Chain guide roller for a bicycle derailleur, bicycle derailleur and bicycle drive train

Abstract

The invention relates to a chain guide roller (16) for a bicycle drive train having a chain (6), a multi-layer pinion configuration (5) and a bicycle rear derailleur. The chain guide roller (16) comprises a bearing region rotatable about an axis of rotation, a tooth region constructed with teeth for engaging the chain (6), and a load-bearing structure connecting the bearing region and the tooth region together. On the inner and outer sides of at least one tooth of the chain guide roller (16), a guide region is respectively constructed on the lateral face in order to laterally guide the chain (6) substantially parallel to the axis of rotation. At least one inner-side guide region of the at least one tooth has a thickness dimension which is at least locally reduced relative to at least one outer-side guide region with respect to a central plane (P M ) of the chain guide roller (16), so that a chain section (6 t ) which exits substantially tangentially from the chain guide roller (16) can adopt a greater angle of inclination (λ o ) in the outer-side direction (S i ) than in the inner-side direction (S i ).

Description

Technical Field

[0001] This invention relates to a chain guide roller for a bicycle rear shift mechanism, a bicycle shift mechanism, and a bicycle drivetrain. Background Technology

[0002] The positional or directional descriptions used in the following descriptions, such as "left," "right," "front," "back," "up," and "down," are equivalent to the rider's perspective on a bicycle. The same applies to the industry-standard directional descriptions used in the descriptions, such as "inside" (left side, to the left, or towards the larger pinion of the freewheel) and "outside" (right side, to the right, or towards the smaller pinion of the freewheel), which specifically refer to the shifting process or the position of the pinion on the freewheel.

[0003] A bicycle pinion freewheel consists of multiple pinions spaced axially along the rear axle, each pinion having a different number of teeth. Depending on the specific gear ratio selected by the rider, the bicycle chain is positioned on one of the pinions via a shifting mechanism. This, in conjunction with the number of teeth on the sprocket on the bottom bracket, determines the gear ratio and the rider's desired cadence.

[0004] In recent years, the bicycle industry, primarily in the mountain bike sector, has gradually reduced the number of chainrings on the bottom bracket from the traditional three of different sizes to two. During this period, at least in the high-end segment, it has mostly been reduced to a single chainring. This simplifies the drivetrain and enhances its reliability. Consequently, for riders, shifting operations and logic are also simplified, requiring only a shift lever.

[0005] Furthermore, it is also possible to omit the front chain derailleur and its control mechanism, as well as the necessary devices for mounting this chain derailleur and its control mechanism to the bicycle frame and handlebars, within the bottom bracket area. Without the chain derailleur, additional sprockets, shift levers, and associated devices, the bicycle's weight is significantly reduced.

[0006] In bicycles with electric-assisted drives, multiple shiftable chainrings are not used in most cases, for example, for structural space considerations and to simplify the drivetrain.

[0007] Without setting a sub-factor for the gear ratio range on the bicycle, it is necessary to significantly increase the gear ratio range provided by the pinion freewheel, which is provided in advance by multiple sprockets on the bottom bracket and is usually in the range of 180% to 200%.

[0008] This necessity led to the development of pinion flywheels, which feature not only extremely small pinions with 11 teeth or less on the outer side, but also extremely large pinions with 50 teeth or more on the inner side. This allows these flywheels to achieve a 500% gear ratio range, thus providing a suitable gear ratio for almost all riding conditions.

[0009] In order to keep the operating force low when switching between different drive stages of the flywheel, a shifting mechanism with a non-tilted or only slightly tilted parallelogram mechanism is particularly used when combined with such flywheels. Such shifting mechanisms are disclosed, for example, in patents EP2641823B1 and EP3388324A3, and are also known in the industry as so-called direct-drive shifting mechanisms. The expression "non-tilted or slightly tilted parallelogram mechanism" in this and the aforementioned prior art means that, when the shifting mechanism is mounted on the bicycle and ready to be used, the axis of this parallelogram mechanism is arranged parallel to or only slightly tilted relative to the longitudinal center plane of the bicycle. In the "non-tilted or only slightly tilted parallelogram shifting mechanism", the chain guide roller of the shifting mechanism mainly follows the tooth tip profile of the pinion flywheel vertically by means of the deflection motion of the chain cover during shifting, and then by the deflection motion of the upper chain guide roller, rather than by means of the tilt of the parallelogram mechanism as in the shifting mechanism with the tilted parallelogram mechanism.

[0010] Therefore, in this type of shifting mechanism, the shifting parallelogram mechanism moves in a plane that has little or no tilt component around an imaginary straight line extending in the riding direction. Thus, this type of shifting mechanism differs significantly from the more tilted shifting parallelogram mechanisms that have been used for decades, which largely follow the contour of the pinion flywheel during shifting through their tilt.

[0011] In shifting mechanisms with a non-tilted or only slightly tilted parallelogram-shaped shifting mechanism, the upper chain guide roller is mounted at a distance from the P-axis (the deflection axis of the chain cover relative to the movable shifting element or P-steering knuckle), for example, see EP3388324A3. Figure 3 Or EP2641823B1 Figures 3 to 7 .

[0012] In bicycle shifting mechanisms, the upper and lower chain guide rollers are typically housed between two guide plates in a shifting mechanism cover configuration, which is also simply and synonymously referred to in the industry and in the description below as a chain cover configuration or chain cover.

[0013] The shift mechanism roller is primarily used to guide the chain within the small gear flywheel area on the bicycle's rear wheel, maintain chain tension, and accommodate excess chain length depending on the specific gear engaged.

[0014] The chain guard can typically be deflected about the deflection axis relative to the so-called P steering knuckle of the shifting mechanism in a spring-loaded manner, and in this way maintains the required chain tension.

[0015] The lower chain roller, often referred to as the chain tension roller, is responsible for accommodating excess chain length and for reliably guiding empty chain strands into the shifting mechanism under all operating conditions.

[0016] The chain guide roller, also known as the chain guide roller, is responsible for lateral guidance of the chain, particularly the empty chain strands running to the pinion freewheel, and for shifting gears between the different pinions on the freewheel when the rider shifts gears via the shift lever or other operating elements.

[0017] Because the small gear flywheel described at the beginning of this article has a large transmission ratio range or gear difference, the number of gears (usually 10 to 13) is mainly limited by the axially limited structural space, and the selection of gear runout based on the percentage calculation between adjacent small gears. In this type of flywheel, the gear runout is usually greater than that of multiple transmission devices, that is, greater than that of transmission systems with more than one sprocket in the central shaft area, which generally have a smaller flywheel transmission ratio range.

[0018] The combination of large gear shift jumps and (common in shifting mechanisms with tilted parallelogram mechanisms that are not tilted or slightly tilted) a considerable gap between the P-axis and the chain guide rollers produces the following geometric boundary conditions: the so-called chain gap known in the industry, which is the gap between the upper chain guide roller and the pinion flywheel that meshes with the chain, is much smaller during inward shifts than during outward shifts or during normal chain operation.

[0019] The reason is that in most bicycle shifting mechanisms, especially those with a parallelogram-shaped shifting mechanism that is not tilted or only slightly tilted, the chain guard deflects only after the chain has engaged with the larger pinion during an inward shift, and only then does the upper chain guide roller begin following the tapered tooth profile of the pinion sprocket. In such shifting mechanisms, the chain guard deflects fully only after the chain has disengaged from the smaller pinion and moved completely on the larger pinion, causing the upper chain guide roller to follow in the desired manner and creating the desired chain gap between the upper chain guide roller and the larger target pinion in the shifting process.

[0020] Therefore, in the aforementioned shifting mechanism with a parallelogram-shaped shifting mechanism that is not tilted or only slightly tilted, during the inward shifting process, only the deflection of the chain guard increases the chain gap, that is, the distance between the upper chain guide roller and the larger target pinion. However, since in this type of shifting mechanism, the chain guard, together with the upper chain guide roller, has already moved substantially horizontally inward before the chain guard begins to deflect forward and adjust the chain gap as desired, in this type of shifting mechanism, the upper chain guide roller presses the chain against the larger pinion with a smaller radial gap at the beginning of the inward shifting process.

[0021] Especially in the current so-called indexing bicycle shifting device, that is, the bicycle shifting device in which the axial movement of the chain guard and the upper chain guide roller on the pinion flywheel is implemented step by step according to the spacing of the pinions of the pinion flywheel, this axial movement is always roughly constant in each shifted gear, and thus is always roughly equivalent to the absolute amount consistent with the spacing of the pinions.

[0022] As described above, the chain gap and the free chain segment overflowing between the chain guide roller and the larger gear are relatively short when shifting inward. Therefore, based on trigonometric relationships, a constant absolute amount of axial deflection of the shifting mechanism inward produces a desired relatively large overflow chain segment angle, so that the chain can properly transition to the larger gear and prevent shifting errors.

[0023] However, in the known upper chain guide rollers in the prior art, the chain guiding characteristics and the angle are actually the same on both axial sides of the chain guide roller. Therefore, when shifting gears inward with the chain guide roller in the prior art, this angle is relatively small.

[0024] Therefore, in these known chain guide rollers, under the aforementioned premise that the absolute amount of axial shifting mechanism deflection is constant in each shifted gear, and with the relatively small chain angle in these rollers, even when shifting inwards, it usually leads to premature shifting to a larger gear because the chain rubs against the teeth of the larger gear earlier or more strongly during the shifting process, thus tending to move up to the larger gear prematurely.

[0025] The pinions of the multi-layered pinion flywheel are typically equipped with specially designed grooves and dedicated upward-moving teeth. The so-called shift fork shaft paddle grooves are where the chain should move from the smaller pinion to the larger pinion along a precisely defined and, in particular, approximately tangential path between the two pinions. However, to prevent incorrect shifting, the chain must be pushed aside in a laterally sliding manner along all other teeth of the larger pinion until it reaches one of the upward moving teeth of the larger pinion.

[0026] However, the greater the gear shifting between the pinions, the smaller the chain gap and the length of the overflowing chain section at the start of the shift, and the more teeth between the upward moving teeth distributed around the larger pinion, the more difficult it is to push the chain away on the teeth of the larger pinion that are not used for upshifting when shifting inwards.

[0027] There is a particular challenge in pushing the chain away in the following situations: especially in the coarse-to-fine toothed pinion flywheels, also known in the industry as X-Sync pinions, where the chain is on an odd-numbered so-called transition pinion and must somehow switch from there synchronously in a defined orientation to the next larger even-numbered pinion with coarse and fine teeth, such that the fine teeth of this larger pinion mesh with the inner chain plate links, and the coarse teeth of this larger pinion mesh with the outer chain plate links. Paragraph

[0085] and DE102015016767A1 Figure 5 For example, this gear shifting situation was revealed.

[0028] In this scenario, starting from an odd-numbered transition pinion and depending on the specific pinion size, the pinion flywheel may only have two, or in some cases even only one, suitable flywheel rotation angle positions per revolution for the upward-moving tooth to meet the outer link of the chain. This is because it is desirable for the chain to move upwards only to an even-numbered coarse pinion at the outer link, so that the chain does not move asynchronously—that is, by engaging the coarser tooth on the inner link—towards a larger pinion.

[0029] In this case, even if the larger pinion includes multiple inward shift fork block grooves each with corresponding upward shifting teeth, and these inward shift fork block grooves have a substantially even number of tooth pitches due to the alternation of coarse and fine teeth, the chain can still start from the odd-numbered transition pinion and, in the best case, move up to the even-numbered larger pinion only at every other upward shifting tooth, because the chain running to the odd-numbered transition pinion only encounters the upward shifting tooth on the outer chain plate link at every other upward shifting tooth.

[0030] Therefore, in such or similar situations, the chain must be pushed away on a large number of teeth of the larger pinion, and possibly even during almost the entire rotation of the pinion freewheel, to prevent it from shifting onto the larger pinion in an undesirable position. This could result in uneven shifting, increased load on the drivetrain, and unwanted noise, as well as the chain slipping on the pinion freewheel, which could adversely affect riding safety.

[0031] Therefore, generally speaking, especially in shifting mechanisms with non-tilting or only slightly tilted parallelogram shifting mechanisms as described at the beginning of this article, and more often in the combination of such shifting mechanisms with small gear flywheels with coarse and fine teeth, a greater degree of chain skew is desired during inward shifting. For this reason, it is desirable that the axial chain guiding performance of the chain guard or upper chain guide roller be relatively weak, so that the chain does not move up to the next smaller gear at teeth not designed for this purpose, but is pushed as effectively as possible at all teeth not designed for upward movement.

[0032] During outward gear shifting, in this type of shifting mechanism, similar to the aforementioned inward gear shifting process but in the opposite direction, the chain gap formed at the start of the shift, that is, the distance between the upper chain guide roller and the larger gear to be disengaged, is much larger than that of a traditional shifting mechanism with an inclined parallelogram mechanism.

[0033] This relates to the following situation: In the aforementioned shifting mechanism with a non-tilted or only slightly tilted parallelogram-shaped shifting mechanism, the following of the upper chain guide roller along the conical tooth profile of the pinion flywheel, and the following of the correct chain clearance between the chain guide roller and the pinion flywheel, do not begin with the lateral shifting movement of the shifting mechanism. Instead, they only begin after the chain engages with the target pinion, i.e., after engaging with the smaller pinion, based on the gradually freeing chain length, which, viewed from the outside, causes the chain guard assembly to deflect clockwise. Based on the chain length that becomes free as the chain gradually engages with the smaller pinion, this deflection of the chain guard ultimately leads to the restoration of the desired chain clearance, specifically, by the upper chain guide roller following the tooth profile of the flywheel, thereby radially re-approaching the flywheel.

[0034] Because the chain gap is still relatively large at the start of the outward shifting process, and the length of the chain segment overflowing between the upper chain guide roller and the smaller gear to be disengaged is relatively large, and based on the resulting trigonometric relationship, combined with the aforementioned constant absolute amount of axial deflection of the shifting mechanism, the chain should obtain a relatively small angle during the outward shifting process so as to deflect laterally to a sufficient extent within the region of the pinion teeth of the larger gear, so that the chain can be caught by one of the specially designed downward moving teeth of the larger gear and pushed laterally outward in a preset manner, thereby being guided to the smaller gear at the preset shifting position.

[0035] When shifting outwards, the following factors contribute to the correct displacement of the overflow chain segment: a larger chain gap during outward shifting, a relatively long overflow chain segment, and relatively strong axial chain guiding performance of the chain guide roller. In other words, the axial movement of the chain guide roller by the aforementioned absolute amount is transmitted as directly as possible by the shifting mechanism to the overflow chain segment between the chain guide roller and the pinion flywheel.

[0036] If the chain is not properly displaced, and the angle of the chain segment overflowing when shifting outward is too large, it may cause shifting errors or delays in the shifting process. This is because, in this case, the chain is not pushed laterally outward on one of the specially designed downward teeth of the larger gear and guided to the smaller gear as intended.

[0037] Chain guide rollers known in the industry as so-called X-Sync chain guide rollers, which alternately have coarse and fine teeth for meshing with links on the outer or inner chain plates, in principle possess this excellent axial guiding performance, and the chain can be deflected more precisely and uniformly in its direction of rotation based on the relevant axial guidance of the inner and outer chain plates. However, in X-Sync chain guide rollers known in the prior art, where the teeth are generally mirror-symmetrical to the center plane of the chain guide roller, this axial guiding performance is the same in degree or intensity when shifting outwards and inwards.

[0038] Therefore, the aforementioned relationship given by the same type of chain roller in the prior art creates the following objective conflict: when shifting gears inward, it is desirable for the upper chain guide roller (in the axial direction of the chain roller) to have weaker lateral chain guiding performance, but when shifting gears outward, stronger chain guiding performance is required.

[0039] In addition, other challenges exist. In X-Sync chain guide rollers known in the prior art with alternating coarse and fine teeth, for example, when the rear wheel of a bicycle bounces upwards, the chain may lift off the chain guide roller, resulting in a missynchronization of the chain and the tooth geometry of the chain guide roller. In this case, the coarse teeth of the chain guide roller no longer engage with the chain links on the outer chain plate, causing the chain to snag on the tips of the chain guide roller teeth.

[0040] This can be noticed through poor chain operation and the corresponding noise. In many cases, it is necessary to shift to a specific gear and press the pedal backward to make the chain skip over a tooth on the chain guide roller, i.e., jump back to the synchronized position.

[0041] Furthermore, there is a conflict of objectives regarding the optimal chain clearance for inward and outward shifts, as well as regarding the desired maximum wrap angle of the chain on the chain guide roller or pinion, and consequently, the originally desired forward positioning of the shifting mechanism relative to the always-constrained structural space on the rear fork end. This structural space, which can be used for the shifting mechanism in the fork end region on the bicycle frame, is particularly constrained by frame components in the chain guide region.

[0042] This results in compromises being made for the orientation of the shift mechanism, the deflection and length of the chain guard, and the final wrapping of the chain on the upper chain guide roller, which cannot be fully or only optimized by the chain guide roller in the sense of optimal chain guidance.

[0043] Specifically, to achieve a good trade-off between shift mechanism capacity, rear fork end structural space, and chain wrap around the freewheel and chain guide rollers, the shift mechanism is typically twisted further rearward clockwise when viewed from the outside than it would be without considering frame structural space. In practice, this results in a reduced wrap angle around the chain guide rollers, leading to poor chain guidance, particularly during outward shifts, especially in the area of ​​the largest pinion, as seen in EP2641823B1. Figure 3 As shown, in these pinions, the chain guards deflect counterclockwise to a greater extent, thereby further reducing the wrapping of the chain guide rollers.

[0044] These target conflicts in the prior art, in particular, can lead to shifting delays or shifting errors when shifting outwards. When the chain runs asynchronously on the chain guide roller, the reduced wrap angle of the chain on the upper chain guide roller, as mentioned above, increases the difficulty of chain resynchronization.

[0045] The aforementioned conflicting aspects and objectives result in a significant limitation on the range of chain gaps that can be reasonably used when employing chain guide rollers in the prior art, or in general, a conflict between geometric optimizations for inward shifting and outward shifting in the shifting mechanism. Summary of the Invention

[0046] Based on the aforementioned prior art, the purpose of this invention is to provide a chain guide roller, a bicycle shifting mechanism, and a bicycle transmission system to overcome the aforementioned disadvantages and conflicting objectives.

[0047] The present invention provides a chain guide roller, a bicycle shifting mechanism, and a bicycle drivetrain as solutions to achieve the above objectives.

[0048] Generally, a chain guide roller first includes a bearing region that can rotate about an imaginary axis of rotation, the bearing region being used to accommodate a bearing configuration, such as a ball bearing; it also includes a toothed region having teeth configured to engage with a bicycle chain; and a load-bearing structure including the bearing region and the toothed region.

[0049] In this embodiment, on at least one tooth of the chain guide roller, preferably on multiple or all teeth, a guide area is constructed on the inner and outer sides of the at least one tooth, so as to guide the chain laterally in a direction parallel to the axis of rotation.

[0050] According to the invention, the chain guide roller is characterized in that at least one inner guide region of the at least one tooth has a thickness dimension that is at least partially reduced relative to the center plane of the chain guide roller, relative to at least one outer guide region of the at least one tooth. This at least partially reduced thickness dimension of the inner guide region is designed or caused in such a way that, for example, during chain shifting in a pinion configuration, when viewed from the chain guide roller, the chain segment that exits the chain guide roller generally tangentially and overflows, for example, into a pinion in a multi-layered pinion configuration, can adopt a greater angle in the outer direction (i.e., when shifting inwards) than in the inner direction (i.e., when shifting outwards).

[0051] Therefore, the at least locally reduced thickness of the inner guide region of the at least one tooth relative to the outer guide region results in a decrease in the lateral chain guiding performance of the chain roller, that is, in the axial direction of the chain roller, during inward shifting compared to outward shifting.

[0052] In other words, the chain guide roller maintains the desired axial chain guiding performance for outward shifting, while its chain guiding performance is weakened for inward shifting.

[0053] In other words, the reduced thickness of the inner guide area relative to the outer guide area results in the absolute amount of axial deflection of the chain segment overflowing during inward shifting within the pinion tooth area matching the absolute amount during outward shifting, thus making it more uniform.

[0054] Preferably, at least one of the guide regions of the at least one tooth includes a protruding ridge extending axially from the end plane or side of the tooth region of the chain guide roller. Thus, the ridge is arranged within the tooth region of the chain guide roller on the inner or outer side of the at least one tooth.

[0055] By constructing a prominent guide area, the axial guiding performance of the guide area can be matched in a desired manner with the corresponding inner width of the inner or outer chain plate links.

[0056] Preferably, at least one guide element of the at least one tooth has at least partially a thickness that decreases as the distance from the rotation axis increases. This ensures that, especially during gear shifting, in the event of a corresponding chain misalignment, any overflowing chain segment can move away from the chain guide roller uniformly, gradually, and smoothly. Furthermore, this prevents the chain from unintentionally catching on the tooth tip of the chain guide roller when the pedal is pressed backward.

[0057] Preferably, the region where the thickness of at least one guide element of the at least one tooth is reduced is constructed as a chamfered surface. This chamfered surface defines a chamfered plane, which is arranged obliquely relative to the center plane of the chain guide roller along the axial direction of the chain guide roller, thereby defining the chamfered surface relative to the surface of the tooth region of the chain roller or the radial inner boundary edge of the side surface of the at least one tooth by this oblique angle.

[0058] Therefore, particularly preferably, in addition to the aforementioned axial inclination, the chamfer plane and the chamfer surface of the at least one tooth are also deflected relative to the center plane of the chain roller about the radial line of the chain roller corresponding to the at least one tooth, such that the radial inner boundary edge of the chamfer surface has a direction that rises radially outward along the working rotation direction of the chain guide roller.

[0059] As a supplement or alternative, this deflection of the chamfered plane can be implemented in a certain way and result in the guide element of the at least one tooth having a thickness that increases from the loaded tooth surface to its unloaded tooth surface in the region of the chamfered surface, that is, having a thickness that increases in the working rotation direction of the chain guide roller.

[0060] The inner boundary edge of the chamfered surface, which rises radially outward in the working rotation direction of the chain guide roller, or the thickness of the tooth in the tooth guide area increasing from the loaded tooth surface to its unloaded tooth surface in the working rotation direction, ensures that, on the one hand, especially during gear shifting, when the chain is correspondingly misaligned, the overflowing chain segment can evenly and gradually leave the chain guide roller. Furthermore, it prevents the chain from unintentionally catching on the tooth tips of the chain guide roller when the pedal is pressed backward. On the other hand, this technical solution allows the chain to be guided along the chain roller axis with the desired strength, even when the chain is running on and guided by the chain roller without leaving it.

[0061] In other words, the teeth of the chain rollers that are roughly tangential to the chain section that overflows from the pinion flywheel have weaker axial guiding performance, especially much weaker guiding performance on the inner side than on the outer side, but have stronger axial guiding performance on the chain section running on the chain rollers that is not weakened on either the inner or outer side.

[0062] According to another preferred embodiment, the tooth surface angle of the loaded tooth surface of the at least one tooth is gentler than the tooth surface angle of the unloaded tooth surface of the at least one tooth. Also preferably, the tooth tip region surrounding the at least one tooth has an inclination angle that is primarily inclined towards the unloaded tooth surface.

[0063] By utilizing a gentler load-bearing tooth angle and / or an inclination angle of the tooth tip region primarily inclined towards the unloaded tooth surface, the chain can more easily and quickly revert from potentially undesirable asynchronicity on chain rollers with coarse and fine teeth to synchronized operation on the chain rollers in a defined manner, or prevent asynchrony altogether. The tooth tip region inclined towards the unloaded tooth surface, in particular, causes a relative torque between the chain and chain rollers to be generated when the chain asynchronically engages the tooth surface or tooth tip radially outward. This relative torque causes the chain rollers to rotate relative to the chain until the chain re-engages with the chain rollers in synchronization and stabilizes there. The steeper angle of the unloaded tooth surface of the chain guide rollers (which becomes the load-bearing tooth surface when the pedal is pressed backward) also suppresses chain asynchrony, thereby reducing the frequency of asynchrony.

[0064] The present invention can be implemented on any chain roller, specifically in that, as described above, at least one tooth of the chain roller, or preferably the inner guide region of one tooth, has the aforementioned at least partially reduced thickness relative to the tooth, and preferably the outer guide region of all teeth.

[0065] However, the chain guide roller preferably has an even number of teeth, which alternate with the first or second group of teeth in the circumferential direction. The teeth in the first group are narrower, narrower than the spacing between the inner chain plates of the chain, so that these narrower teeth cannot easily enter the gaps between the relatively close inner chain plates of the inner chain plate links.

[0066] The second set of teeth includes at least one wider tooth. Preferably, one or all of the teeth in the second set of teeth are configured to be wider such that these wider teeth can only enter the inter-plate gaps between relatively distant outer chain plates of the outer chain plate links, but cannot enter the inter-plate gaps of the inner chain plate links.

[0067] In other words, this means that the chain guide roller is preferably implemented as a so-called X-Sync chain guide roller with alternating coarse and fine teeth. Its advantage is that the lateral guiding effect of the chain guide roller along the chain roller axis on the chain segment that overflows substantially tangentially between the chain guide roller and the pinion flywheel is generally enhanced, which is beneficial for shifting accuracy. Furthermore, this method matches the guiding effect of the coarse teeth relative to the outer chain link with the guiding effect of the fine teeth relative to the inner chain link, resulting in a more uniform effect. This also helps to improve shifting accuracy when shifting between different pinions on the pinion flywheel.

[0068] Furthermore, preferably, at least one tooth in the first group of teeth, preferably all teeth in the first group of teeth, has a radially reduced tooth height relative to at least one tooth in the second group of teeth, preferably relative to all teeth in the second group of teeth.

[0069] The reduced tooth height of the first set of teeth, which is also a narrower tooth suitable for meshing with the inner chain plate links, serves two purposes. First, it ensures uniform lateral guidance of the chain segments overflowing between the chain guide roller and the pinion flywheel along the chain roller axis on alternating coarse and fine teeth. Second, this technique also helps, particularly in conjunction with the preferred fine tooth tips that are more significantly inclined towards the non-loaded tooth surface, to quickly re-synchronize the chain that may be out of sync on the chain guide roller and thus caught on the tips of the coarse teeth.

[0070] Furthermore, preferably, one or two tooth surface angles of at least one tooth, preferably multiple or all teeth in the first group of teeth, i.e., fine teeth, are gentler than the corresponding tooth surface angles of at least one tooth, preferably multiple or all teeth in the second group of teeth, i.e. coarse teeth.

[0071] When the chain runs undesirably out of sync on the chain rollers, particularly when one or more inner chain links may engage with the tips of coarse teeth, the above-described embodiment of the tooth face angle on the chain guide rollers facilitates chain resynchronization. This takes into account the fact that finer teeth have a lesser effect on resynchronizing out-of-sync chains than coarse teeth, because finer teeth have almost no contact with the chain links in the out-of-sync state; therefore, the chain generally only needs to passively overcome the finer teeth to return to a synchronized state.

[0072] The present invention also relates to a bicycle rear shift mechanism comprising: a base element that can be connected to the bicycle rear fork end frame, the base element also referred to in the industry as a B-knuckle; a shift element that can move relative to the base element by means of a deflection mechanism, the shift element also referred to in the industry as a P-knuckle; and a chain guide device that is rotatably connected to the shift element, the chain guide device also known as a chain guard or chain guard assembly, having upper and lower chain guide rollers.

[0073] Furthermore, the present invention relates to a bicycle drivetrain comprising at least one front sprocket or chainring, also known as a pinion flywheel, a rear multi-pinion configuration, and a rear shift mechanism having upper and lower chain rollers. The bicycle shift mechanism and the bicycle drivetrain are characterized by chain guide rollers having the aforementioned teeth.

[0074] According to a preferred embodiment of the bicycle drivetrain, the pinion freewheel has at least one pinion with an even number of teeth, which alternately correspond circumferentially to a first or second group of teeth. The first group of teeth consists of narrower teeth, narrower than the spacing between the inner chain plates, and the second group of teeth includes at least one wider tooth. Preferably, the width of one or all of the teeth in the second group is greater than the spacing between the inner chain plates. Therefore, the wider tooth of at least one pinion of the freewheel can only fully penetrate the gap between the outer chain plate links, but cannot fully penetrate the gap between the inner chain plate links.

[0075] Another preferred embodiment of the bicycle drivetrain is characterized in that the rear shift mechanism is a pin-type shift mechanism with a non-tilted or only slightly tilted parallelogram shifting mechanism. Detailed specifications of the geometry and characteristics of this pin-type shift mechanism are provided in the introduction to the specification above.

[0076] Based on the combined action of all components of the bicycle drivetrain described above and below in the accompanying drawings, it will be clear to those skilled in the art that the design of the chain guide roller of the present invention affects the entire bicycle shifting mechanism and the entire bicycle drivetrain. In particular, the improved shifting accuracy in both the inward and outward directions achieved by the chain guide roller of the present invention, and based on better and more uniform chain guidance, enable adjustments and optimizations to other components of the drivetrain, especially the pinion freewheel and the shifting mechanism. This includes determining the dimensions of the shifting mechanism geometry and arranging and positioning the shifting mechanism relative to the bicycle frame or frame fork, which would be impossible to achieve without the chain guide roller of the present invention, or might adversely affect operation and the shifting process.

[0077] Thanks to the chain guide roller of this invention, the shifting characteristics of the pinion flywheel, particularly for shifting in the inward direction, and the shift fork axle shift block grooves can be more pronounced or clearer without causing premature shifting. Also based on the improved chain guiding performance in the chain roller axial direction and the better synchronization performance of the chain roller based on this invention, the entire drivetrain can be designed to be more compact and have more flexible positioning relative to the frame rear fork.

[0078] Therefore, it will be clear to those skilled in the art that the shifting mechanism equipped with the chain guide roller of the present invention, and the bicycle drivetrain equipped with such a shifting mechanism, both on their own and as a matching overall system, bring significant improvements to the structural design of the entire drivetrain and to riding and shifting operations. Attached Figure Description

[0079] The embodiments of the present invention will now be described by way of example with reference to the accompanying drawings. The inventors note that all drawings are based on CAD models of preferred embodiments and are drawn to scale; therefore, possible relationships or dimensions not specifically described can be seen from the drawings.

[0080] In the picture:

[0081] Figure 1 Mountain bikes with a 1x drivetrain, meaning they have a single sprocket, a pinion flywheel, and a rear shift mechanism;

[0082] Figure 2 : Figure 1 The mountain bike shown has a drivetrain including the gear shifting mechanism.

[0083] Figure 3 : Figure 2 The image shown is a rear-view perspective view of the transmission system, including the gear shifting mechanism.

[0084] Figure 4 Similar to Figures 1 to 3 The rear view of the components of the small gear flywheel of the transmission system and the chain guide roller, and schematically showing the chain direction during the shifting process;

[0085] Figure 5 During the inward shift, Figure 4 The side view of the chain guide roller, chain section, and pinion flywheel shown is taken from the outside, with detailed view A and the corresponding view direction.

[0086] Figure 6 During the inward shift, according to Figure 5 Detailed view and view A in the middle Figure 5 An enlarged rear view of the chain guide roller, chain section, and pinion shown.

[0087] Figure 7 During the outward shift, according to Figure 5 Detail A in the middle Figure 5 and Figure 6 Enlarged rear perspective view of the chain guide roller, chain section, and pinion shown;

[0088] Figure 8 : Figures 4 to 7 The rotational side view of the chain guide roller and chain section shown is drawn outside the chain roller, with views A and B.

[0089] Figure 9 During the inward shift, from Figure 8 Viewed from viewpoint A (from above, in relation to the bicycle). Figure 8 The chain guide roller and chain section are shown.

[0090] Figure 10 During the outward shift, from Figure 8 Viewed from view direction B (from the rear of the bicycle). Figure 8 and Figure 9 The chain guide roller and chain section shown, and Figure 5 The pinion pair shown;

[0091] Figure 11 During the inward shift, from Figure 8 Viewed from viewpoint A (from above, in relation to the bicycle). Figures 8 to 10 The chain guide roller and chain section are shown.

[0092] Figure 12 During the outward shift, from Figure 8 Viewed from view direction B (from the rear of the bicycle). Figures 8 to 11 The chain guide roller and chain section shown, and Figure 5 The pinion pair shown;

[0093] Figure 13 : Figures 4 to 12 The chain guide roller shown is connected to a similar chain guide roller. Figures 5 to 12 The chain segment shown and Figure 5 Side view of the pinion pair shown from the outside;

[0094] Figure 14 : Figure 13 Side view of the chain guide roller, chain section, and pinion pair as seen from the inside;

[0095] Figure 15 : Figures 1 to 14 The shown is a perspective view of the chain guide roller from the front, looking towards the inside of the chain guide roller.

[0096] Figure 16 : Figure 15 The shown chain guide roller is viewed from the front towards the outside of the chain guide roller.

[0097] Figure 17 : Figures 4 to 16 The chain guide roller shown is Figure 18 A side view of the cutting plane looking towards the inside of the chain roller;

[0098] Figure 18 : Figure 17 The chain guide roller shown is along Figure 17 A sectional view of the cutting plane in the middle;

[0099] Figure 19 : Figures 4 to 18 A magnified rear view of the chain guide roller shown;

[0100] Figure 20 : Figures 4 to 19 The side view of the chain guide roller shown, viewed from the inside.

[0101] Figure 21 : Figure 20 The side view of the chain guide roller shown from the outside;

[0102] Figure 22 : Figure 20 A magnified partial detail of the chain guide roller shown in Figure A;

[0103] Figure 23 : Figure 21 A magnified partial detail (B) of the chain guide roller shown;

[0104] Figure 24 Another embodiment of the chain guide roller, viewed from the front, corresponds to the inner side of the chain guide roller. Figure 15 A perspective oblique view;

[0105] Figure 25 : Figure 24 The chain guide roller shown is viewed from the front towards the outer side of the chain guide roller, corresponding to... Figure 16 And a partially cut perspective oblique view; and

[0106] Figure 26 : The longitudinal section of the tooth tip Figure 24 and Figure 25 The chain guide roller shown. Detailed Implementation

[0107] Figure 1 The mountain bike 1 is shown, which has a so-called 1x drivetrain 2, namely a drivetrain with a single chainring 3, a rear shift mechanism 4, a multi-spindle freewheel 5, and a chain 6. The drivetrain is located within the area of ​​the rear fork endplate 7, which is connected to the front fork endplate 9 in a rotatable manner via a spring / damper device 8. Unlike... Figure 5 And the following figures, as well as the so-called flat-topped chain shown in part therein, Figure 1 The mountain bike shown is equipped with a traditional chain.

[0108] Figure 2 Show Figure 1 The drivetrain 2 of the mountain bike 1 shown is relative to Figure 1 A magnified view, in which the toothed disc 3 is shown... Figure 2 The rear fork end bracket 7 is shown only schematically.

[0109] Regarding the shifting device 4, it can be seen that the base element 10, which is connected to the rear fork end bracket 7 and is also known in the industry as a B-knuckle, is connected to the shifting element 12, which can move substantially horizontally relative to the base element 10, via a parallelogram-shaped deflection configuration 11. This shifting element is also known in the industry as a P-knuckle. The chain guide device 13, also known as a chain guard configuration or chain guard, is connected to the shifting element 12 in a manner that allows it to deflect about axis P under spring load.

[0110] The chain guide device 13 includes the original chain cover 14 and the lower chain tension roller 15 to accommodate the empty chain strands 6 of the chain 6. E And maintain chain tension. The chain guide device 13 also includes an upper chain guide roller 16 for guiding the chain 6 to the pinion of the pinion flywheel 5.

[0111] The upper chain guide roller 16 is also used to allow the chain 6 to overflow between the chain guide roller 16 and the pinion of the flywheel 5 during gear shifting. T The small gear flywheel 5 is shifted between different small gears.

[0112] In recent years, Figure 1 or Figure 2 The 1x drivetrain shown is a drivetrain consisting of a single sprocket and a large gear ratio cassette, commonly used in high-quality mountain bikes. These cassette cassettes typically have a gear ratio between the maximum and minimum gear ratios, for example, 400% or higher.

[0113] In order to keep the operating force low when switching between different gear ratios of the flywheel, a shifting mechanism with a non-tilting or only slightly tilted parallelogram mechanism is particularly used when combined with such flywheels. Such shifting mechanisms are disclosed, for example, in patents EP2641823B1 and EP3388324A3, as detailed above in the introduction to the specification. This shifting mechanism is also provided in… Figure 1 or Figure 2 In the transmission system shown.

[0114] In order to maintain a suitable so-called chain clearance C in all different pinion flywheel transmission ratios G (The radial distance between the chain guide roller 16 and the pinion of the small gear flywheel 5) Figure 2 C with black bar G As shown), in this type of shifting mechanism 4, the axis A of the chain guide roller 16 of the shifting mechanism 4 is... P The gap E between the deflection shaft P of the P steering knuckle is significantly larger than that of a conventional shifting mechanism with an inclined parallelogram mechanism.

[0115] One consequence of this is that the chain gap CG In this type of shift mechanism 4, the correlation with chain length and other factors is significantly enhanced, such as the possible spring movement system of the rear suspension 8, and the wear of the chain 6 over time. Therefore, compared to conventional shift mechanisms with an inclined parallelogram mechanism, this type of shift mechanism 4 with a non-inclined or slightly inclined parallelogram mechanism 11 results in a greater correlation between the drivetrain and chain clearance C. G The response to the size is generally much more sensitive.

[0116] Therefore, in the shifting mechanism 4 with a parallelogram mechanism 11 that is not tilted or slightly tilted, the chain gap C G It occupies a central position in the function of the shifting system and transmission system. Its main responsibilities include: ensuring the proper functioning of the molded components for shifting and pushing (see...). Figure 5 The chain 6 is properly applied in the area of ​​the shift fork shaft groove of the pinion of the ring gear 5, so that the chain 6 can be switched in the dedicated rotation position of the 5 or pushed away in the non-dedicated rotation position of the 5, and the components of the transmission system are generally prevented from being damaged by poor shifting quality or collision.

[0117] In addition, the chain gap C G Similarly, the chain segment 6 that overflows between the chain guide roller 16 and the pinion flywheel 5, which is currently engaged with the pinion S2 of the chain 6. T Length L s It has an impact. However, during actual gear shifting, the overflowing chain segment 6... T The shifting element 12 of the shifting mechanism is generally parallel to the rear axle A. R The shifting direction and shifting position have a greater impact.

[0118] In this regard, such as Figure 2 The chain segment 6 shown is the section that overflows between the chain guide roller 16 and the second gear S2. T Having a length L s When chain 6 switches to the second gear S2 during riding, there is an overflow of chain segment 6. T The length L s .

[0119] like Figure 2 As shown, for example, when shifting from the second pinion S2 to the third pinion S3, specifically at the start of the shift, i.e., in the area 6 where the chain 6 engages with the pinion flywheel. i Initially, while still fully engaged with the second gear S2, there was an overflow of chain segment 6. T Approximately the same length L So ≈L s .

[0120] However, during the corresponding inward shift, the overflowing chain segment 6 Ti The length is much shorter than that of a normal chain during operation and when shifting gears outwards, which is evident in... Figure 2 In this situation, the chain segment 6, which is already on the largest pinion S1 immediately after the outward shift begins, overflows. Ti dotted curve 6 Ti As shown.

[0121] To better illustrate this relationship with the shifting process of shifting mechanism 4, Figure 3 The main geometric dimensions are shown again in the perspective view of the transmission system 2. It can be seen that the chain 6 first switches to the second pinion S2, thereby creating a structurally predetermined chain gap C between the chain guide roller 16 and the pinion S2. G Chain gap C G Together with the spatial relative position of the chain guide roller 16 and the pinion S2, they form the chain overflow section 6 between the chain guide roller 16 and the pinion S2. T Length L s .

[0122] During the outward shift process S o Initially, the shifting element 12 of the shifting mechanism 4 is roughly parallel to the rear axle A. R Move outwards, horizontally to the right as shown in the diagram, until the chain guide roller 16 is just below the next smaller gear S3 in the vertical direction, at which point the overflowing chain segment 6... T The length L s (as length L) So The overall structure remains largely unchanged. The next smaller gear... Figure 3 The point position 16 of the chain guide roller 16 o As shown.

[0123] During the outward shift process S o In the middle, the overflowing chain segment 6 To ≈6 T The length L So ≈L s The reason why it initially remains approximately unchanged is that during the outward shift process S o Initially, the chain segment 6 on the flywheel i It continues to run on the pinion S2 that is about to leave, until it reaches the groove of the outward shift fork shaft with the corresponding shift tooth on the same pinion S2, thereby overflowing the chain segment 6. T Start switching to target pinion S3 (see Figure 7 However, therefore, if segment 6 of chain 6 is on the pinion flywheel 5... iIt is still running entirely on the pinion S2 that is about to leave, while the chain guide roller 16 is already in the target shift position 16. o So, for S to correctly begin the outward shifting process o The length L is of paramount importance. So ≈L s and overflowing chain segment 6 To ≈6 T The direction.

[0124] But in the opposite case, that is, from the second large gear S2 to the largest small gear S1, in Figure 3 The inward shifting process from left to right (S) i In the middle, as already addressed in the previous text Figure 2 As explained, Figure 3 The diagram further illustrates the overflowing chain segments as dots. (6) Ti It already has a significantly shorter length L at the start of gear shifting. Si To perform this inward shifting process, the generally horizontally movable shifting element 12 moves the upper chain guide roller 16 to the position also shown as a dot 16. i .

[0125] This relates to the following situation: when shifting inwards (S) i At that time, the overflow of chain segment 6 of chain 6 Ti At the start of shifting, its inner edge is already pressed against the outer end face of the larger pinion S1, and it slides there lightly until it reaches the matching outward shift fork block groove on the target pinion S1. Subsequently, the overflowing chain segment 6 Ti Jump-to-the-target pinion S1 (see Figure 5 and Figure 6 ).

[0126] In other words, during the inward shift process S i With the outward shift process S o One point to note regarding the differences is that when shifting inwards (S...) i At that time, the overflowing chain segment 6 Ti Always held in place by the shift fork shaft paddle groove on the larger target pinion, therefore, the typically relatively short overflow chain segment 6 Ti During the inward shift process S i The middle part plays a role, while in the outward shifting process S o In the middle, the overflowing chain segment 6 To Interacting with the shift fork shaft paddle groove on the pinion to be disengaged, therefore, it is typically a relatively long overflow chain segment 6. To During the outward shift process S o This plays a role. Overall, due to the inward shifting S...i Time gap C G The chain 6 and pinion flywheel 5 in the prior art are significantly shorter than those used for outward shifting S. o It makes shifting gears easier.

[0127] Figure 4 These relationships are illustrated schematically again. A portion of the pinion flywheel 5, the upper chain guide roller 16, and (highly schematically shown in double lines) the pinion S can be seen. 2' 6. Overflowing chain segments during normal straight chain operation. T Starting from the pinion S 2' Inward shift S i To larger gear S 1' At the time of the target pinion S 1' Chain section 6 overflowing between chain guide roller 16 Ti , and in the small gear S 2' Shift outwards to the smaller gear S 3' Overflowing chain segment 6 To .

[0128] As stated in the introduction to the instruction manual and as... Figures 1 to 3 As shown, for the reasons mentioned in Publication EP2641823B1, the shifting mechanism 4 does not have an inclined parallelogram mechanism, which causes the chain guide device 16 to immediately follow during shifting. Figure 4 The tooth tip profile 20 is shown in dashed lines. Specifically, the shift mechanism 4 is a pin-type shift mechanism with a non-tilted or only slightly tilted shift parallelogram mechanism 11; therefore, during inward shifts S... i And outward shifting S o At that time, the upper chain guide roller 16 moves generally horizontally first through the shifting parallelogram mechanism 11.

[0129] In this type of shifting mechanism 4 with a parallelogram mechanism 11 that is not tilted or only slightly tilted, as described above, due to the axis A of the chain guide roller 16 P The gap E between the chain guard 13 and the deflection shaft P is relatively large, and only when the pinion flywheel 5 rotates further, until the area 6 of the chain 6 meshes with the pinion flywheel 5. i (See also) Figure 2 Completely aligned with the larger target pinion S1, S 1' Or with smaller target pinions S3, S 3' When engaged, the vertical component of the chain guide roller 16 following the tooth tip profile 20 of the pinion flywheel 5 is gradually generated.

[0130] The reason is that the inward shifting process S is performed by the shifting mechanism 4, which has a shifting parallelogram mechanism 11 that is not tilted or only slightly tilted. i At that time, the chain guide roller 16 moves to position 16 via the shifting mechanism 4. i Afterwards, the chain cover 13 gradually overflows into the larger gears S1 and S2. 1' Chain 6 deflects counterclockwise around its deflection axis P; therefore, chain 6 only deflects when it has already engaged with the larger gears S1 and S2. 1' When engaged, the upper chain guide roller 16 begins to vertically follow the conical tooth profile 20 of the pinion flywheel 5. That is, in this type of shifting mechanism 4, the pinions S2 and S3 only begin to follow the chain 6 completely before it disengages. 2' And completely within the larger gears S1 and S 1' When the chain guard 11 moves upward, it fully deflects, causing the chain guide roller 16 to follow vertically in the desired manner, and the chain guide roller 16 interacts with the larger gears S1 and S2. 1' The desired chain gap C is generated between them. G .

[0131] Opposite outward shifting process S o The same applies to the chain guide roller 16, where the shifting mechanism 4 causes the chain guide roller 16 to initially move generally horizontally to the right or outward into position 16. o And only after the pinion flywheel 5 rotates further, and with the complete deflection of the chain guard 11, in the area 6 where the chain 6 meshes with the pinion flywheel... i (See also) Figure 2 Completely disengaged from the starting pinion S2, S 2' And entirely within the smaller gears S3 and S 3' When the chain guide roller 16 is running, the vertical component following the tooth tip profile 20 of the pinion flywheel 5 is gradually generated.

[0132] In other words, during the outward shifting process S o In the middle, only when chain 6 is already connected to smaller gears S3 and S... 3' When engaged, the chain cover 13 gradually overflows to the smaller gears S3 and S4. 3' The chain 6 deflects clockwise around its deflection axis P, and then the upper chain guide roller 16 follows vertically along the conical tooth profile 20 of the pinion flywheel 5.

[0133] Therefore, in the aforementioned shifting mechanism 4 with a non-tilted or only slightly tilted shifting parallelogram mechanism 11, during the shifting process, only the deflection implemented by the chain guard 13 after the shifting process begins will change the chain gap C. G That is, the upper chain guide roller 16 and the corresponding target pinion S1, S2 1'Or S3, S 3' The spacing between them.

[0134] Reference Figure 4 This also indicates that during the inward shifting process, S i In the middle, the chain guide roller 16 has already moved horizontally inward into position 16 before the chain cover 13 deflects, and further before the chain gap adjustment is carried out during the gear shifting process. i Therefore, during the inward shifting process S i Initially, the chain guide rollers 16 are positioned at a small radial spacing C Gi Overflowing chain segment 6 Ti Pressing down on the smaller gear.

[0135] Therefore, from position 16 i The chain guide roller 16, which shifts gears from top to inside, overflows into the larger gear S. 1' The length is L Si Chain segment 6 Ti (See also) Figure 2 and Figure 3 The length of the chain guide roller 16 is much smaller than that of the pinion S to be disengaged. 2' The length between them is L s Chain segment 6 T The length.

[0136] Shifting outwards (S) o At that time, the shifting mechanism 4 causes the chain guide roller 16 to move generally horizontally to the right or outward. Figure 4 Position 16 shown o As mentioned above, the vertical component of the chain guide roller 16 following the tooth tip profile 20 of the pinion flywheel 5 is only generated after the pinion flywheel 5 rotates further.

[0137] Therefore, from position 16 o The chain guide roller 16, which shifts gears from top to outside, overflows into the smaller gear S. 3' The length is L So Chain segment 6 To The length is approximately equal to that previously at the chain guide roller 16 and the pinion S to be disengaged. 2' The length between them is L s Chain segment 6 T The length.

[0138] In other words, this means shifting outwards (S). o Chain gap C Go And the overflowing chain segment 6 To The length is much greater than the inward shift S i Chain gap C GiAnd the overflowing chain segment 6 Ti The length.

[0139] In the current so-called indexing bicycle shifting device, the chain guard 13 and the chain guide roller 16 are in the axial direction A R The horizontal movement is generally carried out with a constant tooth pitch corresponding to the spacing of the pinion of the flywheel 5.

[0140] Therefore, in each gear shift, the constant absolute amount S of the axial deflection of the gear shift mechanism 4, combined with the inward gear shift process S, i The chain gap C is significantly smaller. Gi Or the outward shifting process S i The chain segment with significantly smaller overflow in the middle 6 Ti Compared to the length during the outward shifting process, S o The chain gap C is significantly larger in the middle. Go Or during the outward shift process S o The chain segment 6 with a significantly larger overflow To The length, based on trigonometric relationships, during inward shifting S... i For the overflowing chain segment 6 Ti Forming an oblique angle λ i The angle is much larger than the outward shift S. o Overflowing chain segment 6 To The oblique angle λ o .

[0141] Therefore, using the existing upper chain guide roller, which is typically constructed symmetrically with respect to the center plane in the axial direction, it thus has the same transverse chain guiding performance along the chain roller axial direction and inward shifting S i And outward shifting S o When they have the same oblique angle λ i =λ o With the upper chain guide roller in place, shift gears inward (S). i The overflow chain segment 6 is significantly shorter. Ti In this overflowing chain segment 6 Ti The oblique angle λ i =λ o Chain segment L that causes overflow if it remains unchanged Si The increased axial or horizontal displacement along the chain roller leads to the action of the chain roller on the larger gears S1 and S2. 1' The shifting function is greatly enhanced and may be earlier (see Figure 6 The reason is that, in existing technology, the chain rollers are not allowed to overflow from the chain segment 6. Ti Features inward shift S i The larger bevel angle λ that appears or is needed at that time iInstead, it forces the overflow of chain segment 6. Ti Entering a straighter path, similar to an outer bevel, results in a path towards a larger gear S. 1' The gear shifting process is brought forward.

[0142] Conversely, in the overflowing chain segment 6 To The bevel angle λ of the axially symmetrical chain guide roller in the prior art o =λ i While remaining unchanged, shifting inwards (S) i Compared to the outward shifting process, S o The significantly longer overflow chain segment 6 To This leads to shifting inwards (S) i In comparison, the overflowing chain segment 6 To The axial or horizontal displacement of the chain roller decreases, resulting in a reduction in the inward shifting S. i Compared to the reduced shifting effect and shifting towards smaller gears S3 and S... 3' The shifting process is relatively late (see Figure 7 ).

[0143] In other words, among the known chain guide rollers, the outer oblique angle λ o Consistent inner oblique angle λ i And the resulting relatively short overflow chain segment L Si Towards a larger goal, small gears S1 and S 1' The large displacement in the direction caused the overflow of the chain segment L. Si With the aid of known chain guide rollers, the larger target pinions S1 and S2 are engaged earlier and more intensely. 1' outer surface 31 F (See also) Figure 6 Friction on the surface causes undesirable impact on the gears S1 and S2, leading to friction on the smaller gears. 1' The shifting process occurs at the larger gears S1 and S2. 1' It does not occur earlier than the position set for gear shifting.

[0144] The multi-layered pinion flywheel has a specially designed groove, usually in the form of a shift fork shaft paddle groove, and a dedicated upper shifting tooth, for inward shifting S gears. o At that time, chain 6 should extend from the smaller pinions S2 and S3 along a precisely defined and, in particular, approximately tangential path between the two pinions on the groove and the upper moving tooth. 2' Move up to the larger gears S1 and S 1' However, to prevent incorrect gear shifting, chain 6 must be moved laterally along the larger and smaller gears S1 and S2. 1'All other teeth slide away until chain 6 reaches one or more gears S1, S2 in the shift fork shaft shift block groove. 1' One of the upward-moving teeth.

[0145] However, the greater the gear shift jump, the smaller the chain gap C at the start of the shift. Gi And the overflowing chain segment 6 Ti The smaller the length L Si And larger pinions S1 and S 1' Along the larger pinion S1, S 1' The more teeth between the grooves of the shift fork shaft paddles or the upward-moving teeth distributed around the perimeter, the better the shifting speed when shifting inwards (S). i At the time when the larger pinion S1, S 1' The greater the difficulty, the more difficult it is to push the chain 6 horizontally on the teeth that are not used for upshifting.

[0146] There is a particular challenge in pushing off chain 6 in the following situations: especially in a pinion flywheel with coarse and fine teeth, chain 6 is on an odd number of so-called transition pinions 30, and must be switched synchronously in a defined longitudinal orientation to the pinion with coarse and fine teeth T. W T N The next larger even-numbered pinion 31, such that the finer teeth T of the larger pinion 30 N The coarse teeth of the smaller gear 31 mesh with the inner link IL, and mesh with the outer link OL.

[0085] and DE102015016767A1 Figure 5 For example, this shifting situation is revealed, and is also described below. Figure 5 As shown in the image.

[0147] Figure 5 The inward shifting process S is shown. i During this period, the two pinions 30 and 31 of the pinion flywheel 5 are as follows: the smaller pinion 30 is an odd-numbered transition pinion with 21 teeth, and the larger pinion 31 is a T-shaped pinion with coarse and fine teeth. W T N The even-numbered pinions. Also visible are the upper chain guide roller 16 (not shown) of the shift mechanism 4, and the chain segment 6 overflowing between the chain guide roller 16 and the odd-numbered pinions 30. Ti .

[0148] Figure 5 The chain 6 shown in the following figures refers to a so-called flat-top chain, which is asymmetrical in its vertical orientation when mounted on a bicycle. Vertical asymmetry means that, with the load on the chain 6 strand 6... L For example (see) Figure 2Ideally, all links should have a profile that is as flat or straight as possible on the top side, while the links should have a common concave profile on the bottom side. The advantage of this type of flat-top chain is that it has greater stability without changing or even improving its running and shifting performance, because the direct orientation of the link surfaces increases the cross-sectional area of ​​the links.

[0149] In this invention, the tooth geometry of the chain guide roller 16 is preferably as shown in the figure. Figure 5 And match the flat-top chain of chain 6 shown in the following figures, so that it is inward according to the shift (see Figure 6 ) or outward (see Figure 7 (From the overflowing chain segment 6) Ti The desired different chain 6 bevel angles are achieved when the chain leaves the chain guide roller 16.

[0150] However, the tooth geometry of the chain guide roller 16 can also be matched with conventional chains that do not have vertical asymmetry. Similarly, the chain guide roller 16 optimized for interaction with flat-top chains can be used with conventional chains that do not have vertical asymmetry.

[0151] During inward shifting, also in the overflowing chain section 6 Ti The chain 6 angle produced when leaving the chain guide roller 16 is different from that when shifting outwards; however, depending on the specific geometry, especially according to the relative position of the chain links... Figure 2 The load section 6 shown L The upper limit of the radius of curvature will vary, and the difference may be smaller or larger than that of using a flat-top link.

[0152] Therefore, preferably, the chain guide roller 16 should match the geometry of the chain link 6 used, or the chain used with the chain guide roller 16, preferably a flat-top chain, should be mounted on the bicycle.

[0153] exist Figure 5 In the even-numbered pinion 31 with coarse and fine teeth shown, the coarse tooth T W Marked with black dots, these coarse teeth, due to their axial thickness on the pinion, can only match or mesh with the gap between the chain plates of the outer link LO, but cannot match or mesh with the gap between the chain plates of the inner link LI. The reference numerals LO and LI are directly marked on the corresponding links in the attached figures.

[0154] The smaller odd-numbered transition pinion 30 has only fine teeth T N Because each tooth of the transition pinion 30 alternately meshes with the inner link LI and the outer link LO in each rotation due to its odd number of teeth. Figure 5 Overflowing chain segment 6 TThe meshing with the transition pinion 30 during the current rotation of the pinion pair 30, 31 results in the outer chain plate link OL meshing with the circled teeth of the transition pinion 30.

[0155] The larger even-numbered pinion 31 has a chain segment 6 at three equidistant positions for overflow during inward shifting. Ti The inward shift fork shaft shift block groove L moves from the smaller odd-numbered pinion 30 to the larger even-numbered pinion 31. C1 L C2 L C3 Eight teeth are provided between these spaced-out positions. The inward shift fork shaft lever groove L... C Including the upward slope R C1 R C2 R C3 , its in Figure 5 6th chain segment that was overflowed T Partially covered, but its shape can also be seen in... Figure 13 Seen in the middle. Upward slope R C A chain segment 6 is provided on the outer end face of the larger gear 31, and is allowed to overflow. T Shift inwards (S) i Initial axial displacement is achieved via shift mechanism 4 (see reference). Figure 3 ).

[0156] The three inward shift fork shaft grooves L of the larger gear 31 C1 L C2 L C3 Each of them has a shift tooth or receiving tooth T C1 -T C3 It has a special bevel and chamfer, and the corresponding receiving tooth T C1 -T C3 With the help of these bevels and chamfers and the overflowing chain segment 6 T The outer chain plate links mesh. Therefore, the receiving tooth T C For the larger gear 31 and the overflow chain segment 6 T The first tooth that engages in the gap between the middle of the chain plate.

[0157] exist Figure 5 In the case shown, the overflowing chain segment 6 at the bottom of the diagram... Ti Just through the receiving tooth T at that location C1 (The receiving tooth is in) Figure 5 6th chain segment that was overflowed Ti The inward shift fork shaft groove L (covered by the outer chain plate link OL) C1 And at the same time, the chain guide roller 16 deflects outward by a degree S through the shifting mechanism 4 (see reference). Figure 4 This initiates the inward shifting process. i However, the one at the bottom of the diagram has an upward slope R at that location. C1 and receiving tooth T C1 Shift fork shaft paddle groove L C1 It was just missed, therefore, the overflowing chain segment 6 Ti It is currently impossible to move up to the larger gear 31, up to the overflowing chain segment 6. Ti As the small flywheel 5 rotates further D W The middle and next matching shift fork shaft paddle groove L C An encounter.

[0158] Although at one-third of the rotation of the small gear flywheel D W Subsequently, there is an upward slope R at this location. C2 and receiving tooth T C2 The next shift fork shaft paddle groove L C2 Reaching the overflowing chain segment 6 Ti This point is Figure 5 The overflow chain segment 6 is shown again after being rotated 120°. Ti 'As shown.' However, it is still impossible to find the L-shaped groove in the shift fork shaft. C2 The gear shifting process is being carried out, and the overflow chain segment 6 Ti' First, it must be pushed laterally outward by the larger gear 31 (see...) Figure 6 The reason is that if the overflowing chain segment 6... Ti' At this location, by means of the upward slope R at that point. C2 and receiving tooth T C2 Shift fork shaft paddle groove L C2 When the chain moves upwards to a larger gear 31, it will cause the chain 6 to run asynchronously on the even-numbered larger gears 31. From position 6... Ti' The shift position or shift fork shaft paddle groove L on the top C2 Within the area, it can be seen that the inner chain plate link IL connects with the coarse tooth T of the larger gear 31 at that location. C2 Upon meeting, the outer link plate link LO correspondingly meets the fine teeth of the larger gear 31.

[0159] Of course, chain 6 has coarse and fine teeth T W T N The asynchronous operation on the even-numbered, larger gear 31 is undesirable because, in this case, the inner link IL of chain 6 is engaged with the coarse gear T. W On the tip of the tooth, this could cause a break in the torque transmission from chain 6 to pinion flywheel 5, resulting in a potentially dangerous situation or damage to the transmission system 2.

[0160] In other words, Figure 5 The overflowing chain segment 6 is shown. Ti' It is still impossible to have an upward slope R at that location. C2 and receiving tooth T C2 Shift fork shaft paddle groove L C2 The section moves upward to the larger gear 31, while the overflowing chain segment 6... Ti It is still necessary to use the outer end face 31 of the larger gear 31 F (See also) Figure 6 dotted line 31 F The upward sliding motion is pushed away by the pinion 31 until the pinion flywheel 5 rotates further. W Arrival Figure 5 The upper left has an upward slope R at that location. C3 and receiving tooth T C3 The third shift fork shaft paddle groove L C3 .

[0161] In other words, depending on the specific pinion size, there may only be a few suitable rotation angle positions of the flywheel 5 per revolution for the correct shifting process, or, depending on the situation, only one suitable rotation angle position, or as in... Figure 5 As shown in the example, there are two shift fork shaft paddle grooves L at this location. C1 or L C3 The appropriate rotation angle position is provided for the corresponding upward moving tooth T. C1 or T C3 It encounters link OL of the outer link plate of chain 6.

[0162] Therefore, in T with coarse and fine teeth W T N In the flywheel, even if the larger gear 31 includes multiple gears each having a corresponding upward moving tooth T C Inward shift fork shaft paddle groove L C These inward shift fork shaft paddle grooves have a generally even number of teeth pitch due to the alternation of coarse and fine teeth, allowing the chain 6 to still start from the odd number of transition pinions 30, ideally only every other upward shift tooth T. C The chain 6, which runs on the odd-numbered transition pinion 30, moves up to the even-numbered smaller gear because it only moves up to the even-numbered smaller gear T every other tooth. C As preset, the outer link plate link OL and the upper moving tooth T C An encounter.

[0163] Therefore, in relation to Figure 5 In the same scenario, chain 6 must be pushed away on a large number of teeth of the larger gear 31. Figure 5 In the case shown, that is, in the section 31 that includes two-thirds of the circumference of the larger gear 31.S All the teeth inside, including this section 31 S The receiving tooth T included C2 The upper part is pushed away, so it won't be in the undesirable position L. C2 Moving the gear 6 to a larger pinion 31 could lead to uneven shifting, increased load on the transmission system, unwanted noise, and could cause the chain 6 to slip on the pinion flywheel 5, thus adversely affecting riding safety.

[0164] Figure 6 The inward shifting process S is shown. i In the middle, the chain segment 6 overflows from the odd-numbered transition pinion or starting pinion 30 to the even-numbered larger pinion 31. Ti The process of being pushed apart. It can be seen that the inner link in the left image is on the end surface 31 of the larger gear 31. F It slides upwards and is pushed away by this small gear, meaning it has not yet engaged with the teeth of the larger gear 31. For this reason, the overflowing chain segment 6... Ti Need to adopt Figure 6 The S-shaped path indicated by the dashed line in the middle is 6. TiC And with a relatively large oblique angle λ i (See also) Figure 4 The chain overflows from the chain guide roller 16 to the pinion flywheel 5. If the overflowing chain segment 6 is forced... Ti If a straight line with minimal curvature is used, then the overflow chain segment 6... Ti Maybe not as Figure 5 As shown along the entire arc segment 31 S Instead of being pushed away by the teeth of the larger gear 31, it may move to the larger gear 31 prematurely and possibly out of sync, unintendedly.

[0165] These relationships are Figures 1 to 3 The shift mechanism 4, which has a non-tilted or only slightly tilted shift parallelogram mechanism 11, is particularly important because, as mentioned above, it is important for... Figures 2 to 4 As described, in this type of shifting mechanism, the chain guide roller 16 is in the inward shifting process S of the shifting mechanism 4. i Initially, it moves only horizontally. However, as described, it only begins to move horizontally when chain 6 switches to the larger gears S1 and S2. 1' After 30, the chain guide roller 16 then moves vertically to restore the required chain gap C. G Therefore, as Figures 2 to 4 As shown, the overflowing chain segment 6 Ti Shift inwards (S) i Having a relatively small length L Si .

[0166] Under these conditions, the tooth geometry in the prior art is approximately aligned with the center plane P of the chain guide roller 16. M Mirror symmetry (see) Figure 19 The chain guide roller cannot shift inwards (S). i Ensure that the overflowing chain segment 6 is contained. Ti Pushing aside to implement the normal shifting process, because the chain guide roller in the prior art is symmetrical with respect to the center plane for inward shifting S and outward shifting S. o They have the same chain-guided performance.

[0167] This pair Figure 6 In other words, this means that the overflowing chain segment 6 Ti Unable to utilize the inward shifting S method in existing technology i Chain guide rollers with strong chain guiding performance are used to achieve the required relatively large bevel angle λ. i And the direction with a greater degree of curvature 6 TiC Therefore, it is possible that there are rotation angle positions not designed for this purpose or shift fork shaft paddle grooves L. C2 There is a tendency to move to the smaller gear 31 earlier than expected.

[0168] Therefore, generally speaking, especially in the shift mechanism 4 with the shift parallelogram mechanism 11 that is not tilted or only slightly tilted, and more often in such shift mechanisms 4 with coarse and fine gears T W T N In the combination of the small gear flywheel 5, during the inward shifting process S i In the middle, the expected overflow chain segment 6 Ti The oblique angle λ i Larger, therefore, it is desirable that the axial chain guiding performance of the chain guide roller 16 be relatively weak, so that the overflow chain segment 6 Ti It will not move to the larger gear S1, S where the teeth were not originally designed for this purpose. 1' 30, but as Figure 5 31 S As shown, all teeth not designed for upward movement are pushed away as effectively as possible.

[0169] However, at the same time, the chain guide roller 16 ensures that during outward gear shifting S... o At times, such as Figure 5 As shown, the overflowing chain segment 6 To Based on the foregoing, especially... Figure 3 and Figure 4 Regarding the described overflow chain segment 6 To The chain segment 6 is deflected to a sufficiently large extent by a greater length, thus causing the overflow chain segment 6 to deflect to a greater extent. To The lower tooth T of the larger gear 31D One of them is grasped and pushed outward laterally in a preset manner, thereby being guided to a smaller gear 30 at a preset shift position.

[0170] Figure 7 This situation is illustrated in the chain segment 6 where it overflows outwards. To The expected and such Figure 7 The relatively small bevel angle λ shown has also been achieved. o In particular, see also Figure 4 As can be seen from the figure, different oblique angles λ can be obtained by referring to the corresponding instruction manual. i and λ o , and such Figures 2 to 5 As shown, the outward overflow of the chain segment corresponds to the S segment during inward shifting. i Overflowing chain segment 6 Ti Length L Si Compared to having a relatively large length L So .

[0171] The chain guide roller 16 of the present invention satisfies the above requirements, namely, during outward gear shift S o The chain has strong lateral chain guiding performance along the chain roller axis, and relatively strong performance during inward shifting. i It has relatively weak lateral chain guiding performance.

[0172] In the embodiment of the chain guide roller 16 shown in the accompanying drawings, this is achieved in such a way that the teeth of the chain guide roller 16 have an inner guiding region A. Gi and outer guidance area A Go The inner guiding region A Gi Relative to outer guide region A Go Having a center plane P relative to the chain guide roller 16 M The thickness dimension T is reduced locally. T (See also) Figure 19 ).from Figure 6 and Figure 7 It can already be seen that this type of inner guiding region A Gi and outer guidance area A Go .

[0173] Combination Figure 6 It can be seen that although the chain guide roller 16 has switched horizontally inward, this is mainly due to the coarse teeth T of the chain guide roller 16. W1 Inner guiding area A Gi Slight lateral guidance of the outer link plate link OL1, overflowing chain segment 6 Ti L Si The marked portion can use the relatively large bevel angle λ required above. iThe obvious S-shaped trend 6 TiC .

[0174] Figures 8 to 12 Inward shifting is shown again in a different view. Figure 9 and Figure 10 ) and shifting gears outwards ( Figure 11 and Figure 12 The chain guide roller 16 and the chain segment 6 overflowing between the chain guide roller 16 and the pinion flywheel 5. Ti Or 6 To .

[0175] Figure 8 The chain guide roller 16 and the chain segment 6 overflowing from the chain guide roller 16 to the pinion flywheel 5 are shown in a view from the outside towards the chain guide roller 16. T D W This again indicates normal operation, that is Figure 1 or Figure 2 The rotation direction of the chain guide roller 16 during the operation of the transmission system 2 shown. The chain guide roller 16 in... Figures 8 to 12 The tooth T is marked with a dashed ellipse in the middle. W1 This refers to the coarse tooth T of the chain guide roller 16 equipped with X-Sync teeth, which are alternating coarse and fine teeth. W .

[0176] Figure 9 and Figure 10 It is shown that, from Figure 8 The two views A and B shown illustrate the overflow of chain segment 6 when shifting from the smaller pinion 30 to the larger pinion 31. Ti . Figure 11 and Figure 12 Correspondingly, the overflow chain segment 6 is shown when shifting outward from the larger pinion 31 to the smaller pinion 30. To .

[0177] Similar to Figure 6 From the ground Figure 9 and Figure 10 It can be seen that the chain guide roller 16 is shifting inwards (S) i As expected, it has relatively weak axial chain guiding properties, thus allowing for overflow of chain segments 6. Ti With a relatively large oblique angle λ i This prevents overflow from the chain segment 6. Ti Move to the smaller gear 31 earlier.

[0178] Correspondingly, similar to Figure 7 From the ground Figure 11 and Figure 12 It can be seen that the chain guide roller 16 is shifting outwards at point S.o It possesses the desired relatively strong axial chain guiding performance, thus resulting in better outward shifting S... o Overflowing chain segment 6 Ti The oblique angle λ o Relatively large.

[0179] Especially as Figure 9 and Figure 11 As shown, this is achieved in the following way: the teeth of the chain guide roller 16 have an inner guide area A. Gi and outer guidance area A Go The inner guiding region A Gi Relative to outer guide region A Go Having a center plane P relative to the chain guide roller 16 M The thickness dimension T is reduced locally. T (See also) Figure 19 ).like Figure 6 as well as Figure 9 and Figure 10 As shown, inner guiding region A Gi The reduced thickness dimension makes the bevel angle λ i The expected increase is when shifting inwards.

[0180] Figure 4 , Figures 6 to 12 The same oblique angle λ i , λ o The reason why the sizes appear different is because, as seen in the attached diagram, the oblique angle λ... i , λ o The directions and perspectives are different.

[0181] Figure 13 Again, shown in a magnified close-up view. Figure 5 As shown, during the inward shift, the two pinions 30 and 31 of the small gear flywheel 5 can also be seen. The chain guide roller 16 of the shift mechanism 4 (not shown) and the chain segment 6 overflowing between the chain guide roller 16 and the smaller pinion 30 can also be seen. Ti . Figure 14 This is shown as a view from the back, that is, from the inside. Figure 13 The situation is shown below.

[0182] dashed ellipse L C1 Corresponding to Figure 5 The dashed ellipse shown, and the inward shift fork shaft groove L of the larger gear 31 marked therein. C1 The area in which the shift fork shaft paddle recess specifically includes an upward ramp RC1 formed by a groove in the end-side front surface of the pinion 31 and a corresponding receiving tooth T. C1 Receiver T C1It is the process of the larger and smaller gears 31 shifting inwards. i 6th segment of the chain with overflow Ti The first tooth that engages in the gap between the chain links and the chain plates.

[0183] Due to the chain guide roller 16 and the overflowing chain section 6 Ti And pinion 30, 31 in Figure 13 and Figure 14 In the process of shifting gears inward S i In such cases, Figure 6 As shown, chain links IL and OL are based on the chain guide roller 16 (see reference) which has been horizontally moved into the plane of the larger and smaller gears 31 by the shifting mechanism 4. Figure 4 Position 16 i The contact surface F between the chain plate and the pinion teeth of pinions 30 and 31 is laterally located. C1 F C2 F C3 Friction within the area (see) Figure 6 The overflowing chain segment 6 is shown. Ti On the outer surface 31 of the larger gear 31 F Frictional sliding on the surface, and on the contact surface F C4 Within the area where the outer chain plate OL abuts against the chain guide roller 16, the coarse tooth T W1 inner chamfer C S1i Friction between them.

[0184] Chain segment 6 based on overflow Ti In the example of the inward shifting process shown, the frictional processes of chain links IL, OL relative to the teeth of pinion pair 30 or relative to the teeth of chain guide roller 16 result in the overflow of chain segment 6. Ti At the indicated moment, the tangent 6 between the chain guide roller 16 and the smaller gear 30 was not observed. TiD The extension is based on these frictional processes and the forces generated in the process along the radial direction relative to the chain guide roller 16 or relative to the pinion pairs 30, 31, relative to the tangent 6. TiD It deflects slightly in an S-shape.

[0185] When the chain guide roller 16 and the pinion pairs 30 and 31 further rotate along the working direction D W During rotation, the inner chain plates of links OL1, IL2, and OL2... Figure 13 and Figure 14 The middle finger's right edge and the surface pointing inwards, along with the upward-moving slope R... C1 The corresponding surface and chamfer contact, thus, the overflow chain segment 6 Ti Finally, it moves upward to the larger gear 31. During this process, the receiving gear T...C1 The chain plates mesh between the chain links OL1 on the outer chain plate. Subsequently, as the chain guide roller 16 and the pinions 30 and 31 move further along the working rotation direction D... W During rotation, the overflowing chain segment 6 Ti Alternatively, the chain 6 running on the larger gear 31 may then fully mesh with the larger gear 30.

[0186] Figure 13 and Figure 14 The axial direction A of the chain roller along the chain guide roller 16 of the present invention is also shown again. P (See also) Figure 9 and Figure 11 The guiding performance of transverse chains of different strengths. Figure 13 and Figure 14 The process of shifting gears inward is shown, for example, in... Figure 6 As shown in the image.

[0187] The reason why the chain guiding performance of the chain guide roller 16 has different strengths on the inner and outer sides is primarily due to the fact that the chain guide roller 16, especially the coarse-toothed T... W Guiding area A Gi (inner side) and A Go The design of the (outer) side differs between the inner and outer sides. From Figure 9 and Figure 11 It can also be seen that at least the coarse teeth T of the chain guide roller 16 W Inner guiding area A Gi and outer guidance area A Go At least locally, they have different thickness dimensions, specifically in particular... Figure 13 or Figure 14 Visible chamfered surface C S1i (inner side) and C S1o The size of the (outer) part varies, or relative to the coarse tooth T. W The corresponding end-side tooth surface A T1i (inner side) and A T1o The degree of retraction (on the outer side) varies.

[0188] like Figure 15 and Figure 16 As shown and described in detail below, the outer chamfered surface C S1o and the inner chamfered surface C to a greater extent S1i This design, especially its spatial tilt, makes the coarse-toothed T... W The thickness dimension that is reduced on the inside is A T1i (inner side) and A T1o The tooth root at the (outer) position has not yet been utilized; the reduced thickness dimension is primarily used to weaken the chain guiding performance of the chain guide roller 16 in the chain roller axial direction.

[0189] In other words, this means that in the chain segment 6, which has not yet been overflowed... Ti Gradually separating from the chain guide roller 16, but still fully engaged with the chain guide roller 16 (in Figure 13 and Figure 14 For example, in the case of the outer chain plate link OL0), the chain 6 is axially A on the chain roller. P (See also) Figure 9 and Figure 11 The chain 6 is guided on both the inner and outer sides by chain guide rollers 16 with a transverse chain guiding performance of substantially the same strength and without weakening. Its advantage lies in ensuring reliable guidance of the chain 6 on the chain rollers, especially with X-Sync teeth, i.e., alternating coarse teeth T. W and fine-tooth T N The undesirable lateral movement of the chain 6 on the chain guide roller 16 and the undesirable asynchrony of the chain 6 are reduced in the chain guide roller 16.

[0190] Specifically, the chain guide roller 16 is located in the chain roller axial direction A. P (See also) Figure 9 and Figure 11 The reduced lateral chain guidance performance is only noticeable during inward shifts (S). i The action on the overflowing chain segment 6 only occurs when the outer chain plate link OL gradually separates from the chain guide roller 16. Ti .exist Figure 13 and Figure 14 The point shown refers to the coarse tooth T. W1 The situation there. From Figure 14 It can be seen that, through the outer link plate link OL1, the chain roller gradually approaches the coarse tooth T in the radial direction. W1 Separation and during the separation process, coarse-toothed T W1 inner chamfered surface C S1i How does it achieve its reduced lateral chain guiding performance?

[0191] Similar to Figure 13 and Figure 14 The inward shift S shown i The time point is also in Figure 5 and Figure 6 As shown in the image. Combined with... Figure 5 ,from Figure 6 Similarly, it can be seen how the inner chain plate of the outer chain link OL1 is radially aligned with the coarse tooth T of the chain roller. W1 Separation, resulting in the overflow of chain segment 6 Ti Able to follow Figure 6 The S-shaped path shown is 6 TiC To the outside, or to the right in the diagram, thus preventing premature upshifting to the larger gear 31.

[0192] from Figure 13 and Figure 14 It can also be seen that the fine teeth T of the chain guide roller 16 N A certain implementation method is also adopted, so that the corresponding fine tooth T N1 Inner guiding area C S2i Relative to the outer guide region C S2i Having a center plane P relative to the chain guide roller 16 M (See also) Figure 16 The thickness dimension is reduced at least locally, so that the chain segment 6, which is generally tangentially separated from the chain guide roller 16, Ti A larger bevel angle can be used in the outer direction than in the inner direction.

[0193] In the illustrated embodiment of the chain guide roller 16, this is evident in the fine tooth T. N The following method is used to achieve this: an inclined inner chamfered surface C S2i Larger than the corresponding outer chamfer surface C S2o And toward the center plane P of the chain guide roller 16 M The direction is further recessed. Therefore, relative to the outer chamfered surface C... S2o Inner chamfered surface C S2i This results in the corresponding fine tooth T N1 Thickness dimension T T The area of ​​these chamfered surfaces is reduced (see...). Figure 19 Similarly, it can be obtained from... Figure 15 , Figure 16 and Figure 18 as well as Figures 24 to 26 See these relationships.

[0194] These chamfered surfaces C S2i and C S2o They are also arranged at an angle in space, so that only the corresponding inner chain plate link IL gradually aligns with the fine tooth T in the radial direction of the chain roller. N Separated and thus becoming the chain segment 6 overflowing from the chain guide roller 16 to the pinion flywheel 5 T In some cases, these chamfered surfaces will reduce the corresponding fine tooth T. N The effect is on the thickness of chain 6.

[0195] Figure 15 and Figure 16 Show Figures 4 to 23 The coarse tooth T of the embodiment of the chain guide roller 16 shown W and fine-tooth T N Inner guiding area A Gi C Si and outer guidance area A Go CSo The construction scheme, especially the spatial layout of the corresponding chamfered surfaces.

[0196] Figure 15 Shown from the perspective of looking inwards from the front. Figures 4 to 23 The perspective view of the chain guide roller 16 shown is shown. Figure 16 Shown from the perspective of looking outwards from the front. Figures 4 to 23 A perspective view of the chain guide roller 16 shown.

[0197] First, with coarse-toothed T W1 For example, for coarse-tooth T W1 Inner guiding area A Gi ( Figure 15 How is it relative to coarse tooth T? W1 outer guide area A Go ( Figure 16 At least locally reduced thickness dimension T T (See also) Figure 19 The reduced thickness dimension is used to weaken the coarse teeth T of the chain guide roller 16 on the inner side. W The chain-guided performance.

[0198] It can be seen that the coarse-toothed T W1 Inner guiding area A Gi and outer guidance area A Go These are constructed as prominent ridges, particularly located on the tooth T. W1 inner side A T1i A within or on the outer side T1o Within the region, or separately forming these regions A T1i A T1o .

[0199] It can also be seen that the inner guiding region A Gi Relative to outer guide region A Go Having an imaginary center plane P relative to the chain guide roller 16 M The thickness dimension is reduced at least locally. In the illustrated embodiment of the chain guide roller 16, this is achieved by: coarse teeth T W1 inner side A T1i C with a chamfered surface that is inclined in space S1i Chamfered surface C S1i Arranged in a certain way and oriented on tooth T W1 Up, thus through the chamfered surface C S1i Define a chamfered plane P C1 .

[0200] Chamfered plane P C1 Initially along the axial direction D of the chain guide roller 16A Relative to the center plane P of the chain guide roller 16 M Arranged at an angle α. Through the chamfered plane P. C1 The tilt α defines the chamfered surface C. S1i radial inner boundary edge B B1i Chamfered surface C S1i Adjacent teeth T along the boundary edge W1 inner side A T1i .

[0201] Except along axis D A In addition to the tilt α, in the illustrated embodiment, tooth T W1 Definition of chamfered surface C S1i chamfered plane P C1 Also around the corresponding tooth T W1 chain roller radial line L R Relative to the center plane P of the chain roller M Deflection angle β. This further deflection β results in the chamfered surface C. S1i radial inner boundary edge B B1i Having a working rotation direction D along the chain guide roller 16 W The direction of radial outward increase, and tooth T W1 At least on chamfered surface C S1i The region has the unloaded tooth surface F of the tooth. N The load-bearing tooth surface F of the front tooth L Decreasing thickness W T See this point. Figures 17 to 19 And the corresponding description.

[0202] For clarity, this additional tilt β in Figure 15 The chamfered plane P relative to the tilted angle α C1 As shown, this is further relative to the radial line L of the same relative chain roller. R The correspondingly inclined straight line L' R As shown. If the chamfered plane first circles the radial line L of the chain roller R The deflection angle β is then adjusted along the axial direction D of the chain guide roller 16. A Tilting at an angle α will yield the same result, especially for the chamfered plane P. C1 The same position.

[0203] With a beveled plane C S1i The aforementioned layout and spatial positioning, particularly along the axial direction D of the chain guide roller 16. A Inclined at an angle α and additionally around the radial line L of the corresponding toothed T chain roller. R L' R Relative to the center plane P of the chain roller MIn the case of a deflection angle β, in the embodiment of the chain guide roller 16 mentioned above, it is also possible to deflect the tooth T. W and T N Define other chamfered surfaces.

[0204] This is especially true for the inner chamfered surface C. S2i Its radial inner boundary edge B B2i With fine teeth T N The corresponding end face tooth surface A T2i Relatively speaking. As mentioned earlier regarding chamfered surface C... S1i As described, coarse-toothed T W The radial inner boundary edge B B1o With the corresponding end face tooth surface A T1o Opposite outer chamfered surface C S1o and fine-tooth T N The radial inner boundary edge B B2o The outer chamfered surface C opposite to the corresponding end tooth surface AT2o S2o They are defined, positioned, and arranged at an angle in space in a similar manner.

[0205] Furthermore, in the illustrated embodiment of the chain guide roller 16, coarse teeth T are designed or defined in a similar manner. W Additional inner chamfered surface C S3i .

[0206] Overall, this means that all the inclined chamfered surfaces C of the chain guide roller 16 S1i C S2i C S3i C S1o C S2o radial inner boundary edge B B1i B B2i B B3i B B1o B B2o All have a working rotation direction D along the chain guide roller 16 W The direction of rising radially outwards.

[0207] Furthermore, the chain guide roller 16 is shown in the inner side view. Figure 17 The inner boundary edge B is also shown. B1i B B2i B B3i The radially outward rising direction and the corresponding chamfered surface C of the chain guide roller 16 S1i C S2i C S3i . Figure 17 The text also provides information about the Chinese language and its implications. Figure 18 The cutting surface C in A C B CC The cutting planes AA, BB, and CC are used as the basis, and the coarse tooth T is marked. W and fine-tooth T N Loaded tooth surface F L Non-loaded tooth surface F N The load tooth surface F in the chain guide roller 16 L With non-loaded tooth surface F N The difference between them can also be found in the reference. Figure 5 as well as Figure 13 and Figure 14 .

[0208] This shows that the load tooth surface F in the chain guide roller 16 L Defined as transmitting power along the working rotation direction D of the chain guide roller 16 W The tooth surface that transmits data from chain 6 to chain guide roller 16. Correspondingly, the tooth surface opposite the loaded tooth surface is defined as the unloaded tooth surface F. N .

[0209] Combination Figure 18 The coarse tooth T shown in the cross-sectional view W1 And the fine-toothed T, also shown in cross-section N1 It can be seen that, in combination with the preceding text Figures 15 to 17 The described coarse tooth T W and fine-tooth T N Inner guiding area A Gi and outer guidance area A Go and its spatially inclined inner and outer chamfered surfaces C S1i C S2i C S3i C S1o C S2o The design scheme also resulted in, especially in the inner guide area A Gi and at least the local lateral guidance area A Go At least on the corresponding chamfered surface C S1i C S2i C s3i C S1o C S2o Within the region, there is a load-bearing tooth surface F from tooth T. L Towards its non-loaded tooth surface F N Increasing thickness.

[0210] This also helps to guide the chain segment 6 overflowing from the chain guide roller 16 to the pinion flywheel 5 as evenly and smoothly as possible along the entire width of the teeth T in the circumferential direction of the chain guide roller 16 during the gear shifting process. Ti Or 6 To Because, as Figures 5 to 7 as well as Figure 9 and Figure 11 As shown, the overflowing chain segment 6 Ti Or 6 To The contact radius R of the chain guide roller 16 T The upper part contacts the chain guide roller 16, and the contact radius is along the working rotation direction D. W The load increases obliquely, that is, from the load tooth surface F of the tooth T of the chain guide roller 16. L Towards the non-loaded tooth surface F N Increasing (see also) Figure 22 ).

[0211] Therefore, the chain segment 6 to be removed from the chain guide roller 16 Ti Or 6 To This oblique contact is more advantageous, and the width of the teeth T along the circumferential direction of the chain guide roller 16 is more uniform, because the guide area A Gi A Go The thickness of the chain guide roller 16 and the thickness W of the teeth T used for chain guidance. T (See also) Figure 19 From the unloaded tooth surface F of tooth T N Towards the load-bearing tooth surface F L Decreasing. This also allows for maintaining the oblique angle λ as invariably as possible. i or λ o Overflowing chain segment 6 Ti Or 6 To Uniform lateral guidance of the inner link LI and the outer link LO.

[0212] Figures 19 to 23 The chain guide roller 16, inner and outer guide areas A are shown again. Gi and A Go Chamfered surfaces C, inner and outer sides S1i C S2i C S3i C S1o and C S2o and its boundary edge B B1i B B2i B B3i B B1o and B B2o Compared to coarse and fine teeth T W and T N The corresponding end-side tooth surface A T1i A T2i A T1o A T2o The basic geometric properties.

[0213] exist Figure 22 and Figure 23 In the enlarged detailed view shown, the inner and outer chamfered surfaces C are particularly visible.S1i C S2i C S3i C S1o and C S2o The boundary edge B extending circumferentially inclined along the chain guide roller 16 B1i B B2i B B3i B B1o and B B2o As mentioned above Figure 15 As described, these boundary edges are due to the chamfered surfaces C with spatial inclination angles α and β. S1i C S2i C S3i C S1o and C S2o And thus formed.

[0214] As mentioned above... Figure 6 as well as Figure 13 and Figure 14 As described, chamfered surface C S1i C S2i C S3i C S1o and C S2o This sloping layout and the resulting boundary edge B B1i B B2i B B3i B B1o and B B2o The tilting direction caused the overflow of chain segment 6. T As the chain links gradually leave the chain guide roller 16 (see, for example, see...) Figures 5 to 14 In the chain link OL1) along the chain roller axial direction A P The guidance it receives is weakened evenly.

[0215] Due to the tooth T W and T N The thickness dimension in the inner guide region A Gi Inner and outer guiding areas A Go Compared to a significant reduction, in other words, due to the coarse and fine teeth T W and T N end-side tooth surface A T1i A T2i A T1o A T2o More thorough chamfering on the inside (see) Figure 15 and Figure 16 As described above, this results in a greater overall chain guiding performance of the chain guide roller 16 along the chain roller axial direction A compared to the outer lateral chain guiding performance of the chain guide roller 16. P The lateral chain guiding performance is significantly weakened on the inner side, see reference. Figure 4 and Figures 6 to 14 And the corresponding instruction manual.

[0216] However, as mentioned above, this chain guiding performance, which is weakened on the inside and also weakened to a smaller extent on the outside, only applies to the chain segment 6 that overflows between the chain guide roller 16 and the pinion flywheel 5. Ti Or 6 To The chain links that have been partially separated from the chain guide roller 16, especially refer to Figures 5 to 14 Link OL1 in the chain. Links that still run entirely on the chain guide roller 16 (see, for example, [reference needed]). Figure 13 and Figure 14 Links OL0 and OL1 in the chain are on the outer and inner sides along the axial direction A of the chain roller. P The lateral guidance it receives is relatively complete and has not been weakened.

[0217] Compared to shifting inwards, shifting outwards (especially see...) Figure 7 Similarly, the effect is reduced to a smaller extent on the overflowing chain segment 6. To The chain link that has been partially separated from the chain guide roller 16 (see Figure 7 The chain guiding function of link OL1 is to ensure that, although during outward shifting, the overflowing chain segment 6... To The chain segment 6 should slip off the tooth tip of the chain guide roller 16 as late as possible (corresponding to stronger chain guiding performance), but this slippage should also be done in a uniform and smooth manner to prevent spillage of the chain segment 6. To Due to possible vibration, the chain may slip off the back groove on the teeth of the pinion flywheel 5. In addition, since the chain guiding performance is also weakened on the outside, at least in the tooth tip area, asynchrony is reduced or prevented, or when the transmission system 2 reverses, the chain 6 may slip off the chain guide roller 16.

[0218] This can also be achieved by looking at the chamfered surface C. S1i C S2i C S3i C S1o and C S2o The sloping layout and the resulting boundary edge B B1i B B2i B B3i B B1o and B B2o This is achieved through the inclined orientation, because thus, region A on the end-side tooth surface has a complete and unreduced thickness dimension. T1i A T2i A T1o AT2o is retained on both coarse and fine teeth T. W and T N The latter option, in particular, can be combined with... Figure 22 and Figure 23 from Figure 19 It can be seen. Combined Figure 22 ,from Figure 19 It can be seen, especially the coarse-toothed T W At the transition radius R T Inner surface area C (excluding) S1i Inner thickness dimension T T It has decreased somewhat, while the transition radius R T Coarse teeth T within W Inner thickness dimension T T At least in surface region A T1i The internal volume did not decrease.

[0219] This also applies to fine-tooth T-type gears. N Inner surface region C S2i However, the degree is reduced, and it applies to coarse-tooth T gears to a lesser extent. W outer surface region C S1o and fine-tooth T N outer surface region C S2o In all the above cases, this applies only to chain links that are still running entirely on the chain guide roller 16 (see, for example, [reference needed]). Figure 13 and Figure 14 In the chain links OL0 and IL1), then tooth T W and T N Guiding area A Gi Or A Go Always has a complete thickness dimension T T However, if the chain link involved is partially separated from the chain guide roller 16 (see, for example, [reference needed]), Figures 5 to 14 In the chain link OL1), then tooth T W and T N Guiding area A Gi Or A Go Mainly in the inner surface region C S1i and C S2i The inner part has a locally reduced thickness, but the same applies to the outer surface region C. S1o and C S2o It has a reduced thickness to a lesser extent.

[0220] Therefore, although the chain guiding performance of the chain guide roller 16 is particularly good in the inner direction S i The effect is somewhat reduced, but especially for coarse-toothed T-type teeth. W of Figure 19 The effective tooth thickness W that causes the chain 6 to synchronize on the chain guide roller 16 is shown. T It is not necessary to reduce (see below) Figures 6 to 12 The selected radius R with the critical effective tooth thickness. TThe larger it is, the coarser the T-shaped teeth on it. W The larger the radius of the tooth thickness becomes, exceeding the inner width of the inner link, the more effective the synchronization of chain 6 on the chain guide roller 16 becomes, and the less sensitive this synchronization is to tooth profile changes caused by wear or small wrap angles of chain 6 around the chain guide roller 16. Refer to the description of wrap angles in the introduction of the manual. Figure 2 The corresponding illustration in the diagram.

[0221] It can be achieved by chamfering surface C S1i C S2i and C S3i The slanted layout, especially through its following chain output 6 TiD (See also) Figure 14 The spatial tilt and the resulting boundary edge B B1i B B2i and B B3i The inclined direction caused the chain to overflow 6 Ti In particular, it can be found in the groove of the inward shift fork shaft (see) Figure 5 and Figure 6 (and the corresponding description) while proceeding in the most uniform and smooth manner possible, and for making the coarse and fine teeth T of the chain guide roller 6... W T N Effective radius R synchronized with chain 6 T It can be as large as possible.

[0222] Due to the coarse and fine teeth T of the chain guide roller 16 of the present invention W T N The chain guiding performance is not weakened for chain links that are still running entirely on the chain guide roller. Therefore, even with reduced wrapping of the chain guide roller 16, the chain 6 can still be guided well and synchronized. Thus, compared to chain guide rollers in the prior art, i.e., chain guide rollers where the teeth T may not employ an axially asymmetrical design, the chain guide roller 16 of the present invention can, for example, have longer teeth, thereby achieving better chain guiding performance. This is because in the chain guide roller 16 of the present invention, during inward shifting S... i At that time, the force required to move chain 6 to a smaller gear is less (see...) Figure 5 and 6 (and the corresponding description).

[0223] Figure 22 Also shown is the fine-toothed T N Or coarse-toothed T W Loaded tooth surface F L1 F L2 Tooth surface angle γ L1 γ L2 and non-loaded tooth surface F N1 F N2 Tooth surface angle γN1 γ N2 In the embodiment of the chain guide roller 16 mentioned above, the tooth T N T W Loaded tooth surface F L1 F L2 Tooth surface angle γ L1 γ L2 Always more than the unloaded tooth surface F N1 F N2 Tooth surface angle γ N1 γ N2 More gentle. In addition, the fine-tooth T... N The two tooth surface angles γ L1 γ N1 Always coarser than T W The corresponding two tooth surface angles γ L2 γ N2 Smoother. Fine-toothed T N Or coarse-toothed T W Tooth surface angle γ L1 γ L2 The preferred value is γ L1 =24.77° and γ N1 =24.20° and γ L2 =23.88° and γ N2 =23.34°. Fine tooth T N Loaded tooth surface angle γ L1 Coarser T W Loaded tooth surface angle γ L2 Smoother, because of the finer T-tooth N It does not help with synchronization, but only needs to overcome the desynchronization in order to restore the desired synchronization in the event that chain 6 may become desynchronized.

[0224] from Figure 22 You can also see the coarse-toothed T. W Or fine-tooth T N Region A of the tooth tip S1 A S2 It can be seen that the tooth T W T N The tooth tip in region A S1 A S2 The inner teeth each have an inclination angle ε1 and ε2, which mainly face the corresponding tooth T. W T N The corresponding non-loaded tooth surface F N1 F N2 tilt.

[0225] Chain 6 has coarse and fine teeth T W T NUndesired asynchrony on the chain guide roller 16 typically or primarily occurs when the pedal is pressed backward. To prevent or reduce this, the tooth T... N and T W Non-loaded tooth surface F N1 F N2 The tooth surface angle γ (which becomes the load tooth surface when the pedal is pressed backward) N1 γ N2 Always more than the load-bearing tooth surface F L1 F L2 Tooth surface angle γ L1 γ L2 Steeper.

[0226] Towards the non-loaded tooth surface F N1 F N2 Inclined around tooth T W T N Region A of the tooth tip S1 A S2 For the same purpose. These areas also serve to prevent undesirable asynchrony of the chain 6 on the chain guide roller 16, and in the event of asynchrony, to quickly resynchronize the chain 6 running on the chain guide roller 16.

[0227] Towards the non-loaded tooth surface F N1 F N2 Inclined tooth tip region A S1 A S2 In particular, this causes the chain 6, which may be out of sync and thus hangs on the tooth surface or tip of the chain guide roller 16 radially outward, to generate a relative torque between the chain 6 and the chain guide roller 16. This relative torque causes the chain guide roller 16 to rotate relative to the chain 6 until the chain 6 re-engages synchronously with the chain guide roller 16 and stabilizes there.

[0228] like Figure 22 As shown, in the circumferential direction, tooth T W With T N The spacing DD between the teeth of the chain guide roller 16 should also be as short as possible. Conversely, this means that in the circumferential direction, the teeth T of the chain guide roller 16... W and T N The corresponding tooth width should be as long as possible. This is combined with a shorter, finer tooth T that is fully rounded in the transition area between the tooth tip and the load-bearing tooth surface. N And combined in coarse and fine T-tooth W and T N Upper non-loaded tooth surface F N The slanted tooth tips, as described above, are beneficial to the synchronization of chain 6.

[0229] Therefore, overall, the synchronization of chain 6 on chain guide roller 16 is improved, so that in the event of possible asynchrony, it can be controlled by rotating along the working direction D. W As operation continues, chain 6 will automatically resynchronize itself as quickly as possible, without requiring any special user intervention, such as pressing the pedal backward until resynchronization occurs. During this brief phase, the user will hardly perceive any asynchrony in chain 6 on the chain guide roller 16 or its automatic resynchronization.

[0230] Figures 24 to 26 Another embodiment of the chain guide roller 16 of the present invention is shown. Figures 24 to 26 The embodiment shown is actually identical to the one in all the details of the teeth. Figures 4 to 23 The embodiments shown are consistent, but in particular, according to the present invention, these details differ in the inner and outer embodiments.

[0231] Figures 24 to 26 The difference between the illustrated embodiment and the aforementioned embodiment lies only in that... Figures 24 to 26 In the embodiment shown, on the outer S o and inner S i Of the several teeth, preferably all teeth T W T N The transition zone or root R between teeth T The area has chamfered C C This can be achieved by using a chamfered C. C To achieve or improve the self-cleaning capability of the chain guide roller 16, the specific method is to [details about the tooth root R]. T Based on chamfer C C The narrowing of the blade, thus approximating its shape, reduces or prevents dirt buildup, and especially reduces or prevents undesirable ice buildup at the tooth root R during winter operation. T Within the area.

[0232] This can be particularly seen from Figure 25 As shown in the sectional view, it is also shown that it is located on both sides, that is, on the inner side S. i and the outer S o Chamfer C C This leads to T-tooth W T N Between tooth roots R T Accordingly, slopes B are formed on both sides within the area. R .

[0233] Figure 26 Shown in another sectional view Figure 24 and Figure 25 The chain guide roller 16 is shown. The cut surface passes through the axis A of the chain guide roller 16. P And in the upper region of the figure, with coarse tooth TW Intersecting, in the lower region of the diagram, with the fine tooth T. N Intersecting. Similar to Figure 19 The land, too, can be obtained from Figure 26 The inner guide area A of the chain guide roller 16 can be seen. Gi With outer guide area A Go The asymmetry of the teeth between them. If we consider... Figure 26 The chain guide roller 16 is cut in the manner shown. Figures 4 to 23 The implementation shown will yield the same result as... Figure 26 The same cross-sectional image. In other words, this means Figure 26 The view shown applies to chain guide rollers. Figures 4 to 23 as well as Figures 24 to 26 The two implementation methods are shown.

[0234] right Figure 26 The visible inner guiding region A Gi and outer guidance area A Go Surface C of the inner teeth S1o C S2o C S1i C S2i C S3i and chamfer B B1o B B2o B B1i B B2i B B3i For a description, please refer to the above text, especially regarding... Figure 15 and Figure 16 The description.

[0235] Furthermore, the chain guide roller 16 of the present invention can also be used as the chain tension roller 15 (see [reference]). Figure 2 ), or used in other areas of the bicycle drivetrain, particularly as a so-called guide wheel (Idler Pulley) on the bottom bracket B. B (See also) Figure 1 and Figure 2 Near the bottom bracket. Applying guide wheels to bicycles, especially mountain bikes with rear suspension, can provide a desired special orientation for the chain load strands around the bottom bracket or near the hinge of the rear suspension, or more reliably guide the empty chain strands or bring them closer to the rear pillar, thereby preventing the chain from slapping or bouncing.

[0236] In these situations, it is also desirable for the chain tension roller 15 or guide wheel to be in the outward direction S. o With the inner direction S i The chain guide roller 16 of this disclosure can achieve this by having different degrees of guiding effect.

[0237] In the case where the chain guide roller 16 is used as a guide wheel for the load strand of the chain 6, it is preferably implemented as an all-metal structure, while the guide wheel in the empty chain strand of the chain 6 is preferably made of plastic, similar to the case described above for the bicycle shifting mechanism 4.

Claims

1. A chain guide roller (16) for a bicycle drivetrain (2), the bicycle drivetrain having a chain (6), a multi-layer pinion configuration (5) and a bicycle rear shift mechanism (4), the chain guide roller (16) comprising a rotation axis (A) P The rotating bearing region, the tooth region having teeth (T) for meshing with the chain (6), and the load-bearing structure connecting the bearing region and the tooth region together, wherein on the inner and outer sides (A) of at least one tooth (T) T Guiding regions (A) are constructed on each of the above. G ), so as to be substantially parallel to the axis of rotation (A) P The chain (6) is guided laterally. Its features are, At least one inner guide region (A) of the at least one tooth (T) Gi ) relative to at least one outer guiding region (A Go ) has a center plane (P) relative to the chain guide roller (16). M The thickness dimension (T) is reduced at least locally. T ), so that the chain segment (6) that is generally tangentially separated from the chain guide roller (16) t ) can be in the outer direction (S) o The ratio of the inner direction (S) is used on the upper part. i A larger oblique angle (λ) on i ).

2. The chain guide roller according to claim 1, Its features are, At least one guidance area (A) Gi A Go This includes a prominent ridge arranged on the inner side surface (A) of at least one tooth (T). T1i ) or outer side (A T1o Within the area.

3. The chain guide roller according to claim 1 or 2, Its features are, At least one guide region (A) of the at least one tooth (T) Gi A Go At least partially, it has a property that varies with the rotation axis (A). P The thickness (T) decreases as the spacing increases. T ).

4. The chain guide roller according to claim 1, Its features are, At least one guide region (A) of the at least one tooth (T) Gi A Go At least one thickness (T) T The reduced area is constructed as a chamfered surface (C). S The chamfer plane (P) is defined by the chamfered surface. C The chamfered plane is along the axial direction (D) A ) relative to the center plane of the chain guide roller (P) M The chamfered surface (C) is arranged at an angle (α) to define the chamfered surface. S ) relative to the side surface (A) of the at least one tooth (T) T The radial inner boundary edge (B) B ).

5. The chain guide roller according to claim 4, Its features are, The at least one chamfered plane (P) C ) and at least one chamfered surface (C) of the at least one tooth (T) S ) around the radial line (L) of the chain roller corresponding to the at least one tooth (T) R L' R ) relative to the center plane (P) of the chain guide roller M The chamfered surface (C) is deflected by an angle (β) such that the chamfered surface (C) is deflected by an angle (β). S The radial inner boundary edge (B) B ) has a working rotation direction (D) along the chain guide roller (16). W The radially outward rising direction, and / or the guiding area (A) Gi A Go At least on the chamfered surface (C) S The region has the load tooth surface (F) of the tooth (T) within the area. L ) toward its non-loaded tooth surface (F N Increasing thickness (T) T ).

6. The chain guide roller according to claim 1, Its features are, The load-bearing tooth surface (F) of the at least one tooth (T) L Tooth surface angle (γ) L The unloaded tooth surface (F) of at least one tooth (T) N Tooth surface angle (γ) N (More gentle) 7. The chain guide roller according to claim 1 or 6, Its features are, The tooth tip region (A) surrounding the at least one tooth (T) S ) has a non-loaded tooth surface (F) mainly facing the tooth (T). N The tilt angle (ε).

8. The chain guide roller according to claim 1 or 4, Its features are, The chain guide roller (16) has an even number of teeth (T), which alternate with either a first group or a second group of teeth along the circumferential direction, wherein the teeth in the first group are narrower (T). N It is narrower than the spacing between the inner chain plates, and the second set of teeth includes at least one wider tooth (T). W The width of the at least one wider tooth is greater than the spacing between the inner chain plates, such that the at least one wider tooth (T) W It can only be completely submerged in the gap between the outer link (OL) and the inner link (IL), but cannot be completely submerged in the gap between the inner link (IL).

9. The chain guide roller according to claim 8, Its features are, At least one tooth of the first group of teeth (T) N ) relative to at least one tooth of the second group of teeth (T) W It has a tooth height that is reduced in the radial direction.

10. The chain guide roller according to claim 9, Its features are, At least one tooth of the first group of teeth (T) N One or two tooth surface angles (γ) L1 γ N1 ) compared to at least one tooth of the second group of teeth (T) W The corresponding tooth surface angle (γ) L2 γ N2 (More gentle) 11. A bicycle rear gear shifting mechanism, The system includes a base element (10) that can be connected to the bicycle rear fork end bracket (7), a shifting element (12) that can move relative to the base element (10) by means of a deflection mechanism, and a chain guide device (13) that is deflectably connected to the shifting element (12), the chain guide device having a chain guide roller (16) and a lower chain tension roller (15). Its features The chain guide roller (16) according to any one of claims 1 to 10.

12. A bicycle drivetrain, It includes at least one front sprocket (3), a multi-layer pinion configuration (5), and a rear shifting mechanism (4) with a chain guide roller (16) and a lower chain tension roller (15). Its features are, The rear shift mechanism (4) includes a chain guide roller (16) according to any one of claims 1 to 10.

13. The bicycle drivetrain according to claim 12, Its features are, The multi-layer pinion configuration (5) has at least one pinion (31) having an even number of teeth (T), which alternately correspond to a first or second group of teeth in the circumferential direction, wherein the teeth in the first group are narrower teeth (T). N It is narrower than the spacing between the inner chain plates, and the second set of teeth includes at least one wider tooth (T). W The width of the at least one wider tooth is greater than the spacing between the inner chain plates, such that the at least one wider tooth (T) W It can only be completely submerged in the gap between the outer link (OL) and the inner link (IL), but cannot be completely submerged in the gap between the inner link (IL).

14. The bicycle drivetrain according to claim 12 or 13, Its features are, The rear shift mechanism is a direct pin shift mechanism (4) with a shift parallelogram mechanism (11) that is not tilted or only slightly tilted.

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