industry as a locking ring, is used to fasten the pinion arrangement Ap to the transmission device Dd. The screw plug device Sd has an external thread Te, not specifically shown here, which can be screwed into the internal thread Ti of the transmission device Dd. This produces a similar Figure 4 The closed fastening force flow Ff is shown extending generally parallel to the rear wheel axle through the transmission Dd and the pinion arrangement Ap. The fastening force flow Ff holds the components or modules of the pinion arrangement Ap together, while similar to the above in Figure 4 As explained in the description of , it is used to fasten the pinion arrangement Ap to the transmission device Dd.

[0236] In this embodiment, the first pinion set Sc1 is also mounted on the outside so as to be rotatable relative to the gear mechanism Db, for which purpose the spacing unit Db has a preferably approximately cylindrical bearing region Sb.

[0237] In order to rotatably support the first pinion gear set Sc1 on the outside, the outer pinion gear Z9 of the first pinion gear set Sc1 has an inner peripheral area Ic on its inner periphery that corresponds in shape to the support area Sb of the bearing device Db, i.e., is also substantially cylindrical (see Fig.10 , Fig.13 and Fig.15A ).

[0238] Different from Figures 1 to 13 The illustrated embodiment of the spacing unit Db comprises a substantially cylindrical region and a flange-shaped stop St in one piece. Fig.14A In the embodiment shown, the spacing unit Db is substantially of two-part design, since the collar-shaped stop St is formed here by a separate annular element.

[0239] exist Fig.14AIn the embodiment shown, the spacer unit Db has the additional function of vibration reduction or sound absorption. To this end, the spacer unit Db is equipped with a receiving recess in which a vibration-damping plastic element Ee is arranged, such as a block made of an elastomer or a vibration-absorbing foam material.

[0240] When the pinion arrangement Ap is mounted on the transmission Db, the vibration-damping plastic element Ee rests on the arm As of the star wheel pinion Pti / Z1 and is clamped between the arm As and the spacer unit Db. This allows undesired vibrations to be introduced into the vibration-damping plastic element Ee via the pinion arm As and converted there into heat.

[0241] In a pinion arrangement Ap, such as the subject of the present disclosure, such undesirable vibrations, in particular in the audible sound range, frequently occur due to the large number of pinions, due to the larger diameter of such a pinion arrangement Ap and in particular due to the light construction of such a pinion arrangement with the self-supporting pinion set Sc1 and are generally regarded as disruptive during the operation of the bicycle.

[0242] This self-supporting first pinion gear set Sc1 is Figure 2 , Figure 3 , Figure 5 , Figure 6 , Fig. 9 , Fig.13 , Fig.14A and Fig.15A The self-supporting pinion set Sc1 shown therein consists of individual pinions Z3 to Z7 ( Figure 2 , Figure 3 , Figure 5 , Figure 6 , Fig. 9 , Fig.13 ) or by a single pinion Z2 to Z9 ( Fig.14A ) in which the individual pinions are connected by pins (or in FIG. 15 by means of additional brackets).

[0243] This self-supporting pinion set Sc1, which can also be constructed as an integral milled part, has the following characteristics: this pinion set is connected to other components or modules of the pinion arrangement only in the area of ​​its two final pinions on the inner and outer sides, for example, to the star wheel pinion Pti / Z1 on the inner side (e.g. Fig.14A as shown) or connected to the pinion star wheel Sp (as shown Figures 2 to 6 , Fig. 9 , Fig.13 The pinions of this self-supporting pinion gear set between the inner and outer final pinions are only connected to the adjacent pinions, thereby forming a conical or truncated cone-shaped self-supporting structure of the pinion gear set.

[0244] An alternative embodiment of the spacer unit Db is the spacer unit Db2 in the right area of ​​Figure 14. This spacer unit Db2 also has a vibration-damping plastic element Ee, which is designed as an O-ring in this embodiment. When the pinion arrangement Ap is mounted on the transmission Db, this annular plastic element Ee abuts against the annular radial inner abutment area of ​​the star wheel pinion Pti / Z1 and can in this way help to reduce undesirable acoustic vibrations of the pinion arrangement Ap.

[0245] Fig. 14B Another embodiment of the spacing unit Db3 is shown. This spacing unit Db3 is also integrally formed, similar to Figures 2 to 5 as well as Figures 9 to 13 It can be seen that the spacer unit Db3 has two synchronous protrusions Es1 and Es2.

[0246] The first synchronization protrusion Es1 forms an inwardly directed extension of the radially inner toothing structure of the spacing unit Db3 in the axial direction Da, and the extension corresponds in shape to the toothing transmission profile Pd of the transmission device Db.

[0247] Standard transmissions that have been known and used in the industry for decades, such as Figures 2 to 9 and Fig.14A The transmission device Dd shown has a toothed transmission profile Pd with a rotational encoding. The rotational encoding is that one of the transmission recesses extending along the transmission device Dd in the axial direction Da and distributed on the outer circumference of the transmission device Dd has a greater width than the remaining transmission recesses, and these transmission recesses together form the toothed transmission profile Pd. As a result, a pinion with an internal toothed profile Pe with a corresponding shape and corresponding rotational encoding can only be inserted into the transmission device Dd at a specific relative rotational angle.

[0248] This allows the shift channels Ci and Co (see Figure 2) to be arranged on the pinion gears in order to control the chain transfer during gear shifting. Figure 2 , Fig. 9 , Fig. 12A / B and Fig.13 The shift channels Ci and Co) in the control unit are arranged in the correct relative rotational positions to prevent installation errors.

[0249] but Fig.14AThe star wheel pinion Pti / Z1 of the pinion arrangement Ap shown has an internal toothing profile Pe without such a rotational coding, because in addition to the pinion arrangement Ap shown, this star wheel pinion Pti / Z1 is also used substantially unchanged for a one-piece pinion arrangement or pinion flywheel. In a one-piece pinion arrangement or pinion flywheel, the rotational position of the pinion flywheel on the transmission Dd is irrelevant, because due to the one-piece nature of the pinion flywheel, all shift paths of all pinions already occupy the correct rotational relative position relative to all other pinions. Since the rotational position relative to the transmission Dd is irrelevant in such an one-piece pinion flywheel, such an one-piece pinion flywheel usually has an internal toothing profile Pe without rotational coding, so that it can be pushed onto this transmission Dd in any rotational position even in the case of a transmission with a rotationally coded toothing transmission profile Pd as described above.

[0250] Before installation on the transmission Dd, Fig.14A The pinion configuration Ap shown is composed of at least two independent flywheel modules Mc1 and Mc2, which must be based on the shift paths present on these two flywheel modules Mc1 and Mc2 (see for example Figure 2 , Fig. 9 , Fig. 12A / B and Fig.13 The shift channels Ci and Co in the flywheel module Mc1 are inserted into the transmission Dd at a specific relative rotational angle. However, this cannot be guaranteed in the flywheel module Mc1 when it is initially inserted into the transmission Dd, because, as mentioned above, the internal toothing profile Pe of the star wheel pinion Pti / Z1 of the flywheel module Mc1 does not have a rotational encoding.

[0251] Therefore, the spacing unit Db3 has a synchronization protrusion Es1. The synchronization protrusion Es1 forms an axial extension of the rotationally encoded internal tooth system profile Pe of the spacing unit Db3, which is composed of meshing protrusions Ep extending in the axial direction Da and distributed on the inner circumference of the spacing unit Db3. The synchronization protrusion Es1 particularly forms an axial extension of the meshing protrusion Ep1 of the rotationally encoded internal tooth system profile Pe, which has a width greater than the remaining transmission protrusions Ep of the internal tooth system profile Pe of the spacing unit Db3, so as to be suitable for meshing with the transmission recess of the tooth system transmission profile Pd of the transmission device Dd, which transmission recess correspondingly has a larger width than the remaining transmission recesses of the transmission profile Pd of the transmission device Dd.

[0252] In the bay unit Db3 is installed, for example Fig.14AIn the state on the flywheel module Mc1 of the pinion configuration Ap shown, the synchronization projection Es1 penetrates the non-rotationally encoded internal toothing profile Pe of the star wheel pinion Pti / Z1 of the flywheel module Mc1 and thereby converts the non-rotationally encoded internal toothing profile Pe of the star wheel pinion Pti / Z1 into a rotationally encoded internal toothing profile Pe. Thus, the synchronization projection Es1 of the spacing unit Db3 ensures that the flywheel module Mc1 can only be pushed onto the transmission Dd in a preset specific rotational relative position when it is initially pushed onto the transmission Dd.

[0253] The second synchronization protrusion Es2 extends inwardly from the flange-shaped stopper St of the spacing unit Db3 in the axial direction Da. Fig.14A In the state on the flywheel module Mc1 of the pinion configuration Ap shown, the second synchronization protrusion Es2 meshes with the synchronization groove Ns arranged on the outer end side of the flywheel module Mc1, for example, on the outer end side of the outer final pinion Z7 of the pinion set Sc1. Fig.13 and Fig. 17C An example of a synchronizing groove Ns on the outer end side of the outer final pinion Z7 of the pinion set Sc1 can be seen in FIG.

[0254] In particular, when manufacturing the pinion arrangement, i.e. when the pinion set Sc1 is connected to the star wheel pinion Pti / Z1 via the connecting pin Cp, the second synchronization projection Es2 ensures in this way the correct rotational relative position between the pinion set Sc1 and the spacing unit Db3 and its rotationally encoded internal gearing profile Pe. In this manufacturing step, before the pinion set Sc1 is connected to the star wheel pinion Pti / Z1 via the connecting pin Cp, the shift paths Ci and Co of the pinion set Sc1 and the star wheel pinion Pti / Z1 must be ensured (see Figure 2 , Fig. 9 , Fig. 12A / B and Fig.13 The correct rotational relative position of the shift channels Ci and Co).

[0255] Fig.15A An alternative embodiment of the self-supporting pinion gear set Sc1 is shown. Fig.15A In the self-supporting pinion gear set Sc1 shown in FIG. 1 , the individual pinions Z3-Z8 are not only Figure 2 , Figure 5 , Figure 6 , Fig. 9 and Fig.14A As a supplement or replacement for the connecting pin Cp1, Fig.15A In the embodiment shown, the individual pinions Z3-Z8 are connected via a plurality of star carriers Cs.

[0256] The individual pinions Z3-Z8 can be connected to the star carrier Cs by any connecting elements, such as screws, rivets or pins, which are FIG. 15A to FIG. 15C As an alternative or supplement to such connecting elements, the individual pinions Z3-Z8 can also be connected to the star wheel carrier Cs by bonding. The star wheel carrier Cs can be made of metal, or alternatively of non-metallic material, in particular of fiber reinforced plastic.

[0257] Especially in Fig. 15B The three-dimensional hierarchical spatial structure of the star wheel carrier Cs can be seen in the outer side view shown. Through this structure, when observed along the direction Da parallel to the rear wheel axle Ar, six axially spaced fastening steps Lf3-Lf8 are formed in this embodiment, and six individual pinions Z3-Z8 can be abutted and fastened on these fastening steps.

[0258] In this way, a self-supporting pinion set Sc1 is obtained which has a low mass and high torsional and bending rigidity.

[0259] Fig.16 Another embodiment of the pinion gear arrangement Ap is shown similar to Fig. 9 A partially cutaway exploded view of Fig. 9 As shown, a pinion arrangement Ap is also shown together with a rear wheel transmission Dd, on which the pinion arrangement Ap can be mounted in a torque-transmitting manner.

[0260] Fig.16 Zhongyu Fig. 9 Components and subassemblies consistent with Fig. 9 The same reference numerals are used in Fig. 9 The details are described in the accompanying drawings.

[0261] Fig.16 The embodiment shown is Fig. 9 The embodiment shown (the latter of which is also generally similar to Figures 2 to 8 The main difference is that, on the one hand, the single pinion Z8 is different from Fig. 9 On the one hand, there is a multifunctional spacing element Ems, which is embodied as an additional pinion device Pi.

[0262] Fig.16 The single pinion Z8 shown with Figures 2 to 7 and Fig. 9 The difference of the single pinion Z8 shown is that Fig.16The single pinion Z8 shown has a meshing profile Pe on its inner circumference, which is designed in the form of a groove (Durchzug) produced by stamping or deep drawing, for example. This can greatly widen or increase the width of the contact surface of the meshing profile Pe with the transmission Dd, thereby reducing the surface pressure between the meshing profile Pe and the toothing transmission profile Pd arranged on the outer circumference of the transmission Dd. This can better transmit high torques between the single pinion Z8 and the transmission Dd, especially when the single pinion Z8 and / or the transmission Dd are made of relatively soft light metal instead of steel.

[0263] The multifunctional spacing element Ems has the function of an annular spacing element between the single pinion Z8 and the other pinion set Sc2 (see Fig. 9 ), on the other hand, in the pinion arrangement Ap not mounted on the transmission Dd, i.e. Figure 1 Shown without being mounted on a bicycle rear wheel Wr, it also has the function of connecting all components of the pinion arrangement Ap into an integrally maneuverable unit.

[0264] Combination Fig.16 and Fig.17A -C It can be seen that the multifunctional spacing element Ems, with the help of its three elastic clamping arms Ac here, passes through the notch groove Ct of the single pinion Z8 and spans the width range of the single pinion Z8 and the width range of the flange-shaped stopper St integrally formed on the bearing device Db here.

[0265] In addition, the three elastic clamping arms Ac of the multifunctional spacer element Ems also span the width of the outer final pinion Z7 of the first pinion gear set Sc1. Specifically, the elastic clamping arms Ac pass through the corresponding notch grooves Ct of the outer final pinion Z7.

[0266] The snap-fit ​​protrusion Pl arranged on the inner end of the elastic clamp arm Ac clamps the notch groove Ct of the outer final pinion Z7 from the back in this way, so that all components of the pinion configuration Ap except the outer final pinion device Pto which exists here as another pinion set Sc2 are held together by the elastic snap action of the clamp arm Ac of the multifunctional spacer element Ems.

[0267] In other words, the multifunctional spacing element Ems holds the outer final pinion Z7 of the first pinion set Sc1 (which is connected to all other pinions Z1-Z6 of the first pinion set Sc1 and to the star wheel pinion Sp into a fixed unit Sc1+Pti=Mc1 based on the pin connection Cp1 and the riveting Jr) together with the single pinion Z8 and the rotating bearing device Db in such a way that these components or assemblies together with the multifunctional spacing element Ems form an integrally operable unit.

[0268] In order to additionally accommodate the outer final pinion device Pto, which is in this case another pinion set Sc2, in the aforementioned integrally operable unit, the multifunctional spacing element Ems has a plurality of, preferably at least three, clamping projections Pg on the outer circumference. The clamping projections Pg together define an outer diameter, the size of which is somewhat larger than the preferably cylindrical inner shoulder Si arranged on the inner circumference of the other pinion set Sc2, see Fig.16 .

[0269] Thereby, the other pinion set Sc2 can be pressed or pressed onto the clamping protrusion Pg of the multifunctional spacing element Ems, thereby being connected to the multifunctional spacing element Ems.

[0270] Thus, the multifunctional spacing element Ems in this way holds together the inner final gear arrangement Pti, the first pinion set Sc1, the further pinion arrangement Pi (in this case in the form of an intermediate pinion Z8), the outer final gear arrangement Pto (in this case in the form of a further pinion set Sc2) and the bearing arrangement Db in the form of an integrally manipulable unit, see in particular Fig.17A .

[0271] This is advantageous for most handling steps after the manufacture of the pinion arrangement Ap, such as packaging, transport and logistics, removal from the packaging at the customer and mounting of the pinion arrangement Ap on the transmission Dd of the bicycle rear wheel Wr by the customer.

[0272] This not only simplifies the handling of the pinion arrangement Ap, but also prevents installation errors. Otherwise, installation errors may occur if one or more of the modules or components "flywheel module Mc1 = inner final pinion device Pti + first pinion set Sc1", "further pinion device Pi", "bearing device Db" and "outer final pinion device Pto" are assembled together by the manufacturer or customer, for example in an incorrect rotational relative position relative to the other modules or components of the pinion arrangement Ap. This can significantly affect the efficiency, shifting performance and service life of the pinion arrangement, or make it impossible to install the pinion arrangement Ap on the transmission Dd.

[0273] Combination Fig.17A and Fig. 17CThe rotational coding of the intermediate pinion Z8 or the further pinion arrangement Pi relative to the outer pinion Z7 of the first pinion set Sc1 and relative to the bearing arrangement Db or the determination of the relative rotational position by means of the multifunctional spacing element Ems can be seen, as will be described below. This determination of the rotational coding also applies to the entire unit Sc1+Pti=Mc1 based on the pinion connection Cp1 of the intermediate pinion Z8 and the riveted connection Jr to all other pinions Z1-Z6 of the first pinion set Sc1 and to the pinion star wheel Sp.

[0274] Fig. 17C The bearing device Db is shown as a flange-shaped stopper St (see FIG. 1 ) extending inward from the bearing device Db in the axial direction Da. Figures 2 to 7 and Fig.17A ) extends outwardly from the synchronous projection Es2 (see Fig. 14B ) is engaged with the synchronization groove Ns arranged on the outer end side of the flywheel module Mc1, for example, on the outer end side of the outer final pinion Z7 of the first pinion set Sc1, so as to determine the rotational relative position of the bearing device Db and the flywheel module Mc1.

[0275] Fig. 17C The drawing is based on a high perspective view so that all important elements can be clearly seen. In particular, the apparent inwardly pointedness of the bearing device Db is a result of this perspective view. The bearing device Db is in fact substantially cylindrical, as can be seen from most of the other figures and e.g. Fig.17A This can be seen in .

[0276] At the same time, the rotational relative position of the bearing device Db and the intermediate pinion Z8 or another pinion device Pi is determined by the multifunctional spacing element Ems in that a plurality of flange-shaped stops St (see FIG. 1 ) extending outwardly from the bearing device Db in the axial direction Da are provided. Figures 2 to 7 and Fig.17A ) The protruding directional projection Po engages the corresponding pinion arm As of the intermediate pinion Z8 (see Fig. 17C and Fig.16 ).

[0277] The engagement of the directional projection Po of the bearing device Db with the pinion arm As of the intermediate pinion Z8 simultaneously ensures that the intermediate pinion Z8 is centered relative to the remaining components of the pinion configuration Ap, the transmission Dd and subsequently the rear wheel axle Da of the rear wheel Wr of the bicycle 1, thereby simplifying the installation of the pinion configuration Ap on the transmission Dd.

[0278] The bearing device Db also has the task of centering the outer final pinion Z7 of the pinion set Sc1 and the outer side of the entire flywheel module Mc1, which consists of the inner final pinion device Pti and the first pinion set Sc1 (see Figure 2 , Figure 5 , Figure 6 , Fig. 9 , Fig.14A , Fig.16 and Fig.17A For this purpose, the bearing device Db provides a substantially cylindrical bearing area Sb, against which the inner diameter of the outer final pinion Z7 of the first pinion set Sc1 rests, see Figures 2 to 7 as well as Fig. 9 , Fig.14A , Fig.16 and Fig.17A .

[0279] Finally, the radial recess Rr formed on the flange-like stop St of the bearing device Db corresponding to the elastic clamping arm Ac of the multifunctional spacing element Ems ensures the determination of the rotational relative position between the multifunctional spacing element Ems and the bearing device Db, see Fig.16 .

[0280] Thus, the correct rotational relative position and coaxial centering of all modules or components of the pinion arrangement Ap, "flywheel module Mc1 = inner final pinion arrangement Pti + first pinion set Sc1", "further pinion arrangement Pi" or "intermediate pinion Z8", "bearing arrangement Db" and "outer final pinion arrangement Pto", are ensured by the multifunctional spacing element Ems in conjunction with, in particular, the elements Es2, Ns, Ac, Rr, Po, As and Db. This brings about the advantages already mentioned above with regard to transport and error-free installation of the pinion arrangement Ap on the transmission Dd of the rear wheel Wr of a bicycle.

[0281] In addition to the aforementioned outer synchronous protrusion Es2, Fig.16 and Fig.17A The bearing device Db of the embodiment of the pinion arrangement Ap shown also has an inner synchronization projection Es1, which helps the pinion arrangement Ap to be rotationally correctly pushed onto the transmission device Dd under certain boundary conditions. This has already been described above with reference to Fig. 14B The description is explained in detail.

[0282] Figures 18 to 21 show in particular Figure 2 to Figure 1 7 shows a schematic cross-sectional view or detailed view of a wide pinion tooth Tw of a pinion arrangement Ap, wherein arrows Rdd indicate the transmission rotation direction of the pinion under the transmission load applied by the bicycle chain Cn, see Figure 1 The cross-sectional views or detailed views of the pinion teeth shown in FIGS. 18 to 21 may particularly relate to, for example, Fig.10 The wide pinion teeth Tw of the smaller pinions Z6-Z12 of the pinion arrangement Ap shown. The wide pinion teeth Tw shown in Figures 18 to 21 can be generally in the same form, but in principle according to Figures 1 to 17C Each of the pinions Zx of the pinion configuration Ap shown is implemented.

[0283] The wide pinion teeth Tw shown in FIGS. 18 to 21 preferably refer to the wide pinion teeth Tw of a pinion manufactured by a stamping and coining process.

[0284] Fig.18A The shape of the wide pinion tooth Tw shown is roughly equivalent to Fig.10 The shape of the wide pinion teeth Tw of the pinion Z6 in FIG. Consistent with other drawings showing wide teeth Tw and / or narrow teeth Tn, in FIGS. 18 to 21 , the wide teeth Tw are also indicated by small circle marks, and the narrow teeth Tn are also indicated by small square marks.

[0285] Similar to Fig.10 ,exist Fig.18A It can also be seen that the thickness Tb of the base material of the pinion (which preferably corresponds to the width of the narrow tooth Tn, see Fig.10 , Figures 4 to 7 As can also be seen in Figure 1, the increased width Ww of the wide tooth Tw is caused by the embossing Di, which is usually on the outer end face of the pinion Zx. When the pinion is pressed, the embossing Di causes material displacement and produces a corresponding protrusion Dp on the opposite, usually inner end face of the corresponding pinion.

[0286] exist Fig.18B This is also the case with the wide pinion teeth Tw shown, which are for example Fig.10 The width of the pinion Z8 is roughly consistent with the pinion tooth Tw. Fig.18B The width of the pinion tooth Tw shown is Fig.18A The main difference between the wide pinion teeth Tw shown is that in Fig.18B In the wide pinion tooth Tw shown, the outer embossing Di and the inner protrusion Dp are constructed asymmetrically along the circumferential direction or rotation direction Rdd of the pinion Zx. The advantage of this construction scheme is that Fig.18B The pinion tooth Tw is shown on its load flank side Fl (see Fig.10 ) and has more load-bearing material there.

[0287] This is because Fig.18B The asymmetric design of the stamping Di and the protrusion Dp on the wide pinion tooth Tw shown in the figure makes it possible to omit the matching stamping Ec on the load tooth surface side. Fig.18A This matching impression is also required in the wide pinion tooth Tw shown to produce the desired material displacement Di, Dp from the outside to the inside.

[0288] Fig.18C Shows Fig.18BA technical variant of the wide pinion tooth Tw shown. Fig.18C In the wide pinion tooth Tw shown, the mating impression Ec extending transversely with respect to the longitudinal axis of the pinion tooth extending radially relative to the pinion is arranged so that the two side walls Ws of the impression Di are in the circumferential direction of the pinion Zx relative to the transmission load of the bicycle chain Cn (see Figure 1 ) support each other. Thus, we can obtain Fig.18C The pinion teeth Tw shown are particularly resistant to chain loads.

[0289] Fig.19A In the direction of viewing the outer end side of the pinion Z8, that is, from the same direction as, for example, Figure 1 The same viewing direction shows Figure 2 to Figure 1 7 shows another embodiment of the pinion gear arrangement. The pinion gear Z8 is also a pinion gear with coarse and fine teeth, that is, it has narrow teeth Tn that can mesh with the gaps Wco in the outer link plates of the bicycle chain and the gaps Wci in the inner link plates (see FIG. Fig. 11B ), and having wide teeth Tw' that can only engage with the gaps Wco in the outer link plates of the bicycle chain but cannot engage with the gaps Wci in the inner link plates. As mentioned above in Fig.10 As described in detail in , advantages can be achieved in this way, especially with regard to stable chain running and shifting behavior.

[0290] The tooth Tw3' of the pinion Z8 has no outer impression Di, since this tooth, although nominally designated as a "wide" tooth Tw, is located in the region of the outer shift channel Co, cf. Fig.11A and Fig. 12A The teeth Tw1 , Tw3 shown at +B, which are also located in the region of the shifting channels Co, Ci, are also only nominally “wide”.

[0291] Such teeth Tw1, Tw3, Tw1', Tw3', which are nominally "wide" but are arranged in the area of ​​the shifting channels Co, Ci, usually have no outer impression Di and accordingly no inner projection Dp, because at least in the inner area Ri1, Ri2 of the shifting channels Co, Ci, the inner projection Dp (see Figures 11-12) is undesirable and can interfere with the transition of the chain to the adjacent pinion during the shifting process, see Fig.11A and Fig. 12A The same also applies analogously to the likewise only nominally “wide” Tw1 ′ of the pinion Z8 which is arranged in the region of the inner shifting channel Ci.

[0292] Fig.19B Shows Fig.19A The width of the pinion gear Z8 is shown along the pinion gear tooth Tw' Fig.19AA cross-sectional view of the cross-sectional profile AA is shown. Fig. 20B Shows Fig.19A An oblique view of the wide pinion tooth Tw' of the wide pinion Z8. Fig.19A +B and the principle and corresponding tooth geometry of the wide pinion tooth Tw' shown in Figure 20 also apply to Fig.10 On the wide pinion tooth Tw of the smallest pinion Z12 in the chain. In the case of the wide pinion tooth Tw of the pinion Z12, only the inside / outside direction is interchanged mirror-inverted. In other words, on the wide pinion tooth Tw of the smallest pinion Z12, the impression Di is on the inside and the projection Dp is on the outside, for optimizing the chain running, especially on the smallest pinion.

[0293] exist Fig.19A , Fig.19B and Fig. 20B In the pinion Z8 shown, the thickness Tb of the pinion basic material is also consistent with the width of the narrow tooth Tn, and the width Ww' of the wide tooth Tw' is also generated by the deformation caused by the material displacement Di and Dp from the outer end face of the pinion Z8 to the inner end face of the pinion Z8 during the stamping and pressing of the pinion Z8.

[0294] Fig. 20A The tooth shape of the wide tooth Tw shown (see Fig.18A -C) and Fig. 20B The tooth shape of the wide tooth Tw' shown (see Fig.19A +B) shows, in particular, the different arrangements and shapes of the outer embossing Di, which results in correspondingly different shapes of the inner protrusions Dp on the corresponding wide teeth Tw or Tw'. Fig. 20B The wide tooth Tw' shown (see Fig.19A +B), this can lead in particular to a width Ww' of the wide tooth Tw' being much greater than Fig. 20A The width Ww of the wide tooth Tw shown (see Fig.18A -C).

[0295] This is due to the following facts: Fig. 20B The wide tooth Tw' (roughly equivalent to Fig.19A +B shows the width of the small gear teeth Tw'), and Fig. 20A The width of the pinion gear Tw (roughly equivalent to Fig.18A Compared with the wide pinion tooth Tw shown in FIG. 1 , the outer impression Di has a much larger volume and depth. Fig. 20B and Fig.19A In the wide pinion tooth Tw' shown in +B, the volume and width of the inner protrusion Dp are also much larger than Fig. 20A and Fig.18A The width of the pinion tooth Tw is shown. This can also be seen from Fig. 20B and Fig.19A+B shows the wide pinion tooth Tw' and the above described Fig.18B , Fig.18C This can be seen in the comparison of the width of the pinion tooth Tw shown.

[0296] exist Fig.19A +B and Fig. 20B In the wide pinion tooth Tw' shown, the relatively large volume and width are achieved by the special shaping of the embossing Di and the protrusion Dp, which can be combined with Fig.19A +B and Fig. 20B It can be seen clearly. Fig.19A +B and Fig. 20B In the illustrated wide pinion tooth Tw', the embossing Di and the projection Dp almost completely surround the non-loaded tooth flank Fn of the corresponding pinion tooth in the region of material displacement from the outside to the inside.

[0297] In contrast, Fig.18A -C shows that the non-loaded tooth surface Fn of the wide pinion tooth Tw (similar to the loaded tooth surface Fl) is in a constant basic position along the rear wheel shaft axial direction Da within the thickness Tb of the pinion basic material. This means that Fig.19A +B and Fig. 20B In the embodiment shown, the pinion base material can only be deformed to a much lesser extent.

[0298] The latter can also be obtained from Fig.21A and Fig. 21B Seen again in. Fig.21A Shows Fig.18A and Fig. 20A The wide tooth Tw shown is Fig.19A +B and Fig. 20B Graphical overlay of wide tooth Tw' shown. Fig. 21B Shows Fig.18B The wide tooth Tw shown is Fig.19A +B and Fig. 20B Graphical overlay of wide tooth Tw' shown.

[0299] Combination Fig.21A and Fig. 21B It can be seen that Fig.19A +B and Fig. 20B The wide tooth Tw' (in Fig.21A and Fig. 21B Based on the dashed lines in particular Fig. 20B The special design shown and described in the corresponding figure description above, comprises a non-load bearing tooth surface Fn extending into the impression Di and having a considerable width Ww': Fig.18A -C shows the case of wide tooth Tw, the width Ww' is much larger than the thickness Tb of the pinion base material.

[0300] Relative to Fig.21A The wide tooth Tw shown in solid line (see Fig.18A ) and its tooth width Ww, the wide tooth Tw' ( Fig.19A +B and Fig. 20B ) obviously has a larger width Ww'. This also applies similarly to Fig. 21B The wide tooth Tw shown in solid line (see Fig.18B ). Fig.21A The wide tooth Tw in (shown by solid line, see Fig.18A and Fig. 20A ), wide tooth Tw'( Fig.21A The dotted line in the figure also has a material thickness Tm' on the load tooth surface F1 side that is greater than the material thickness Tm of the wide tooth Tw.

[0301] This way, you can Fig.21A +B shows the wide tooth Tw' pinion Z8 or Zx (see Fig.19A +B and Fig. 20B ) to achieve excellent chain guiding performance with wide teeth Tw'. As mentioned above, especially in Fig.11A As described in FIG. 1B, the wide teeth Tw' are designed to engage specifically with the outer link plate intermediate gap Wco of the outer link plate link Lo.

[0302] Thanks to Fig.21A +B or Fig.19A +B and Fig. 20B The design of the wide teeth Tw' shown in the figure not only allows the chain to mesh with the inner plate intermediate space Wci of the inner plate chain link Li through the narrow gear teeth Tn (see Fig.11A +B), also through the close and particularly effective guiding engagement with the outer link plate intermediate gap Wco of the outer link plate chain link Lo, along the chain movement direction Dmc (see Figure 1 ) to be guided.

[0303] This also applies in particular to Fig.19A The wide tooth Ts2' at the bottom of the diagram is located in the overlapping area of ​​the outer shift channel Co and the inner shift channel Ci in the pinion Z8 with 18 teeth. As a stable tooth for chain operation, the tooth Ts2' is particularly important for chain guidance, because the pinion teeth surrounding the tooth Ts2' are narrowed or even greatly narrowed due to the shift channels Ci and Co in which they are located. The corresponding relationship is also described above for Fig.11A Detailed description in the .

[0304] The particularly important guiding task of tooth Ts2' in the area of ​​the shifting channels Ci, Co is irrelevant whether the chain guiding dimension Dcw1 across the teeth is increased on tooth Ts2' (see in particular the corresponding description in FIG. 11 ), or whether tooth Ts2' refers to a "normal" wide tooth Tw or Tw' whose width Ww or Ww' corresponds to the width Ww or Ww' of other wide teeth Tw or Tw' of pinion Z8 or Zx.

[0305] In addition to Fig.19A +B, Fig. 20B and Fig.21A In addition to the larger tooth width Ww' associated with the wide tooth Tw' shown in the +B (dashed line), in this wide tooth Tw', the flat contact surface Fc' is also much larger than Fig.18A C. Fig. 20A and Fig.21A +B (solid line) shows the flat contact surface Fc of the wide tooth Tw. This reduces tool wear during the production of the pinion by stamping. Fig.19A +B, Fig. 20B and Fig.21A +B (dashed line) shows the formation of the unnecessary non-loaded tooth side Fn in the wide tooth Tw' (see Fig.18A +B) also reduces the forming forces when producing the wide teeth Tw' by means of introducing the embossing Di to form the protrusions Dp.

[0306] In order to further improve the Fig.19A +B, Fig. 20B and Fig.21A The lateral stiffness of the wide tooth Tw' shown in +B (dashed line) can be similar to that of the above Fig.18C As described, reinforcing ribs are introduced into the embossing Di, for example in the form of a counter-embossing Ec.

Claims

1. A multi-layer pinion arrangement (Ap) for being mounted on a bicycle rear wheel transmission (Dd) in a manner for transmitting torque to a bicycle rear wheel axle (Ar), the transmission having a toothing transmission profile (Pd) arranged on the outer periphery of the transmission (Dd), the pinion arrangement (Ap) comprising a plurality of pinion devices, each of which has at least one pinion, including an inner final pinion device (Pti), a first pinion gear set (Sc1) connectable to the inner final pinion device (Pti) in a connection area (Ca) of the inner final pinion device (Pti), and an outer final pinion device (Pto), Features A rotary bearing device (Db) is used to support the first pinion gear set (Sc1) rotatably on the outside relative to the transmission device (Dd).

2. The multi-layer pinion arrangement (Ap) according to claim 1, It is characterized in that The bearing device (Db) is formed by a spacer unit, which is suitable for determining the relative distance (Da1, Da2, Da3) between at least two pinion devices of the pinion configuration (Ap) in the axial direction (Da) of the rear wheel shaft when the pinion configuration (Ap) is installed on the transmission device (Dd).

3. The multi-layer pinion arrangement (Ap) according to claim 1 or 2, It is characterized in that The bearing device (Db) is suitable for transmitting the installation tension force between at least two pinion devices of the pinion configuration (Ap) along the axial direction (Da) of the rear wheel axle, wherein when the pinion configuration (Ap) is mounted on the transmission device (Dd), the installation tension force is part of the closed force flow (Ff) extending through the transmission device (Dd) and the pinion configuration (Ap) substantially parallel to the rear wheel axle.

4. The multi-layer pinion arrangement (Ap) according to claim 3, It is characterized in that The bearing device (Db) is suitable for determining the relative distance (Da1) between the inner final pinion device (Pti) and the outer final pinion device (Pto) in the axial direction (Da) of the rear wheel shaft, and is suitable for transmitting the installation tension force between the inner final pinion device (Pti) and the outer final pinion device (Pto).

5. The multi-layer pinion arrangement (Ap) according to claim 2, It is characterized in that The bearing device (Db) is suitable for determining a relative distance (Da2) between the inner final pinion device (Pti) and the outer pinion (Z7, Z9) of the first pinion gear set (Sc1) in the axial direction (Da) of the rear wheel shaft.

6. The multi-layer pinion arrangement (Ap) according to claim 5, It is characterized in that The bearing device (Db) is suitable for determining the relative distance (Da1, Da2, Da3) in the axial direction (Da) of the rear wheel shaft, and is suitable for transmitting the installation tension force between the inner final pinion device (Pti) and the outer final pinion device (Pto) and the outer pinion (Z7, Z9) of the first pinion gear set (Sc1) along the axial direction (Da) of the rear wheel shaft.

7. The multi-layer pinion arrangement (Ap) according to claim 1 or 2, It is characterized in that The bearing device (Db) is made of non-metallic material.

8. The multi-layer pinion arrangement (Ap) according to claim 1 or 2, It is characterized in that The outer final pinion gear arrangement (Pto) comprises another pinion gear set (Sc2).

9. The multi-layer pinion arrangement (Ap) according to claim 8, It is characterized in that The further pinion gear set (Sc2) is constructed as a substantially integrally formed module.

10. The multi-layer pinion arrangement (Ap) according to claim 8, It is characterized in that The further pinion set (Sc2) has an engagement contour (Pe) on its inner circumference which meshes with the transmission contour (Pd) of the transmission device (Dd) in a form-fitting manner in a torque-transmitting manner.

11. The multi-layer pinion arrangement (Ap) according to claim 8, Features A screw plug device (Sd) suitable for engaging with the outer internal thread (Ti) of the transmission device (Dd), wherein the screw plug device (Sd) is suitable for pressing the other pinion set (Sc2) onto the transmission device (Dd) along the axial direction (Da) of the rear wheel shaft relative to the bearing device (Db), thereby forming a closed force flow (Ff) extending through the transmission device (Dd) and the pinion configuration (Ap) substantially parallel to the rear wheel shaft to connect the pinion configuration (Ap) with the transmission device (Dd).

12. The multi-layer pinion arrangement (Ap) according to claim 8, It is characterized in that The further pinion set (Sc2) comprises at least one pinion whose root circle diameter (Dt) is smaller than the outer diameter (Do) of the transmission (Dd) in the region of the transmission profile (Pd).

13. The multi-layer pinion arrangement (Ap) according to claim 8, It is characterized in that The other pinion set (Sc2) includes at least one pinion, whose pinion center plane (Pc11, Pc12) extends outwardly outside the axial end face (Fe) of the transmission device (Dd) when the pinion configuration (Ap) is mounted on the transmission device (Dd).

14. The multi-layer pinion arrangement (Ap) according to claim 1 or 2, It is characterized in that The pinion configuration (Ap) has three axial sections (Pa1, Pa2, Pa3) spaced apart from each other in the axial direction (Da) of the rear wheel shaft when mounted on the transmission device (Dd), and each of the axial sections has a meshing profile (Pe) on the inner circumference that meshes with the transmission profile (Pd) of the transmission device (Dd) in a shape-fitting manner to transmit torque.

15. The multi-layer pinion arrangement (Ap) according to claim 14, It is characterized in that Another pinion gear device (Pi) is arranged between the first pinion gear set (Sc1) and the other pinion gear set (Sc2) along the axial direction (Da) of the rear wheel shaft, and the other pinion gear device has an engagement profile (Pe) on the inner circumference that meshes with the transmission profile (Pd) of the transmission device (Dd) in a shape-fitting manner to transmit torque.

16. The multi-layer pinion arrangement (Ap) according to claim 1 or 2, It is characterized in that The teeth of at least one even-numbered pinion (Z3) of the pinion arrangement (Ap) correspond alternately to a narrow tooth set (Gtn) or a wide tooth set (Gtw) in the circumferential direction, wherein the teeth of the narrow tooth set are narrow teeth (Tn) whose width is smaller than an inner link plate intermediate gap (Wci) of an inner link plate link (Li) of a bicycle chain (Cn) corresponding to the pinion arrangement (Ap), and wherein the wide tooth set includes at least one wide tooth (Tw) whose width is larger than an inner link plate intermediate gap (Wci) of an inner link plate link (Li) of the bicycle chain (Cn) and smaller than an outer link plate intermediate gap (Wco) of an outer link plate link (Lo).

17. The multi-layer pinion arrangement (Ap) according to claim 16, It is characterized in that At least one pinion of the pinion arrangement (Ap) has, in the area of ​​at least one outer shift channel (Co) and / or in an area adjacent to the at least one outer shift channel (Co), at least one stabilizing tooth corresponding to the narrow tooth set (Gtn) and / or at least one stabilizing tooth corresponding to the wide tooth set (Gtw), the inner chain guiding surface of the stabilizing tooth protruding in the inner direction relative to the inner chain guiding surface of the widest tooth (Tn0, Tw0) of the same tooth set (Gtn, Gtw), so that when the chain (Cn) runs on the pinion, the chain is deflected inwardly by the inner chain guiding surface of the at least one stabilizing tooth protruding inwardly.

18. The multi-layer pinion arrangement (Ap) according to claim 16, It is characterized in that At least one pinion of the pinion arrangement (Ap) has, in the region of an inner shift channel (Ci) adjacent to the outer shift channel (Co), at least one stabilizing tooth corresponding to the narrow tooth set (Gtn) and / or at least one stabilizing tooth corresponding to the wide tooth set (Gtw), the inner chain guiding surface of the stabilizing tooth protruding in the inner direction relative to the inner chain guiding surface of the widest tooth (Tn0, Tw0) of the same tooth set (Gtn, Gtw), so that when the chain (Cn) runs on the pinion, the chain is deflected inwardly by the inner chain guiding surface of the at least one stabilizing tooth protruding inwardly.

19. A multi-layer pinion arrangement (Ap) for being mounted on a bicycle rear wheel transmission (Dd) in a manner for transmitting torque to a bicycle rear wheel axle (Ar), the transmission having a toothing transmission profile (Pd) arranged on the outer periphery of the transmission (Dd), the pinion arrangement (Ap) comprising a plurality of pinion devices, each of which has at least one pinion, including an inner final pinion device (Pti), a first pinion gear set (Sc1) connectable to the inner final pinion device (Pti) in a connection area (Ca) of the inner final pinion device (Pti), and an outer final pinion device (Pto), It is characterized in that The teeth of at least one even-numbered pinion (Z3) of the pinion arrangement (Ap) correspond alternately to a narrow tooth set (Gtn) or a wide tooth set (Gtw) in the circumferential direction, wherein the teeth of the narrow tooth set are narrow teeth (Tn) whose width is smaller than an inner link plate intermediate gap (Wci) of an inner link plate link (Li) of a bicycle chain (Cn) corresponding to the pinion arrangement (Ap), and wherein the wide tooth set includes at least one wide tooth (Tw) whose width is larger than an inner link plate intermediate gap (Wci) of an inner link plate link (Li) of the bicycle chain (Cn) and smaller than an outer link plate intermediate gap (Wco) of an outer link plate link (Lo).

20. The multi-layer pinion arrangement (Ap) according to claim 19, It is characterized in that At least one pinion of the pinion arrangement (Ap) has, in the area of ​​at least one outer shift channel (Co) and / or in an area adjacent to the at least one outer shift channel (Co), at least one stabilizing tooth corresponding to the narrow tooth set (Gtn) and / or at least one stabilizing tooth corresponding to the wide tooth set (Gtw), the inner chain guiding surface of the stabilizing tooth protruding in the inner direction relative to the inner chain guiding surface of the widest tooth (Tn0, Tw0) of the same tooth set (Gtn, Gtw), so that when the chain (Cn) runs on the pinion, the chain is deflected inwardly by the inner chain guiding surface of the at least one stabilizing tooth protruding inwardly.

21. The multi-layer pinion arrangement (Ap) according to claim 19, It is characterized in that At least one pinion of the pinion arrangement (Ap) has, in the region of an inner shift channel (Ci) adjacent to the outer shift channel (Co), at least one stabilizing tooth corresponding to the narrow tooth set (Gtn) and / or at least one stabilizing tooth corresponding to the wide tooth set (Gtw), the inner chain guiding surface of the stabilizing tooth protruding in the inner direction relative to the inner chain guiding surface of the widest tooth (Tn0, Tw0) of the same tooth set (Gtn, Gtw), so that when the chain (Cn) runs on the pinion, the chain is deflected inwardly by the inner chain guiding surface of the at least one stabilizing tooth protruding inwardly.

22. A modular system for forming a multi-layer pinion arrangement (Ap) according to any one of claims 1 to 21, The modular system comprises at least three modularly replaceable components (B1), component (B2) and component (B3), component (B1) being formed by the inner final pinion gear arrangement (Pti), component (B2) being formed by the first pinion gear set (Sc1), and component (B3) being formed by the outer final pinion gear arrangement (Pto), wherein at least one component can correspond to a component series comprising at least two members and can be replaced by another member of the component series, for example made of a different material or having a different manufacturing quality, while retaining the remaining components, Features A rotating bearing device (Db) for rotatably supporting the first pinion gear set (Sc1) on the outside relative to the transmission device (Dd), wherein the bearing device (Db) is formed by a spacing unit, the spacing unit is suitable for determining the relative distances (Da1, Da2, Da3) on the axial direction (Da) of the rear wheel axle when the multi-layer pinion configuration (Ap) is installed on the transmission device (Dd), and is suitable for transmitting the installation tension between the component (B1), the component (B2) and the component (B3) along the axial direction (Da) of the rear wheel axle.

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