Bicycle derailleur and method for mounting a bicycle derailleur

Abstract

The invention relates to a rear derailleur (20) for a bicycle gear system comprising: - a base element (26) that can be attached to a bicycle frame (10); and - a movable element (28) coupled to the base element (26) via a pivoting mechanism (30) and pivotally displaceable relative to it, wherein the pivoting mechanism (30) is pivotally displaceable both relative to the movable element (28) and relative to the base element (26). For easier adjustment of the chain tension, the rear derailleur includes a locking device (80, 102) configured to fix the movable element (28) at least temporarily relative to the base element (26), wherein the locking device (80, 102) is designed such that the pivoting mechanism (30) can be temporarily fixed in at least one predetermined locking position via a direct coupling relative to the base element (26) or relative to the movable element (28).

Description

[0001] The present invention relates to a rear derailleur for a bicycle gear system comprising: - a base element that can be attached to a bicycle frame; and - a movable element coupled to the base element via a pivoting mechanism and pivotally displaceable relative thereto, wherein the pivoting mechanism is pivotally movable relative to both the movable element and the base element.

[0002] The present invention further relates to a method for assembling and adjusting such a derailleur.

[0003] Conventional rear derailleurs have long been attached to the right dropout of the frame using a derailleur hanger. The derailleur hanger is secured to the frame at one end coaxially with the rear wheel axle and at the other end coaxially with the B-axis of the derailleur base element (B-knuckle). The distance between the geometric axis A of the rear wheel axle and the B-axis of the base element is bridged by the derailleur hanger. When mounted to the frame, the base element can be rotated about the B-axis relative to the derailleur hanger. Forward rotation of the derailleur is limited – counterclockwise (CW) – by the B-screws. Rearward rotation of the derailleur (CW) is counteracted by the chain tension.

[0004] The following should be considered regarding the technical background of rear derailleurs: Sprocket sets have a gear spread of 500 percent or more. Such gear spreads can be achieved with a smallest sprocket having 9, 10, or 11 teeth and a largest sprocket having 50, 51, 52 teeth, or more. To accommodate the increased number of sprockets with the rear derailleur, the derailleur dimensions are increased.

[0005] In the prior art, rear derailleurs with tilted pivot mechanisms (inclined parallelograms) were often used. Such derailleurs can cause sudden vertical loads, such as those encountered when riding off-road, to jerk the pivot mechanism and thus lead to unwanted shifting (so-called "ghost shifting"). To engage the widely varying sized sprockets of modern sprocket cassettes, the inclined parallelogram would have to be tilted even further and / or the derailleur dimensions would have to be further increased. Both of these would further increase the susceptibility to unwanted shifting.

[0006] The distance between the upper chain roller of a rear derailleur and the pinion below which the chain roller is positioned is referred to as the B-gap or chain gap. When developing a derailleur, the goal is generally to achieve the most constant B-gap curve possible. This constant B-gap curve, or the resulting B-gap curve, results from the interaction of various geometric parameters such as the parallelogram geometry (pivot mechanism), the distance of the parallelogram from the rear wheel axle A, the angle of the parallelogram to the axle-bottom bracket axis connection plane (B-angle), the distance of the P-knuckle axis (P-axis) from the parallelogram, the cage geometry, the size of the chain rollers, the gear range of the sprocket cassette, etc.

[0007] It has been shown that a precise initial adjustment of the B-gap has a particularly strong influence on robustness and shifting performance. Using conventional methods, an ideal B-gap adjustment is often difficult and requires complex and expert installation. The main problems here are the lack of a reference for precise adjustment and the adjustment process, which is too complex for less experienced users without assembly experience. The use of B-gap templates is helpful, but often leads to suboptimal results due to application errors.

[0008] This problem has recently been addressed in a particularly advantageous way by designing the rear derailleur, which is mounted coaxially with the rear wheel axle on the bicycle frame. A coaxial derailleur connection with an adjustable stop element allows for a defined locking position between the chain guide assembly (cage) and the movable element (P-knuckle), enabling simple, quick, and very precise adjustment of the B-gap.

[0009] Although this has brought significant advantages in terms of the simplicity and reliability of rear derailleur installation and adjustment, a further problem has arisen in practice. There is a difference in adjustment and operation between bicycles in different categories, namely bicycles with frames where the rear wheel is unsprung (so-called hardtails) and bicycles with frames with rear wheel suspension (so-called full suspension bikes). On bicycles with frames that provide rear wheel suspension, where the rear wheel is mounted on a suspended rear triangle, the rear triangle geometry changes during compression, with corresponding effects on the B-gap, due in part to changes in the length of the chainstays and changes in the B-angle. For this reason, the B-gap has previously had to be adjusted in the so-called sag position of the suspension. In this sag position, the rear triangle is fully compressed.To achieve this level of compression, the rear end must be subjected to sufficient load during installation and adjustment of the chain tension. This requires two people or other means for the adjustment. For example, the air in the shock must be released, the shock must be removed, or it must be compressed using tools such as a tensioning strap.

[0010] Newer mechanical derailleurs that dispense with the derailleur hanger, i.e., derailleurs specifically designed for coaxial mounting on the rear wheel axle of a bicycle frame, are known from documents EP 0 875 444 A1, EP 1 342 658 A1, and EP 1 764 297 A1. The separate derailleur hanger is omitted; the B-axis of the base element runs along the rear wheel axle A, i.e., coaxial with the rear wheel axle A. Document DE 10 2018 001 253 A1 describes a rear derailleur with a special design for coaxial mounting on the rear frame eyelet. In this context, reference is also made to document DE 10 2022 115 599 A1 for technical background.

[0011] Document DE 10 2018 208 053 ​​A1 describes a rear derailleur with an integrated indicator or marking on the chain guide. The marking on the derailleur functions like a B-gap template, with the advantage that no additional parts are required. The marking indicates the correct distance of the upper chain roller relative to the outer circumference of the largest pinion in a multiple pinion arrangement (B-gap). The disadvantage of this design, however, is that the marking only indicates a single adjustment position of the derailleur relative to the multiple pinion arrangement. This means that, regardless of the bike category (hardtail or full suspension), the derailleur is always adjusted to the same adjustment position. There is no option to vary the adjustment position depending on the bike category. Accordingly, full-suspension bikes can currently only be adjusted in the sag position—i.e., fully compressed.

[0012] Document DE 10 2021 003 745 A1 describes a rear derailleur of the type described above with an electromechanical drive. This device provides for a chain guide arrangement to be temporarily fixed relative to the base element via a locking device. Furthermore, the electromechanically driven rear derailleur can be moved into a predetermined switching position for assembly via the drive and the associated gearing and can be temporarily held in this position. This makes it possible to mount and adjust the rear derailleur in a predetermined position on the frame. In certain embodiments, this locking device can be moved into various locking positions. The special feature of this solution is that the locking device always engages between the base element and the chain guide arrangement, and in particular, on a chain guide plate of the cage of the chain guide arrangement.This leaves the locking mechanism relatively exposed, which can be disadvantageous during operation. The derailleur is locked via the electromechanical drive.

[0013] A comparable blocking device is also described in various embodiments in document DE 10 2011 118 912 A1. Here, too, it is provided to fix the chain guide arrangement relative to the movable element in predetermined blocking positions.

[0014] Document DE 10 2020 209 370 A1 describes a rear derailleur with an integrated damper assembly. The damper assembly acts between the movable element of the derailleur and the chain guide assembly to dampen movements or vibrations of the chain guide assembly relative to the movable element.

[0015] It is an object of the present invention to provide a rear derailleur of the type described above and a method for assembling and adjusting the same, in which the blocking device is better integrated and less exposed than the solutions from the prior art.

[0016] This task is solved by a rear derailleur for a bicycle gear system, which includes: - a base element that can be attached to a bicycle frame; and a movable element that is coupled to the base element via a pivoting mechanism and is pivotally displaceable relative thereto, wherein the pivoting mechanism is pivotally movable both relative to the movable element and relative to the base element. Furthermore, according to the invention, a blocking device is provided that is designed to at least temporarily fix the movable element relative to the base element, wherein the blocking device is designed such that the pivoting mechanism can be temporarily fixed in at least one predetermined blocking position via a direct coupling relative to the base element or relative to the movable element.

[0017] In contrast to the prior art, the blocking device is designed such that it acts directly on the pivoting mechanism and fixes it relative to the base element or relative to the movable element via a direct coupling between two of these components. According to the invention, the pivoting mechanism is formed between the base element and the movable element. Blocking the pivoting mechanism relative to the base element or to the movable element via a direct coupling ensures that the derailleur is securely and temporarily fixed in a predetermined position or assembly position. It is entirely sufficient if one of the pivot joints between a component of the pivoting mechanism and either the base element or the movable element is directly blocked against pivoting movement, i.e. via the direct coupling. The entire pivoting mechanism and thus the derailleur is then fixed in a desired blocking position.This is particularly advantageous for purely mechanical derailleurs, as it allows the derailleur to be temporarily locked in a desired mounting position against the action of a preload spring. The integrated design of the base element, pivoting mechanism, and movable element allows the locking device to be designed simply, unobtrusively, and less exposed than with prior art solutions. This has advantages in terms of avoiding possible impairment by external influences (stone chips, dirt, etc.) as well as in terms of preventing unintentional activation of the locking device. This becomes particularly clear when considering the specific developments described below, which merely represent exemplary embodiments.

[0018] According to one embodiment of the invention, the pivoting mechanism comprises at least two pivot arms, a first pivot arm being pivotably connected to the base element with its first end section and pivotably connected to the movable element with its second end section, and a second pivot arm being pivotably connected to the base element with its first end section and pivotably connected to the movable element with its second end section. With such a configuration of the pivoting mechanism as a parallelogram gear, it is sufficient, as already indicated above, if only one of the pivot arms is blocked relative to the base element or relative to the movable element. As a result, the entire parallelogram gear, i.e. the entire pivoting mechanism of the switching mechanism, is blocked in a predetermined position.

[0019] According to one embodiment variant of the invention, it can be provided that the base element and / or the movable element has a first receiving opening and that the pivoting mechanism has a second receiving opening on a component, wherein the first and second receiving openings are aligned with one another in at least one predetermined relative position of the movable element relative to the base element such that in the event of at least partial alignment of the first and second receiving openings, a blocking body can be introduced into them to produce the direct coupling in order to block a pivoting movement of the movable element relative to the base element via the pivoting mechanism.

[0020] This design variant allows for a particularly simple design of the locking device. Simply by providing two receiving openings that can be aligned so that a locking element can be inserted into them, the rear derailleur can be locked without great technical effort and even with a certain weight advantage. The locking element can be a metal or plastic pin or a tool, such as a screwdriver, a hex key, or the like. The locking element can be left in the two receiving openings as long as locking is required for assembly and adjustment of the rear derailleur. The locking element can then be removed simply by pulling it out of the receiving openings.

[0021] With regard to the above-mentioned embodiment, this means that the base element and / or the movable element have a first receiving opening and that the first pivot arm and / or the second pivot arm have a second receiving opening, wherein the first and second receiving openings are aligned with one another in at least one predetermined relative position of the movable element relative to the base element such that, in the event of at least partial alignment of the first and second receiving openings, a blocking body can be introduced into them to establish the direct coupling in order to block a pivoting movement of the movable element relative to the base element via the pivoting mechanism.

[0022] Furthermore, in this context, it can be provided that at least one of the first and second receiving openings is formed with a rotation-proof receiving profile, in particular with a hexagonal profile. This makes it possible to define a predetermined blocking position by specifically designing the profiled receiving opening in its profile or diameter to fit a specific blocking body.

[0023] Furthermore, an embodiment variant of the invention provides that by providing at least two differently dimensioned blocking bodies which can be attached to the at least partially aligned first and second receiving openings to establish the direct coupling, the rear derailleur can be temporarily fixed in at least two predetermined blocking positions.

[0024] Assuming a technician uses the specially designed blocking element with a predetermined profile and diameter, this ensures that the derailleur is locked in the desired locking position, for example, a specific orientation relative to a sprocket cassette, such as the 6th or 7th sprocket of the cassette. This ensures a predetermined orientation of the derailleur for installation and chain tension adjustment.Furthermore, it can be provided that, for example, by using a hex key matched to the hex profile and by using a predetermined additional hex key of a smaller size, two locking positions can be predefined. These locking positions take into account the problem described above, according to which the appropriate locking position is selected according to the respective bicycle category (hardtail or full suspension with rear wheel suspension), namely by using the respective hex key of a predetermined size. Again, a reliable specification of the locking position can be ensured using simple means simply by appropriately designing the receiving openings, in particular the profiled receiving opening.

[0025] According to one embodiment of the invention, the derailleur can be designed as a cable-operated, purely mechanical derailleur, with at least one of the pivot arms being designed with a cantilever arm or as a cantilever arm for attaching a cable pull, with the cantilever arm preferably being designed with the second receiving opening. This measure allows one of the receiving openings to be realized particularly advantageously, with few parts, and while achieving a weight saving.

[0026] Furthermore, as an alternative, the derailleur can be designed as a motor-operated derailleur, with the drive motor and a drive gear associated therewith being arranged at least partially on the base element. Even though a motor-operated derailleur can generally be moved into any predetermined position and held therein by appropriately controlling the motor or drive mechanism, it may be advantageous to also assign a locking device of the type described above to these derailleurs in order to temporarily and securely fix the derailleur in the desired mounting position.

[0027] An alternative embodiment of the invention can consist in the blocking device having a blocking pin that is attached to one of the components: base element, first pivot arm, second pivot arm, or movable element, and that directly couples the base element or the movable element to the second pivot arm to prevent pivoting movement in order to temporarily fix the derailleur in the at least one blocking position. Unlike what was described above, this embodiment of the invention provides that no additional blocking body is required. The blocking device is operated by actuating the blocking pin. With regard to the design of the blocking device itself, this largely corresponds to the solution according to document DE 10 2021 003 745 A1, wherein, as already stated at the beginning, the blocking device is provided exposed between the movable element and the chain guide arrangement.This prior art locking device serves a completely different purpose than the locking device of the present invention. According to the present invention, the locking device comprising the locking pin is provided in the region of the pivot mechanism for direct coupling to the base element or the elastic element and is integrated into the rear derailleur to position it relative to a reference pinion.

[0028] In connection with this blocking device comprising a blocking pin, a further development of the invention provides that the blocking pin is spring-loaded into a non-blocking passive position and / or can be locked in this position. If necessary, a detent, such as a locking lug interacting with a recess or the like, can be provided for locking. This allows the blocking pin to be locked in its passive position to prevent it from undesirably blocking the derailleur during operation due to external influences or incorrect operation.

[0029] Furthermore, in this context, it can be provided that the locking pin has a cross-sectional profile that deviates from a circle and / or is mounted eccentrically, so that it can be mounted in at least two different relative positions relative to one of the components of the base element or first pivot arm or second pivot arm or movable element in order to achieve at least two different locking positions. This allows the locking pin to be placed in various locking positions. This again addresses the problem that different locking positions relative to the sprocket cassette are required for mounting the rear derailleur, depending on the bicycle category (hardtail or full-suspension).

[0030] According to one embodiment of the invention, it can be provided that, to establish the direct coupling, a pivotable, preferably spring-biased, blocking body is arranged around one of the pivot axes of the pivot mechanism, wherein said blocking body is pivotable, preferably by overcoming the spring preload, between a passive position and at least one blocking position about the associated pivot axis, wherein in the passive position the blocking body permits the relative movement between the base element and the movable element via the pivot mechanism, and wherein in the at least one blocking position the blocking body provides a direct coupling between the base element or the movable element and the pivot mechanism. This embodiment allows the blocking body to be permanently integrated into the switching mechanism and to be pivoted back and forth between the passive position and the blocking position as required.

[0031] A further development of the invention relates to a rear derailleur of the type described above with a chain guide arrangement which is coupled to the movable element and is pivotable relative thereto about a pivot axis, and a pretensioning device with which the chain guide arrangement is pretensioned relative to the movable element about the pivot axis into an initial position, wherein the chain guide arrangement is pivotable against a tensioning force of the pretensioning device from the initial position about the pivot axis into various operating positions.

[0032] It can further be provided that the chain guide arrangement is combined with the pretensioning device to form a single assembly which can be attached to the movable element via a detachable connection, preferably a threaded connection. This design of the chain guide arrangement together with the pretensioning device to form a single assembly enables a modular design of the rear derailleur. A further advantage is that in the event of a defect in the chain guide arrangement or the pretensioning device, the entire rear derailleur does not have to be replaced, but rather only the assembly can be replaced. It is precisely these components that are regularly subject to defects due to external influences or impacts. Coupling this assembly to the movable element via a detachable connection, in particular a threaded connection, allows for particularly simple and tool-free assembly.This means that the assembly can be quickly changed during a bike ride off-road if necessary.

[0033] The invention further relates to a rear derailleur of the type described at the outset or above, wherein the pretensioning device has a damping arrangement designed to counteract a damping effect of a relative movement between the movable element and the chain guide arrangement, wherein the damping arrangement comprises a coupling device via which the damping arrangement is coupled to a rotary shaft and a support, wherein the coupling device has a damping spring which is supported on the one hand on the rotary shaft and on the other hand on an insert part coupled or coupleable to the movable element and which exerts its damping effect between them via a frictional engagement, preferably in the radial direction. It should be noted that the damping arrangement according to the type mentioned above and further specified below is also to be regarded as a separate aspect of the invention, independent of the blocking device.

[0034] According to a further development of the damping arrangement according to the invention, it can be provided that the damping spring is attached at one end to one of the components of the rotary shaft and the movable element in a rotationally fixed manner and is in direct or indirect frictional engagement with the other component of the rotary shaft and the movable element, preferably in radial frictional engagement, wherein the damping effect increases or decreases depending on the direction of the relative rotation.

[0035] For example, it is possible for the damping spring to be designed with a smaller inner diameter than a circumferential surface of a shaft section of the rotating shaft that interacts with it. During assembly, the damping spring is slightly expanded and spread onto this circumferential surface of the shaft section, so that it is subsequently in radial frictional engagement with this circumferential surface of the shaft section. If the damping spring is designed as a spiral spring with multiple coils, its tension state changes depending on the direction of relative rotation between the rotating shaft and the moving element. In one direction of rotation, the damping spring designed as a spiral spring tends to be more tightly tensioned, whereas in the opposite direction of relative rotation the damping spring tends to expand.This allows a greater or lesser damping effect to be achieved depending on the direction of the relative movement between the movable element and the chain guide assembly. This allows, for example, unwanted vibrations of the chain guide assembly in one direction relative to the movable element to be damped more effectively.

[0036] This structure also allows for a simple damping arrangement with advantageous properties regarding force transmission while requiring little installation space.

[0037] In this context, a further development provides that the damping spring has a maximum number of four turns, preferably a maximum number of three turns, and furthermore preferably a maximum number of two turns. Furthermore, in this context, the insert part can be made of metal, preferably steel. The damping spring can cooperate with a spacer ring.

[0038] Furthermore, with regard to the damping device, it can be provided that a first elastic force storage device is coupled to the chain guide assembly via the rotary shaft in order to exert the pretensioning force on the chain guide assembly via the rotary shaft.

[0039] Furthermore, it is possible for the rotary shaft to be rotatably mounted on a cover element by means of a rotary bearing, which, together with the rotary shaft extending through a through opening of the cover element, closes the receptacle of the movable element and is fastened to the movable element.

[0040] As already stated at the outset, the derailleur according to the present invention can be designed for coaxial mounting on a rear wheel axle of a bicycle, wherein the base element comprises a first connection end for coaxial mounting on the rear wheel axle and a second connection end for coupling to a pivoting mechanism. In this context, the invention can provide that the first connection end of the base element has a first arm and a second arm, which are arranged spaced apart from one another in the axial direction, wherein, when mounted on the frame, the first arm is located on an axial inner side of the frame and the second arm is located on an axial outer side of the frame.

[0041] Furthermore, it is possible for the second connecting end of the base element to have a first axle receptacle for a first pivot axis of the pivot mechanism and a second axle receptacle for a second pivot axis of the pivot mechanism, wherein the first axle receptacle and the second axle receptacle - and thus the respective pivot axes - are each oriented substantially orthogonally to the rear wheel axle.

[0042] If the switching mechanism comprises an electromechanical drive, it can be provided that this is arranged in the area of ​​the base element.

[0043] The invention further relates to methods for adjusting a bicycle drive comprising a rear derailleur of the type described above, a multiple chainwheel arrangement, a front chainring and a chain, wherein the rear derailleur is adjusted relative to the multiple chainwheel arrangement, comprising the following steps: a) Determine a bicycle category, in particular bDetermine whether the bicycle has an unsprung or sprung rear wheel on which the rear derailleur is to be mounted, b) Selecting a blocking device adapted to the specific bicycle category or selecting a blocking position of a blocking device adapted to the specific bicycle category, c) depending on the specific bicycle category, moving the rear derailleur against the action of the tension spring in alignment with a reference pinion, in particular with one of the middle pinions of the multiple sprocket arrangement, preferably with the sixth or seventh pinion of the sprocket cassette, such that the chain engages with the reference pinion and in particular such that the first receiving opening is aligned with the second receiving opening, d) Inserting or adjusting the blocking body into the active position so that it fixes the pivoting mechanism relative to the base element, e) Turn the derailleur backwards around the rear wheel axle until the desired chain tension is reached, f) Fixing the rear derailleur to the frame after reaching the desired chain tension, and removing the blocking body from the openings and / or moving the blocking body into its passive position.

[0044] By carrying out this method with the rear derailleur according to the invention, an exact alignment of the rear derailleur relative to the sprocket cassette and the achievement of the desired chain tension are permanently guaranteed.

[0045] In the following, exemplary embodiments of the present invention are explained with reference to the accompanying figures. They depict: Fig. 1 a schematic partial representation of a rear wheel arrangement with a schematically represented rear derailleur; Fig. 2 is a side view of a first embodiment of a rear derailleur according to the invention viewed from the left side of the bicycle; Fig. 3 is a side view of the first embodiment of the rear derailleur according to the invention viewed from the right side of the bicycle; Fig. 4 a perspective view of the rear derailleur according to Fig. 2 and Fig. 3 viewed from behind; Fig. 5 a perspective view of the rear derailleur according to Fig. 2 and Fig. 3 viewed from the front; Fig. 6 a perspective view of the rear derailleur according to Fig. 2 and Fig. 3 viewed from below; Fig. 7 a perspective view of the rear derailleur according to Fig. 2 and Fig. 3 viewed from above; Fig. 8 an exploded view showing the individual components of the rear derailleur according to Fig. 2 to 7; Fig. 9 shows a representation of a component of the base element and a component of the pivoting mechanism to explain a first embodiment of the blocking device; Fig. 10 - 12 different representations of the functionality of the first embodiment of the blocking device; Fig. 13 and Fig. 14Representations of a second embodiment of the blocking device according to the invention; Fig. 15 and Fig. 16Representations of a third embodiment of the blocking device according to the invention; Fig. 17 a further schematic partial representation of a rear wheel arrangement with a schematically represented rear derailleur; Fig. 18 - 22 representations of a fourth embodiment of the blocking device according to the invention; Fig. 23 is a view of an assembly comprising a preload device, a damping arrangement and a chain guide arrangement which can be mounted separately on the rear derailleur; Fig. 24 is a partially exploded view of components for explaining a damping device according to the invention; Fig. 25 a sectional view through the damping device according to the invention; and Fig. 26 a flowchart for explaining the method according to the invention. Detailed description of the preferred embodiments

[0046] In the following, directional terms are used, namely "front / rear", "outside / inside", "top / bottom" and "left / right", which refer to a bicycle that is aligned and used in the direction of travel. A bicycle frame 10 has a left and a right rear dropout 12, 14, between which a rear wheel (not shown here) is mounted with a hub 16, on which a sprocket cassette 18 is attached for drive coupling. The rear wheel rotates together with the sprocket cassette 18 about the rear wheel axis A. The sprocket cassette 18 is shown schematically and rotates about the rear wheel axis A. Such a sprocket cassette 18 can, for example, comprise twelve sprockets, the smallest sprocket having ten teeth and the largest sprocket having 52 teeth.

[0047] Also visible is a rear derailleur 20 mounted on the right dropout 12. The rear derailleur 20 is mounted coaxially with the rear wheel axle A and extends such that it is attached to the axle eye 24 of the bicycle frame 10 via a mounting assembly 22. The rear derailleur 20 includes a multi-part base member 26, a movable member 28, and a pivoting mechanism 30 disposed therebetween. A chain guide assembly 32, which includes two guide rollers 34 and 36, is pivotally mounted on the movable member 28.

[0048] For shifting, the movable element 28 can be pivoted relative to the base element 26 via the pivot mechanism 32 transversely to the longitudinal axis of the frame. When shifting from a larger pinion to a smaller pinion, the rear derailleur 20 moves a partially shown chain 40 axially outward (outboard). When shifting from a smaller pinion to a larger pinion, the rear derailleur 20 moves the chain 40 axially inward (inboard). Axial refers to the rear wheel axis A or the rotational axis A of the pinion cassette 18; the pinion with the largest diameter is located axially further inward than the smaller pinions. The teeth are arranged radially on the outside of the pinions. The chain 40 runs through the chain guide arrangement 32 in an S-shape and engages with the teeth of the upper guide roller 34 and the teeth of the pinion cassette 18 (not shown here).

[0049] The Fig. The bicycle drive shown in Figure 1 comprises a front single chain wheel (not shown here), the pinion cassette 18, the chain 40, and the rear derailleur 20. Shifting commands are sent mechanically or electronically to the derailleur 20 from a handlebar-mounted switch (not shown here). The transmission of the shifting commands from the switch to the derailleur 20 can be wireless or wired.

[0050] Fig. 2 shows only the rear derailleur 20 in the external view, Fig. Figure 3 shows the rear derailleur 20 in an internal view. The coaxial mounting of the rear derailleur 10 by means of bolts 22 along the rear wheel axis A or the B axis of the base element 26 eliminates the need for a derailleur hanger, as is commonly used in the prior art.

[0051] The chain guide assembly 32 is rotatably connected to the movable element 28 about the pivot axis 42 (P-axis) and is biased rearwardly in a clockwise direction so that the chain is tensioned against the effect of this preload. The chain guide assembly 32 comprises the upper and lower guide rollers 34, 36, which are each rotatably mounted between two cage plates 44, 46. The upper guide roller 34 is rotatably arranged at an upper distance from the axis 42. The lower guide roller 36 is rotatably arranged at a lower distance from the P-axis 42, with the upper guide roller 34 being arranged at a smaller distance from the P-axis 42 than the lower guide roller 36.

[0052] This design variant features an optional locking device 48 (flip chip), which can be provided to secure the preloaded chain guide assembly 32 relative to the movable element 28. This allows the rear derailleur 20 to be mounted and adjusted without the chain guide assembly 32 snapping backward due to the preload. This is not absolutely necessary for adjusting the chain tension, but can be helpful, especially during assembly. For details of this optional locking device 48, reference is made to the disclosure of document DE 10 2021 003 745 A1.

[0053] The rear derailleur 20 includes a multi-part base member 20, a movable member 40, a chain guide assembly 90, and a pivot mechanism 30 connecting the base member 20 to the movable member 40.

[0054] If we now turn to the perspective views according to the Fig. 4 to 7, it can be seen that the base element 26 is fork-shaped in its upper region for attachment to the bicycle frame, also referred to as a B-knuckle. It has an inner fork section 50 and an outer fork section 52. The inner fork section 50 engages with the rear dropout 12 on the inside of the frame, whereas the outer fork section 52 engages with the rear dropout 12 on the outside of the frame. Also visible is the screwed-in fastening bolt of the fastening arrangement 22, which has various sleeve and positioning components 22a, 22b and 22c. The two fork sections 50 and 52 are not made of solid material, but have various struts and recesses to save weight and increase stiffness. The two fork sections 50, 52 are also screwed to a connecting body 54 of the base element 26 on both sides. Screw elements 56, 58, 60, 62 are provided for this purpose.The connecting body 54 serves to support the pivoting mechanism 30.

[0055] Turning now to the pivot mechanism 30, it can be seen that it has two pivot arms 64, 66. The pivot arms 64, 66 are also constructed in multiple parts. The pivot arm 64, which is arranged on the inside, has two components 64a and 64b, which are connected to one another in the assembled state by two fastening screws 68 and 70. The pivot arm 66 has two components 66a and 66b, which in turn are screwed together by two fastening screws 72, 74. Component 66b is also designed for attaching an actuating cable (not shown) by means of a fastening screw 76 and a clamping plate 78. It can be seen that component 66b is essentially triangular in shape for cable routing and has a polygonal opening 80. This will be discussed further below.

[0056] The movable element 28 can also be seen. The connecting body 54 of the base element 26, the two pivot arms 64 and 66, and the movable element 28 each have bearing openings into which connecting axes 82, 84, 86, 88 can be inserted and partially fixed. This allows the pivoting mechanism 30 to be assembled into a parallelogram gear. This makes it possible to pivot the movable element 28 via the pivoting mechanism 30 when the base element 26 is stationary relative to the frame and thus when the connecting body 54 is correspondingly stationary relative to the frame. The pivoting occurs against the spring action of a tension spring 90, which is suspended from the two connecting axes 82 and 88 and held under pretension in every position.This tension spring 90 provides spring preload in the rear derailleur 20 such that the chain guide assembly 32 is preloaded outwardly, allowing it to align itself with the smallest sprocket of the sprocket cassette 18 while fully released. Each inward shift, i.e., toward a next larger sprocket, occurs against the increasing preload of the tension spring 90.

[0057] Provided on the movable element 28 is an approximately circular-cylindrical receiving housing section 92, which is largely hollow in its interior. This receives a pretensioning device 94 with an integrated damping device 96 formed on the chain guide assembly 32. Via this pretensioning device 94 with integrated damping device 96, the chain guide assembly 32 is rotatably received about the axis 42 in the receiving housing section 92 and attached to the movable element 28. It should be noted that the pretensioning device 94 ensures that the chain guide assembly 32, with its lower guide roller 36, is pretensioned rearward and swings rearward relative to the bicycle frame when released. This ensures the chain tension already mentioned above.

[0058] If you look at the exploded view according to Fig. 8, the additional components 98 and 100, which are attached to the base element 26, can also be seen. Component 98 serves as a cable guide. Component 100 is a side cover. Furthermore, the assembly comprising the chain guide arrangement 32, pretensioning device 94, and integrated damping device 96 can be pre-assembled as shown and screwed via an external thread 101 into an internal threaded section (not shown) in the receiving housing section 92. This allows for simple, tool-free assembly of the assembly on the movable part 28, if necessary for replacement in the event of damage.

[0059] Fig. Figure 9 shows, with regard to the blocking device according to the invention, the component 66b of the pivot arm 66 and the connecting body 54 of the base element 26. These two components are designed in such a way that they offer the possibility of blocking the switching mechanism in at least one predetermined blocking position. For this purpose, the connecting body has a hexagonal opening 102. The component 66b of the pivot arm 66 has, as already explained above, a polygonal opening 80. In the assembled state, the opening 80 can be aligned relative to the hexagonal opening 102 by pivoting the movable element 28 relative to the base element 26 via the pivot mechanism 30 and against the action of the tension spring 90 such that they are at least partially aligned or overlap. In this state, as shown in the Fig. 10 and Fig. 11, a hexagon wrench 104 is inserted through the opening 80 into the hexagon opening 102. If the movable element 28 is then released again, the hexagon wrench 104 inserted into the hexagon opening 102 comes into contact with the edge of the polygonal opening 80 and blocks any further spring-biased return movement of the movable element 28 relative to the base element 26 against the action of the tension spring 90. As a result, the rear derailleur 20 is fixed in a predetermined relative position between the base element 26 and the movable element 28 under spring preload of the tension spring 90. This predetermined relative position is defined in such a way that the chain tension can be optimally adjusted while the chain lies on a predetermined reference sprocket of the cassette 18.

[0060] The hexagon opening 102 is dimensioned such that it is matched to a specific hexagon wrench size. For example, a hexagon wrench of size HEX 5 can be inserted into it with a form-fitting fit. In this case, the rear derailleur 20 is designed, for example, for the installation and optimal adjustment of the chain tension on a bicycle without rear wheel suspension. If, however, the rear derailleur 20 is to be attached to a bicycle frame designed for a bicycle with rear wheel suspension, in which the rear end of the bicycle is designed to be spring-loaded, a different position is required. The rear derailleur 20 can be secured in this installation position by using a hexagon wrench of size HEX 4 instead of a hexagon wrench of size HEX 5. This wrench can be inserted into the hexagon opening 102 with some play.However, as soon as the rear derailleur moves to its initial position under the action of the tension spring 90, the size HEX 4 Allen key blocks the movement in the different, predetermined mounting position for this bicycle category. Thus, with one and the same hexagon opening 102, by using differently sized locking bodies, two different mounting positions can be achieved, i.e., relative to two different reference pinions, thus enabling the rear derailleur 20 to be mounted and the chain tension to be ideally adjusted on bicycles of different categories.

[0061] In an optional modification, it is possible to design the hexagon opening 102 in a stepped manner, specifically with a first opening section closer to the polygonal opening 80, which is matched to the dimensions of a hexagon wrench of size HEX 5, and with a second opening section further away from the polygonal opening 80, which is matched to the dimensions of a hexagon wrench of size HEX 4. This ensures even more reliably that the predetermined, defined mounting position is held securely and precisely, even when adjusting using the smaller hexagon wrench HEX 4.

[0062] After assembly and adjustment of the chain tension, the hexagon key used as a blocking body can then simply be removed from both overlapping openings.

[0063] The principle of blocking the rear derailleur 20 in two different mounting positions with two differently sized hexagon keys is shown in Fig. 11 and Fig. 12 is shown in more detail. It can be seen that both hex keys of different sizes are superimposed in the drawing for comparison. The size differences show that locking can be achieved in different mounting positions. Fig. Figure 12 shows this again in a different view, where both hexagon keys are shown superimposed and labeled HEX4 and HEX5.

[0064] In this embodiment of the invention, the adjustment of the chain tension on the rear derailleur 20 is carried out according to the following procedure, which also applies in Fig. 26 is shown in a flow chart: a) Step S1: Determine a bicycle category, e.g. Determine whether the bicycle is designed with an unsprung or sprung rear wheel on which the rear derailleur 20 is to be mounted b) Step S2: Selecting a locking body 104 adapted to the specific bicycle category in the form of a hexagon key of size HEX 4 or HEX 5, c) Step S3: depending on the specific bicycle category, moving the movable part of the rear derailleur 20 against the action of the preload spring 90 in alignment with a reference pinion, in particular with one of the middle pinions of the multiple sprocket arrangement, preferably in alignment with the 6th or 7th pinion of the sprocket cassette 18, so that the chain 40 engages with the reference pinion and such that the opening 102 is aligned with the opening 80, d) Step S4: Inserting the blocking body 104 into the active position so that it fixes the pivoting mechanism 30 relative to the base element 26, e) Step S5: Turn the rear derailleur 20 backwards around the rear wheel axle (A) until the desired chain tension is reached, f) Step S6: Fix the rear derailleur to the frame after reaching the desired chain tension, and g) Step S7: Remove the blocking body 104 from the openings 80 and 102.

[0065] In connection with this method, it can be provided that in the meantime the blocking device 48 (see Fig. 2 and Fig. 3) is activated to block relative movement of the chain guide assembly 32 relative to the movable element 28. This facilitates assembly.

[0066] Fig. Figure 13 shows a second embodiment of the present invention. Two special features can be seen therein. Firstly, a hexagonal eye 110 with a hexagonal opening 112 is provided on component 66B of the pivot arm 66 in the area of ​​the polygonal opening 80. This hexagonal eye 110 is coordinated with the hexagonal opening 102 in the connecting body 54 in terms of its position and the dimensions of the hexagonal opening 112. By inserting a correspondingly dimensioned hexagonal wrench 104 (in Fig. 13 not shown), for example size HEX 5, the base element 26 and the pivoting mechanism 30 can be aligned even more precisely to each other in the blocking position.

[0067] Furthermore, one can see another blocking device 118. This is shown in section in Fig. 14. It comprises a movable, spring-loaded blocking pin 118 with a head 120 and a shaft 122. This is received in a guide bore 124 in component 66b of the pivot arm 66. It is secured against loss by the retaining ring 126. A preload spring 128 preloads the blocking pin 118 into a passive position. A receiving opening 130 matched to the diameter of the blocking pin 118 is formed in the connecting body 54. When the blocking pin 118 and the receiving opening 130 are aligned, the pin can be pressed into the receiving opening 130 against the action of the spring 128. For this purpose, it is necessary to align the pivot mechanism 30 relative to the base element 26 by pivoting the movable element 28 relative to the base element 26 against the action of the tension spring 90. Once the alignment with the receiving opening 130 is achieved, the blocking pin 118 can be pressed into the receiving opening 130.If the movable element 28 is then released, the blocking pin 118 is clamped in the receiving opening 130 and thus blocks the rear derailleur 20 in the assigned assembly position.

[0068] With the embodiment according to Fig. 13 and Fig. 14, the rear derailleur 20 can thus be blocked in two different mounting positions, once with a hexagon key via the hexagon eye 112 and once via the blocking pin 118.

[0069] By pulling the blocking body or releasing the blocking pin 118 to release the clamping, the fixing in the blocking position can be released again.

[0070] The embodiment according to Fig. 15 and Fig. Figure 16 shows a further variant of the invention. In this variant, an adjustable blocking device 118 is formed in the component 66b of the pivot arm 66. This is shown in an individual part in Fig. 16. It is designed in the form of a so-called flip chip, meaning it has a non-circular or oval contour and can be brought into two different pivoting positions by rotating it 180°. The blocking device 118 can be locked into each of these positions via a locking mechanism. A locking lug 134 is provided for this purpose.

[0071] Due to the non-circular profile of the locking device 130, different mounting positions can be achieved depending on its rotational position by rotating it 180° clockwise or counterclockwise around its eccentric longitudinal axis when the locking device is inserted through the receiving opening 80 into a corresponding receiving opening 132 in the connecting body 54. The effect is the same: depending on the rotational position of the locking device 130, the rear derailleur 20 can be adjusted to the respective bicycle category. The locking device can be removed after adjustment; for example, it can also be designed as a disposable part.

[0072] Fig. 17 shows a further schematic view of a rear derailleur 20. This has a special blocking device 140, which will be described below with reference to the Fig. 18-22 is explained.

[0073] The base element 26 and the movable element 28 are connected to each other via the pivoting mechanism 30. The pivoting arms 64, 66 of the pivoting mechanism 30 are movably mounted on the base element 26 and the movable element 28, respectively, via pivoting axes 82, 84, 86, 88. Reference is made to the exploded view according to Fig. 8, the description and labeling of which applies analogously. Fig. In the embodiment shown in Figures 18-22, a blocking body 142 is pivotally mounted on one of the pivot axes 84. For this purpose, it has a sleeve-like shaft 144 with a central opening. A blocking arm 146 is formed protrudingly on the sleeve-like shaft 144. Furthermore, the blocking body 142 is biased upward by a coil spring 148.

[0074] The blocking body 142 can be pressed downward against the action of the coil spring 148 and thereby displaced between a passive position and an active position. In the passive position, the blocking arm 146 is pivoted into the pivoting mechanism so that it neither obstructs movement of the pivoting mechanism 30 for shifting nor comes into contact with the movable element 28. Furthermore, the blocking body 142 can be displaced downward along the pivot axis 84 against the action of the coil spring 148 and subsequently rotated from the passive position into an active position in which it blocks relative movement between the pivoting mechanism 30 and the movable part 28. The blocking arm 146 can be shaped such that it even allows for different blocking positions, each tailored to a bicycle category.

[0075] It is understood that such a blocking device 140 with a pivotable blocking body 142 can be optionally attached to each of the pivot axes 82, 84, 86, 88. This allows for further variants according to the invention.

[0076] Fig. 23-25 ​​relate to the pretensioning device 94 and damping arrangement 96, whereby the chain guide arrangement 32 is spring-loaded and a movement of the chain guide arrangement 32 relative to the movable element 28 is damped.

[0077] In Fig. 23 shows the assembly consisting of pretensioning device 94, damping arrangement 96 and chain guide arrangement 32. Again, it should be noted that this assembly can be screwed into the movable element 28 via the external thread 101.

[0078] The damping arrangement 96 has a coupling device in the form of a one-way or freewheel clutch, in particular in the form of a spring clutch 160, with a damping spring 162, which in the exemplary embodiment is designed with only two spring coils. This damping spring 162 has a spring tab 164. The spring tab 164 is essentially in positive engagement with a corresponding profiling in an insert element 166, which is coupled to the housing of the movable element 28 via a circumferential profiling (see Fig. 24). The damping spring 162 rests at its other end against a spacer ring 168. The spacer ring 168 is in turn arranged on a plastic bushing 170, which in turn interacts with the preload spring 176, designed as a torsion spring, on a rotary shaft 172.

[0079] The damping spring 162 acts in a radial damping direction. For this purpose, the damping spring 162 is spread out over the shaft section 173 of the rotary shaft 172, wherein the shaft section 173 is designed with a diameter slightly larger than the inner diameter of the damping spring 162 in its relaxed state, i.e., in its non-spread out state. As a result of the damping spring 162 spreading out over the shaft section 173 of the rotary shaft 172, a damping frictional force acts in a radial direction, i.e., on the circumferential surface of the shaft section 173. The damping spring 162 therefore interacts radially with the shaft section 173 of the rotary shaft 172, wherein the frictional engagement between these components is set or changed depending on the direction of rotation of the rotary shaft 172 due to the orientation of the windings of the damping spring 162.The spacer ring 168 has at most a slight friction effect and serves essentially to separate and support the spring end of the damping spring 162 and the plastic bushing 170 facing it.

[0080] The plastic bushing 170, in turn, acts as a spacer and holds the damping spring 162 axially in position via the spacer ring 168. The preload spring 176 rests on the outer diameter of the plastic bushing 170, but does not engage it in any significant radial frictional engagement.

[0081] The preload spring 176 engages with one end on a receiving cap 178, on which the external thread 101 is provided. The receiving cap 178 has a profiled inner opening 180 that interacts with the profile of the insert element 166.

[0082] The rotating shaft 172 is provided with a flange portion 182 in which an opening 184 is provided. This opening 184 correlates with a projection 186 of the preload spring 176 and receives it in a torque-transmitting manner. Another projection 188 at the other end of the preload spring 176, in turn, engages the receiving cap 178 in a torque-transmitting manner.

[0083] The rotary shaft 172 is rotatably mounted via the opening 184 on a projecting bearing extension 188 of the receptacle 92, which engages a cavity 190 of the opening 184 in the rotary shaft 172. The rotary shaft 172 extends through the receptacle cap 178, which closes the cavity within the receptacle 92 of the movable element 28.

[0084] Furthermore, the rotary shaft 172 is positively coupled to the chain guide arrangement 32 via a hexagonal profile section 196 and thus transmits torque and is secured to the latter via a lock screw 192 and a washer 194.

[0085] The preload and thus the damping is defined by the frictional engagement between the damping spring 162 and the shaft portion 173 of the rotary shaft 172, resulting from the fact that the damping spring 162 is spread out onto the shaft portion 173. As already explained, the inner diameter of the damping spring 162 in the relaxed, i.e., non-spread out, state is smaller than the outer diameter of the shaft portion 173. The two coils of the damping spring 162 generate a frictional force between the damping spring 162 and the shaft portion 173 in the radial direction as a result of the spreading out onto the shaft portion 173. The spring end 164 is rotationally fixed at one end by means of the profiled insert element 166 and the correspondingly profiled inner opening 180 of the receiving cap 178. If the rotary shaft 172 rotates with its shaft section 173 relative to the damping spring 162, the latter is “tightened” in one direction, so that the frictional force increases.This direction corresponds to . Fig. 24 the direction of rotation of the rotary shaft 172 in Fig. 24 in the counterclockwise direction GUZS. If the rotary shaft 172 rotates with its shaft section 173 relative to the damping spring 162 in the opposite direction of rotation according to Fig. 24, ie clockwise UZS, the damping spring 162 tends to expand, so that the friction is reduced.

[0086] The damping arrangement 96 shown with the spring 162 enables a delay-free power transmission with good damping effect and low installation space requirements.

[0087] It is understood that the information relating to the Fig. 23-25 ​​can also be used independently of the remaining structure, in particular the blocking device. Accordingly, the damping arrangement 96, as described with reference to Fig. 23-25, can also be regarded as a separate and independent aspect of the invention. QUOTES CONTAINED IN THE DESCRIPTION

[0000] This list of documents submitted by the applicant was generated automatically and is included solely for the convenience of the reader. This list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions. Cited patent literature

[0000] EP 0 875 444 A1

[0010] EP 1 342 658 A1

[0010] EP 1 764 297 A1

[0010] DE 10 2018 001 253 A1

[0010] DE 10 2022 115 599 A1

[0010] DE 10 2018 208 053 ​​A1

[0011] DE 10 2021 003 745 A1 [0012, 0027, 0052] DE 10 2011 118 912 A1

[0013] DE 10 2020 209 370 A1

[0014]

Claims

[1] Rear derailleur (20) for a bicycle gearshift comprising: - a base element (26) which can be attached to a bicycle frame (10); and - a movable element (28) which is coupled to the base element (26) via a pivoting mechanism (30) and is pivotally displaceable relative thereto, wherein the pivoting mechanism (30) is pivotally movable relative to both the movable element (28) and the base element (26), characterized by a blocking device (80, 102) which is designed to fix the movable element (28) at least temporarily relative to the base element (26), wherein the blocking device (80, 102) is designed such that the pivoting mechanism (30) can be temporarily fixed in at least one predetermined blocking position via a direct coupling relative to the base element (26) or relative to the movable element (28). [2] Rear derailleur (20) according to claim 1, characterized byin that the pivoting mechanism (30) comprises at least two pivoting arms (64, 66), wherein a first pivoting arm (64) is pivotally coupled to the base element (26) with its first end section and pivotally coupled to the movable element (28) with its second end section, wherein a second pivoting arm (66) is pivotally coupled to the base element (26) with its first end section and pivotally coupled to the movable element (28) with its second end section. [3] Rear derailleur (20) according to one of the preceding claims, characterized byin that the base element (26) and / or the movable element (28) has a first receiving opening (102), and in that the pivoting mechanism (30) has a second receiving opening (80) on a component, wherein the first and second receiving openings (80, 102) are aligned with one another in at least one predetermined relative position of the movable element (28) relative to the base element (26) in such a way that, in the event of at least partial alignment of the first and second receiving openings (80, 102), a blocking body (104) can be introduced into them to produce the direct coupling in order to block a pivoting movement of the movable element (28) relative to the base element (26) via the pivoting mechanism (30). [4] Rear derailleur (20) according to claim 2, characterized byin that the base element (26) and / or the movable element (28) has a first receiving opening (102), and in that the first pivot arm (64) and / or the second pivot arm (66) has a second receiving opening (80), wherein the first and second receiving openings (80, 102) are aligned with one another in at least one predetermined relative position of the movable element (28) relative to the base element (28) such that, in the event of at least partial alignment of the first and second receiving openings (80, 102), a blocking body (104) can be introduced into them to establish the direct coupling in order to block a pivoting movement of the movable element (28) relative to the base element (26) via the pivoting mechanism (30). [5] Rear derailleur (20) according to one of the preceding claims, characterized bythat at least one of the first and second receiving openings (80, 102) is formed with a rotation-proof receiving profile, in particular with a hexagonal profile, [6] Rear derailleur (20) according to one of the preceding claims, characterized by that the switching mechanism (20) is designed as a cable-operated switching mechanism, wherein at least one of the pivot arms (64, 66) is designed as a cantilever arm (66b) for the attachment of a cable pull, wherein preferably the cantilever arm (66b) is designed with the second receiving opening (80). [7] Rear derailleur (20) according to one of claims 1 to 5, characterized by that the rear derailleur is designed as a motor-operated rear derailleur, wherein in particular the drive motor and a drive gear associated therewith are arranged at least partially on the base element. [8] Rear derailleur (20) according to one of the preceding claims, characterized bythat by providing at least two differently dimensioned blocking bodies (104) which can be introduced into the at least partially aligned first and second receiving openings (80, 102) to produce the direct coupling, the rear derailleur (20) can be temporarily fixed in at least two predetermined blocking positions. [9] Rear derailleur (20) according to one of the preceding claims, characterized by that the blocking device has a blocking pin (118) which is attached to one of the components base element (26) or first pivot arm (64) or second pivot arm (66) or movable element (28) and that for temporarily fixing the switching mechanism (20) in the at least one blocking position, the base element (26) or the movable element (28) is directly coupled to the first pivot arm (64) or the second pivot arm (66) to prevent a pivoting movement. [10] Rear derailleur (20) according to claim 9, characterized by that the blocking pin (118) is spring-loaded into a blocking-free passive position and / or can be locked in this position. [11] Rear derailleur (20) according to claim 9 or 10, characterized by that the blocking pin (118) has a cross-sectional profile deviating from a circle and / or is mounted eccentrically, so that it can be mounted in at least two different relative positions relative to one of the components base element (28) or first pivot arm (64) or second pivot arm (66) or movable element (28) in order to achieve at least two different blocking positions. [12] Rear derailleur (20) according to one of the preceding claims, characterized byin that, to produce the direct coupling, a pivotable, preferably spring-biased, blocking body is arranged about one of the pivot axes of the pivot mechanism, wherein said blocking body is pivotable, preferably by overcoming the spring preload, between a passive position and at least one blocking position about the associated pivot axis, wherein the blocking body in the passive position allows the relative movement between the base element and the movable element via the pivot mechanism and wherein the blocking body in the at least one blocking position provides a direct coupling between the base element or the movable element and the pivot mechanism, so that a relative movement between the base element and the movable element is blocked in a predetermined position. [13] Rear derailleur (20) according to one of the preceding claims, characterized bya chain guide arrangement (32) which is coupled to the movable element (28) and is pivotable relative thereto about a pivot axis (42), and a pretensioning device (94) with which the chain guide arrangement (32) is pretensioned relative to the movable element (28) about the pivot axis (42) into an initial position, wherein the chain guide arrangement (32) is pivotable against a tensioning force of the pretensioning device (94) from the initial position about the pivot axis (42) into various operating positions. [14] Rear derailleur (20) according to claim 13, characterized by that the chain guide arrangement (32) together with the pretensioning device (94) is combined to form an assembly which can be attached to the movable element (28) via a detachable connection, preferably a threaded connection (101). [15] Rear derailleur (20) according to one of the preceding claims, characterized bythat the pivoting mechanism (30) has pivot axes (82, 84, 86, 88) which are aligned substantially orthogonally to the rear wheel axis (A). [16] Rear derailleur (20) according to the preamble of claim 1 and / or according to at least one of the preceding claims, characterized byin that the pretensioning device (94) has a damping arrangement (96) which is designed to counteract a damping effect of a relative movement between the movable element (28) and the chain guide arrangement (32), wherein the damping arrangement (96) comprises a coupling device (160) via which the damping arrangement (96) is coupled to a rotary shaft (172) and a support, wherein the coupling device (160) has a damping spring (162) which is supported on the one hand on the rotary shaft (172) and on the other hand on an insert part (166) which is coupled or can be coupled to the movable element (28) and which develops its damping effect between them via a frictional engagement, preferably in the radial direction. [17] Rear derailleur (20) according to claim 16, characterized bythat the damping spring (162) is attached at one end to one of the components of the rotary shaft (172) and the movable element (28) in a rotationally fixed manner and is in direct or indirect frictional engagement with the other component of the rotary shaft (172) and the movable element (28), preferably in radial frictional engagement, the damping effect increasing or decreasing depending on the direction of the relative rotation. [18] Rear derailleur (20) according to claim 16 or 17, characterized by that the damping spring (162) has a maximum number of four turns, preferably a maximum number of three turns, further preferably a maximum number of two turns. [19] Rear derailleur (20) according to one of claims 16 to 18, characterized by that the insert part (166) is made of metal, preferably of steel. [20] Rear derailleur (20) according to one of claims 16 to 19, characterized bythat an elastic force storage device (176) is coupled to the chain guide assembly (32) via the rotary shaft (172) in order to exert the pretensioning force on the chain guide assembly (32) via the rotary shaft (172). [21] Rear derailleur (20) according to one of claims 16 to 20, characterized by in that the rotary shaft (172) is rotatably mounted on a cover element (186) by means of a rotary bearing (184), which cover element (186) closes the receptacle (92) of the movable element (28) together with the rotary shaft (172) extending through a through opening of the cover element (186) and is fastened to the movable element (28). [22] Rear derailleur (20) according to one of the preceding claims, characterized byin that the rear derailleur (20) is designed for coaxial mounting on a rear wheel axle (A) of a bicycle and the base element (26) comprises a first connection end for coaxial mounting on the rear wheel axle (A) and a second connection end for coupling to a pivoting mechanism (30). [23] Rear derailleur (20) according to the preceding claim, wherein the first connection end of the base element (20) has a first arm (50) and a second arm (52) which are arranged spaced apart from one another in the axial direction, wherein, when mounted on the frame (10), the first arm (50) is located on an axial inner side of the frame (10) and the second arm (52) is located on an axial outer side of the frame (10). [24] Rear derailleur (20) according to one of the preceding claims, wherein the second connection end of the base element (20) has a first axle receptacle for a first pivot axis (82) of the pivot mechanism (30) and a second axle receptacle for a second pivot axis (86) of the pivot mechanism (30), wherein the first axle receptacle and the second axle receptacle are each oriented substantially orthogonally to the rear wheel axis (A). [25] Method for adjusting a bicycle drive, comprising a rear derailleur of the type described above, a multiple sprocket arrangement, a front chainring and a chain, wherein the rear derailleur is adjusted relative to the multiple chainwheel arrangement, with the following steps: as follows: a) Determining a bicycle category, in particular determining whether the bicycle has an unsprung or sprung rear wheel on which the rear derailleur (20) is to be mounted, b) selecting a blocking body (104) adapted to the specific bicycle category, c) depending on the specific bicycle category, moving the rear derailleur (20) against the action of the tension spring (90) in alignment with a reference pinion, in particular with one of the middle pinions of the multiple sprocket arrangement, preferably with the sixth or seventh pinion of the sprocket cassette (18), such that the chain (40) engages with the reference pinion and such that the first receiving opening (102) is aligned with the second receiving opening (80), d) inserting the blocking body (104) into the active position so that it fixes the pivoting mechanism (30) relative to the base element (26), e) Turn the rear derailleur (20) backwards around the rear wheel axle (A) until the desired chain tension is reached, f) Fixing the rear derailleur to the frame after reaching the desired chain tension, and g) Removing the blocking body (104) from the openings (80) and (102).

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