TWI747152B - Drive arrangement for a bicycle - Google Patents

Abstract

A drive arrangement for a bicycle may be provided with various interactive components configured to reliably and repeatably engage and disengage with one another both when new and after a period of wear. The drive arrangement may include a drive sprocket assembly connected to a driven sprocket assembly with a chain movable by a gear changer.

Description

Drive configuration for bicycles

This patent is related to the previously filed U.S. Provisional Application No. 62/801,608 filed on February 5, 2019, and its priority rights are claimed. The entire contents of these previously filed applications are hereby incorporated by reference.

The present disclosure relates to a driving configuration for a bicycle. Specifically, this disclosure describes a drive configuration of a multi-ratio chain transmission, for example, in an external transmission assembly. Describe a chain that moves between sprockets to change the ratio and maintain the connection between the sprockets to drive the bicycle.

The bicycle can be equipped with a drive configuration. For example, a crank assembly can be provided to transmit torque from a rider to a drive sprocket assembly. The drive sprocket assembly may have one or more drive sprockets. The drive sprocket assembly can transmit torque to a driven sprocket assembly via a chain. For example, the driven sprocket assembly may have a plurality of sprockets that can rotate about a rear wheel axis and are assembled to engage the chain. The driven sprocket assembly can be rotatably fixed to a rear wheel in at least one rotation direction. The driven sprocket assembly can be configured to rotate freely in a direction opposite to the forward rotation of the rear wheel, thereby allowing the rider to continue forward when not operating the crank assembly.

Chain retention is important to maintain the operation of the drive configuration. The tension of the chain between the driving sprocket assembly and the driven sprocket assembly can help the chain to retain. However, if the rider does not step on the pedals and the driven sprocket assembly rotates by inertia relative to the rear wheel (as described above), the tension on the chain can be reduced, resulting in a greater possibility of unintentional chain derailment.

Chain retention feature can be used. For example, the size and shape of the drive configuration can be set to limit the free space between the teeth of the drive sprocket assembly and the chain plates of the chain. Optimizing the ratio of the tooth size filling the distance between the chain roller and the chain plate can balance the desired chain retention quality and undesirable chain retention quality (such as commonly referred to as chain seizure). However, many current drive configuration combinations do not provide sufficient chain retention and/or have undesirable problems (such as chain seizure), whether new or once the drive configuration has reached a minimum wear level.

The nature of shifting is another consideration of drive configuration. Chain shifting can be controlled mechanically, such as via Bowden cables; electronically, such as via wired or wireless communication protocols; hydraulically, such as via open or closed systems; or by similar methods or methods的组合。 The combination. The nature of shifting will also take into account the optimization of the drive configuration geometry. For example, a similar ratio of tooth size to chain distance can be balanced to allow sufficient chain deflection between the drive sprocket and the driven sprocket offset along the crank axis, while also allowing the transmission gear to follow the crank axis Shift the chain precisely. In particular, with the trend toward a larger number of driven sprockets placed on a larger total axial distance and/or axially closer to adjacent sprockets, many current drive configurations do not provide sufficient shift accuracy and / Or axial range.

One of the objectives of this disclosure is to describe various drive configurations that are configured to control the interaction between components to optimize chain retention, controlled chain release, and shift accuracy and shift axial range. The specific relationship between the components of the drive configuration can be configured to optimize these qualities when the drive configuration is new and/or when the drive configuration has worn out to a degree. For example, components can be designed to wear at a similar rate. Components can be designed with wear-specific and/or cooperative features to spread the load and therefore wear.

One aspect of the present invention provides a driving arrangement for a bicycle, which has a crank that can rotate about a crank axis and has a crank mounting portion. A drive sprocket is provided, which has a sprocket mounting portion attached to the crank mounting portion and a chain engaging portion. The chain engaging part has a plurality of thin teeth and a plurality of thick teeth. Each of the plurality of thick teeth has a load characteristic, a guiding tip portion and a recess area arranged radially outward from the load characteristic. The pocket area is bounded by each of the following: a line extending from the crank axis through the radially outermost range of one of the load features in a first radial direction; A circle defined by a radial distance of a radially outermost range; and a circumference of the guide tip between the radially outermost range of the load characteristic and the radially outermost range of the guide tip An external configuration. The driving arrangement has a chain that is assembled to engage with the chain engaging portion of the driving sprocket. The chain has a plurality of outer chain plates; a plurality of rollers, each of the plurality of rollers is axially arranged between a pair of the plurality of outer chain plates with respect to a roller axis; and a plurality of inner chains Plate, which is axially arranged between the plurality of outer chain plates and the plurality of rollers with respect to the roller axis, wherein each of the plurality of inner chain plates has: a load slope, its size and shape Is set to extend beyond the corresponding one of the plurality of thick teeth in the second radial direction relative to the roller axis during the engagement of the drive train. ; And a gap feature whose size and shape are set to allow the corresponding one of the plurality of rollers to interact with the gap feature in a third radial direction of the load slope relative to the roller axis during the engagement of the drive train Align or protrude through the gap feature.

Another aspect of the present invention provides a driving arrangement for a bicycle, which has: a crank which can rotate around a crank axis in a circumferential driving direction and has a crank mounting portion; and a drive sprocket having A sprocket mounting portion attached to the crank mounting portion; a chain engaging portion having a plurality of thin teeth; a plurality of thick teeth, each of the plurality of thick teeth having a load characteristic; and the load characteristic A guiding tip is arranged radially outward. Each of the plurality of thick teeth has an axial protrusion disposed circumferentially outside the load characteristic in a circumferential direction opposite to the driving direction. The driving arrangement has a chain that is assembled to engage with the chain engaging portion of the driving sprocket. The chain has a plurality of outer chain plates and a plurality of rollers. Each of the plurality of rollers is axially arranged between a pair of the plurality of outer link plates with respect to a roller axis. The chain plate has a plurality of inner chain plates axially arranged between the plurality of outer chain plates and the plurality of rollers with respect to the roller axis, wherein each of the plurality of inner chain plates includes a load The characteristic receiving part, and one of the load characteristic widths is filled in the load characteristic receiving part of the first pair of inner link plates in one of the plurality of inner link plates and the load characteristic of a second pair of inner link plates At least 70% of an inner axial distance defined between the receiving parts.

Another aspect of the present invention provides a driving arrangement for a bicycle, which has a crank that can rotate about a crank axis in a circumferential driving direction and has a crank mounting portion, and a drive sprocket. The drive sprocket has a sprocket mounting part attached to the crank mounting part and a chain engaging part. The chain engaging portion has a plurality of thin teeth and a plurality of thick teeth, each of the plurality of thick teeth has a load characteristic; and a guide tip is arranged radially outward from the load characteristic. Each of the plurality of thick teeth has an axial protrusion disposed circumferentially outside the load characteristic in a circumferential direction opposite to the driving direction. The driving configuration has a driven sprocket assembly, which includes at least twelve (12) driven sprocket wheels and a gear transmission. The gear transmission has a guide wheel; a tension wheel that can rotate around a pulling axis; and a fluid shock absorber assembly. The fluid shock absorber assembly has a flow diameter, which is assembled to facilitate the flow from a first chamber to a second chamber at a first flow rate; and a valve, which is assembled with Facilitate the flow from the second chamber to the first chamber at a second flow rate greater than the first flow rate. The driving arrangement has a chain, which is assembled with the chain meshing part of the driving sprocket and meshing with the driven sprocket assembly, the chain has a plurality of outer chain plates; a plurality of rollers, the plurality of Each of the rollers is axially arranged between a pair of the plurality of outer chain plates with respect to a roller axis; and a plurality of inner chain plates are arranged axially with respect to the roller axis on the plurality of outer chain plates Between the chain plate and the plurality of rollers, wherein each of the plurality of inner chain plates includes a load characteristic receiving portion, and one of the load characteristic widths is filled in one of the plurality of inner chain plates. At least 70% of an inner axial distance defined between the load characteristic receiving portion of the inner pair of link plates and the load characteristic receiving portion of a second pair of inner link plates.

FIG. 1 is a side view of a road-type assembly for a bicycle 21 using a driving arrangement 33. As shown in FIG. The bicycle 21 includes a frame 25, front wheels 27 and rear wheels 29 rotatably attached to the frame 25, and a drive configuration 33. A front brake 20 is provided for braking the front wheels 27, and a rear brake 22 is provided for braking the rear wheels 29. Each of the front wheel 27 and the rear wheel 29 includes a tire 35 attached to the rim 31, where the tire 35 is assembled to engage the riding surface 100. A handlebar assembly 24 is provided for steering the front wheels 27. The direction of the arrow "A" indicates that the bicycle 21 is oriented forward and/or forward. Therefore, the forward direction of the movement of the bicycle 21 corresponds to the direction A.

Other combinations of bicycle 21 are expected. For example, FIG. 2 depicts a bicycle 21 with a mountain or off-road configuration. Potential differences between the various bicycle configurations include the differences in the depiction between Figures 1 and 2. For example, FIG. 1 depicts the handlebar assembly 24 in a hanging assembly, and the example in FIG. 2 has a flat assembly of the handlebar assembly 24. The example in FIG. 2 also includes a front suspension 26 for movably mounting the front wheel 27 to the frame 25 and a rear suspension 28 for movably mounting the rear wheel 29 to the frame 25. The front suspension 26 and the rear suspension 28 may include one or more of adjustable suspension components such as springs or shock absorbers. In this example, an adjustable seat cushion assembly 30 is also shown, which is assembled to movably attach a saddle 32 to the frame 25. The adjustable seat cushion assembly 30 may include a seat post head 34 that can be attached to the saddle 32 and connected to the upper part 36 of the seat post. The seat post upper portion 36, the seat post head 34, and the saddle 32 can be assembled to move relative to the seat post lower portion 38 that can be fixedly attached to the frame 25. For example, the upper part of the seat post 36 may ride within the lower part of the seat post 38, wherein the lower part of the seat post 38 is fixed to a seat tube 39 of the frame 25.

Figures 1 and 2 each depict an embodiment of the drive configuration 33, the drive configuration includes: a drive sprocket assembly 40, which is rotatably mounted to the frame 25; a driven sprocket assembly 42, which is mounted to the rear Wheel 29; and a chain 44, which engages the drive sprocket assembly 40 and the driven sprocket assembly 42 (which can be a rear sprocket assembly). The drive sprocket assembly 40 may be attached to a crank 46 to facilitate torque transfer from the rider to the rear wheel 29, to the chain 44 and to the driven sprocket assembly 42 via the drive sprocket assembly 40. For example, the drive sprocket assembly 40 can be connected to a pair of left and right crank arms of the crank 46 via a crank mounting portion 65.

The chain 44 can be shifted by a rear gear transmission 48 as depicted in FIG. 19 via a plurality of driven sprockets of the driven sprocket assembly 42. The plurality of driven sprockets of the driven sprocket assembly 42 can be arranged according to a radius, for example, each sprocket further on the outside has a smaller radius than the last one. The chain 44 can also be shifted by a front gear transmission 50 through a plurality of drive sprockets of the drive sprocket assembly 40. The plurality of drive sprockets of the drive sprocket assembly 40 can be arranged according to a radius, for example, each of the drive sprockets further on the outside has a larger radius than the last one. Alternatively, as in FIG. 4, as when the drive sprocket assembly 40 is composed of one of the individual drive sprocket wheels 52, the front gear transmission 50 may be omitted.

Each of FIGS. 1 and 2 depicts an embodiment of a control assembly 23 for controlling components of a bicycle. For example, the control assembly 23 can be configured to control the shifting of the drive arrangement 33. The control assembly 23 may be a plurality of control assemblies. For example, a pair of control assemblies 23 can be used. Other embodiments of the control assembly 23 are anticipated, for example, in triathlon or time trial applications, where the first pair of control assemblies 23 can be used on the extension of the handlebar assembly 24, and the second pair of control assemblies Can be used on adjacent brake levers.

FIG. 3 is a schematic side view of an embodiment of a driving arrangement 33 having a plurality of driving sprockets on the driving sprocket assembly 40. In one embodiment, the drive sprocket assembly 40 has a first drive sprocket 40a and a second drive sprocket 40b. The front gear transmission 50 may be used to shift the chain 44 between the first drive sprocket 40a and the second drive sprocket 40b. The front gear transmission 50 may be assembled to transfer one of the upper chain segments 44a of the chain 44 defined between the drive sprocket assembly 40 and the driven sprocket assembly 42 from the first drive sprocket 40a and the second drive sprocket. One of 40b is axially displaced to the other. The front gear transmission 50 can also be assembled with a chain 44 on the axially shifting drive sprocket assembly 40, just like the movable shift feature placed on the drive sprocket assembly 40.

The drive sprocket assembly 40 can rotate around a crank axis C. For example, the crank 46 can be used to rotate the drive sprocket assembly 40 around the crank axis C to drive the driven sprocket assembly 42 through the upper chain segment 44a. The driven sprocket assembly 42 can rotate around a rear wheel axis Z. For example, the driven sprocket assembly 42 may be configured to rotationally drive the rear wheel 29 along a driving direction D of the upper chain segment 44a. In one embodiment, the driven sprocket assembly 42 is configured to freely rotate from the rear wheel 29 in a direction opposite to the driving direction D of the upper chain segment 44a.

The driven sprocket assembly 42 may be mounted to the frame 25 around the rear wheel axis Z. For example, fixing members such as quick-release rods, bolted axles, and/or through-wheel axle rods can be used to install the driven sprocket assembly 42. The driven sprocket assembly 42 can be installed together with the rear wheel 29. For example, the driven sprocket assembly 42 can be mounted to the rear wheel 29, the rear wheel 29 can then be mounted to the frame 25 around the rear wheel axis Z, and both the rear wheel 29 and the driven sprocket assembly 42 can surround the rear wheel axis The line Z rotates relative to the frame 25. Alternatively, the driven sprocket assembly 42 may be mounted to the frame 25 independently of the rear wheel 29. For example, at least one of the driven sprocket assembly 42 and the rear wheel 29 can be independently removed from the frame 25.

FIG. 4 is a schematic side view of an embodiment of the drive arrangement 33 with a single drive sprocket 52. The drive sprocket assembly 40 may be specifically configured for a single drive sprocket 52. For example, the drive sprocket assembly 40 may have a sprocket mounting portion 41 as shown in FIGS. 6 to 8, which is assembled to connect a separate drive sprocket 52 by being connected to the crank mounting portion 65 Align with the other components of the drive configuration 33.

The rear gear transmission 48 may include one or more chain tensioning features. For example, the rear gear transmission 48 may include a force wheel 56 that is configured to apply tension to the drive configuration 33. For example, the tension wheel 56 can be stretched on the lower chain segment 44 b of the chain 44 defined between the driving sprocket assembly 40 and the driven sprocket assembly 42. The tension applied to the lower chain segment 44b can assist the retention of the chain 44. The tension wheel 56 can rotate around a pulling axis T. For example, the tension wheel 56 can be rotated in the pulling direction T1 to apply tension to the drive configuration 33 and can be rotated in the relaxation direction T2 to release the tension in the drive configuration 33. The rear gear transmission 48 can control movement in one or both of the tension direction T1 and the relaxation direction T2, as shown and described with reference to FIG. 19.

The rear gear transmission 48 may include a guide wheel 54. The guide wheel 54 can be used to position the chain 44 relative to the driven sprocket assembly 42. For example, the guide wheel 54 can move axially relative to the rear wheel axis X to shift the chain 44 between the driven sprockets of the driven sprocket assembly 42. The guide wheel 54 can also control the radial displacement of a part of the chain 44 relative to the driven sprocket assembly 42 from the axis Z of the rear wheel. For example, the rear gear transmission 48 and the driven sprocket assembly 42 can be geometrically controlled so that the guide wheel 54 maintains a meshing distance from one of the driven sprocket wheels of the driven sprocket assembly 42 with respect to the rear wheel axis Z The same radial distance. In an embodiment, the guide wheel 52 can rotate around the tension axis T.

FIG. 5A is a top schematic view of the embodiment of the driving configuration 33 of FIG. 4 in a driving state. The driving state can be characterized by the engagement of one of the driven sprockets of the driven sprocket assembly 42 with the individual driving sprocket 52. For example, the rider can provide power to the rear wheels 29 via the drive configuration 33 without interrupting the drive state.

The embodiment shown in FIG. 5A depicts a drive configuration 33 with twelve (12) driven sprockets on the driven sprocket assembly 42. Can include more or less driven sprockets. The distance between the driven sprockets of the driven sprocket assembly 42 along the axis Z of the rear wheel can be uniform. Alternatively, this axial distance can be changed. For example, the driven sprocket of the driven sprocket assembly 42 with a relatively small diameter change to the next driven sprocket may have a relatively large change in the axial distance to the next driven sprocket. The driven sprocket of the driven sprocket assembly 42 that has a relatively large change in diameter to the next driven sprocket may have a relatively small change in the axial distance to the next drive sprocket.

The driven sprocket of the driven sprocket assembly 42 may have a uniform change in diameter between adjacent sprocket wheels. Alternatively, the driven sprocket assembly 42 may gradually increase in diameter along the rear wheel axis Z. For example, moving along the rear wheel axis Z from the frame 25 to the rear wheel 29 axially inwardly, the direct percentage change of each of the driven sprockets of the driven sprocket assembly 42 can be increased.

The embodiment in FIG. 5A depicts a straight chain line of the chain 44. The straight chain one can be characterized by no lateral bending or minimal lateral bending of the chain 44 between the driving sprocket assembly 40 and the driven sprocket assembly 42. In an embodiment with a separate drive sprocket 52, a straight chain line can be achieved only at one combination of the driven sprocket and the drive sprocket. In the illustrated embodiment, the chain 44 is in a straight chain line orientation when aligned with the fourth sprocket inward from the frame 25. In an embodiment, the individual drive sprocket 52 may be aligned with the driven sprocket assembly 42 in a plane with or adjacent to a relatively outer driven sprocket.

Fig. 5B is a top schematic view of the drive arrangement 33 of Fig. 4 in a shifting state. The chain 44 is shown shifting between the fourth outermost driven sprocket of the driven sprocket assembly 42 to the sixth outermost driven sprocket. The chain 44 can be shifted by the guide wheel 54 of the rear gear transmission 48. The gear shift can be performed between adjacent driven sprockets of the driven sprocket assembly 42 or between driven sprockets farther away.

The amount of chain deflection of the chain 44 is shown in Figure 5B, starting at the lower chain segment 44a. As the drive configuration 33 continues to rotate in the drive direction D, the driven sprocket assembly 42 can shift the upper chain segment 44b by the same amount of chain deflection as the lower chain segment 44a. The driven sprocket assembly 44a may be equipped with shift features such as ramps, channels, and/or pins to facilitate this shift operation.

FIG. 6 is an external side view of a single driving sprocket 52 of an embodiment of the driving arrangement 33. FIG. The single drive sprocket 52 may include various parts. For example, the individual drive sprocket 52 may include a sprocket mounting portion 41 for mounting to the crank mounting portion 65 of the crank 46. The single drive sprocket 52 may also include a chain engaging portion 58. The chain engaging portion 58 may be provided with a plurality of teeth for engaging the chain 44.

The chain engaging portion 58 may include a thin tooth 60. The thin teeth 60 can be assembled for a relatively small space between the chain plates of the meshing chain 44. For example, the thin teeth 60 can be assembled to fit in each link space of the chain 44. The chain engaging portion 58 may include a plurality of thin teeth 60. For example, a plurality of thin teeth 60 may be alternately arranged around the circumference of the chain engaging portion 58 around the crank axis C.

The chain engaging portion 58 may include a thick tooth 62. The thick teeth 62 can be assembled for a relatively large space between the chain plates of the meshing chain 44. For example, the thick teeth 60 can be assembled in only a relatively large link space of the chain 44. The chain engaging portion 58 may include a plurality of thick teeth 62. For example, the plurality of thick teeth 62 may be alternately arranged between the plurality of thin teeth 60 around the circumference of the chain engaging portion 58 around the crank axis C.

FIG. 7 is an inside side view of the single drive sprocket 52 of FIG. 6. The chain engaging portion 58 may be integral with the sprocket mounting portion 41, or the two may be separable components, as shown in the embodiment of FIG. 7.

Figure 8 is an external side view of an embodiment of a single drive sprocket 52 depicting the engagement of the chain assembly. An outer link assembly 64 meshing with a plurality of thick teeth 62 is shown. Each of the plurality of thick teeth 62 can be specifically configured for engagement with the outer link assembly 64. For example, the size and shape of the thick tooth 62 can be set to mesh only with the outer link assembly 64 and not mesh with the inner link assembly 66.

It is shown that the inner link assembly 66 meshes with a plurality of thin teeth 60. The inner link assembly 66 can be specifically configured for meshing with a plurality of thin teeth. For example, the thick teeth 62 may be too large to fit in the gap of the inner link assembly 66. In one embodiment, the multiple thick teeth 62 have an outer axial dimension relative to the crank axis C, which is larger than a corresponding inner axial dimension of the inner link assembly 66.

The embodiment of FIG. 8 depicts the overall assembly of the sprocket mounting portion 41 and the chain engaging portion 58. This one-piece assembly can facilitate the direct mounting of the individual drive sprocket 52 to the crank 46. In this configuration, the complexity can be minimized. This combination can also increase the gap between the drive sprocket assembly 40 and the frame 25 because the fixing member needs to protrude toward the frame 25.

FIG. 8 depicts the first radial height R1 of the radially outermost range of the thick tooth load characteristic 74 of the thick tooth 62 relative to the crank axis C. As shown in FIG. Each of the second to eighth radial heights R2 to R8 will also be described with respect to the crank axis C. This outermost point can be referred to as the radial outermost range 77 of the thick tooth load characteristic.

The second radial height R2 is the radial height of the roller axis AA of the roller 68 of the chain 44.

The third radial height R3 is the radial height of the root circle of the individual drive sprocket 52.

The fourth radial height R4 is the radial height of the radially outermost range of the thick tooth guide tip 72 of the thick tooth 62. This outermost point may be referred to as the radially outermost range 80 of the thick tooth guide tip.

The fifth radial height R5 is the radial height of the outermost range of the thin tooth guide tip 70 of the thin tooth 60 in the radial direction. This outermost point may be referred to as the radially outermost range 78 of the thin tooth guide tip.

The sixth radial height R6 is the radial height of the outermost point in the radial direction of the outer link assembly 64. The radially outermost point of the outer link assembly 64 may be directly above the roller axis AA along a radial line extending from the crank axis through the roller axis AA. In one embodiment, the radially outermost point of the outer link assembly 64 is equal to the radial height of the radially outermost point of the inner link assembly 66.

The seventh radial height R7 has the radially outermost range of the thin tooth load characteristic 74 of the thin tooth 60. This outermost point may be referred to as the radial outermost range 75 of the thin tooth load characteristic.

The eighth radial height R8 has the radially outermost range of the roller 68 of the chain 44. This outermost point is along a radial line extending from the crank axis C and passing through the roller axis AA.

FIG. 9 is an enlarged view of the single drive sprocket 52 of FIG. 8. The thick teeth 62 can be combined with various features. For example, the thick tooth 62 may include a thick tooth loading feature 76. The thick tooth load feature 76 may be configured to interact with a roller surface 69 of the roller 68. For example, the thick tooth load feature 76 may be contoured to accept the roller surface 69. In one embodiment, the thick tooth loading feature 76 is configured to contact the roller surface 69 at a thick tooth contact point 73. The thick tooth contact point 73 may be part of a contact area. For example, the thick tooth contact point 73 can be placed on a radius that matches the radius of the roller surface 69. The contact area may also represent an enlarged zone during the driving load when one or both of the thick tooth load feature 76 and the roller surface 69 are deformed.

The thick tooth 62 may include a thick tooth guide tip 72. The thick tooth guide tip 72 may be positioned radially outward from the thick tooth load feature 76 relative to the crank axis C. For example, the thick tooth guide tip 72 may directly start radially above the radially outermost range 77 of the thick tooth load characteristic.

The thick tooth guide tip 72 can be configured to guide the meshing of the chain 44. For example, the thick tooth guide tip 72 may be tapered to accept one of the chain link assemblies 64 outside the chain 44. In one embodiment, the thick-tooth guide tip 72 has a thick-tooth guide tip radially outermost range 80, which is disposed relatively far from the crank axis C for a relatively early period during rotation in the driving direction D The point guide chain 44.

The thin teeth 60 can be combined with various features. For example, the thin tooth 60 may include a thin tooth load feature 74. The thin tooth load feature 74 can be configured to interact with a roller surface 69 of the roller 68. For example, the thin tooth load feature 74 may be contoured to accept the roller surface 69. In one embodiment, the thin tooth load feature 74 is configured to contact the roller surface 69 at a thin tooth contact point 79. The thin tooth contact point 79 may be part of a contact area. For example, the thin tooth contact point 79 can be placed on a radius that matches the radius of the roller surface 69. The contact area may also represent an enlarged zone during the driving load when one or both of the thin tooth load feature 74 and the roller surface 69 are deformed.

The thin tooth 60 may include a thin tooth guide tip 70. The thin tooth guide tip 70 may be positioned radially outward from the thin tooth load feature 74 relative to the crank axis C. For example, the thin-tooth guide tip 70 may directly start radially above the radially outermost range 75 of the thin-tooth load characteristic.

The thin-tooth guide tip 70 can be configured to guide the engagement of the chain 44. For example, the thin-tooth guide tip 72 may taper to accept one of the inner link assemblies 66 of the chain 44. In one embodiment, the thick-tooth guide tip 72 has a thick-tooth guide tip radially outermost range 80 that is radially disposed farther from the crank axis C than the thin-tooth guide tip 70. This can be demonstrated by the relatively large fourth radial height R4 compared to the relatively small radial height R5.

The first radial height R1 of the thick tooth load characteristic radially outermost range 77 can be expressed in proportion to the fourth radial height R4 and the fifth radial height R5. For example, the quotient of the first radial height R1 to the fifth radial height R5 may be greater than the quotient of the first radial height R1 to the fourth radial height R4. In an embodiment, the first radial height R1 may be closer to the fifth radial height R5 than the third radial height R3 close to the tooth root circle. The first radial height R1 may be closer to the third radial height R3 than the fourth radial height R4.

Fig. 10 is an enlarged view of the single drive sprocket 52 of Fig. 8. The view of Fig. 10 shows the roller axis AA of the roller 68 during the state in which the drive train is engaged. Although the other components of the chain 44 are not shown in this depiction, each of the rollers 68 are positioned as if the chain 44 were assembled and being driven by one of the torques via a separate drive sprocket 52.

The radial height of the roller axis, denoted as the second radial height R2, is drawn relative to the crank axis C. The second radial height R2 may be greater than the first radial height R1 of the radially outermost range 77 of the thick tooth load characteristic. In one embodiment, the thick tooth contact point 73 is radially below the first radial height R1, and the first radial height R1 is radially below the second radial height R2.

The pair of rollers 68 depicted in FIG. 10 may be part of the inner link assembly 66 as depicted in FIG. 11. The inner link assembly 66 may include one or more features configured to interact with the thick teeth 62. For example, the inner link assembly 66 may include a load ramp 94 configured to guide the thick teeth 62. In one embodiment, the load ramp 94 is configured to guide the thick tooth load feature 76 into driving engagement with the roller surface 69. The size and shape of the load slope 94 can be set to extend beyond the roller surface 69 of the roller 68 with respect to the roller axis AA. The load ramp 94 may extend through the thick tooth load feature 76 of the thick tooth 62 in a radial direction from the roller axis AA during drive train engagement.

As seen from the side view, a recess area can be defined between the components of the driving arrangement 33. For example, the pocket area may be bounded by each of the following: a load line B extending in a radial direction from the crank axis C through the radially outermost range 77 of the thick tooth load characteristic; a circle formed by the thick tooth The fourth radial height R4 of the radial outermost range 80 of the guide tip is defined; and the thick tooth guide between the radial outermost range 77 of the thick tooth load characteristic and the radial outermost range 80 of the thick tooth guide tip The thick teeth of the leading tip 72 guide the tip outer configuration 71.

The recessed area of the thick tooth 62 may represent a release area for the roller 68 of the chain 44. For example, the roller 68 may deviate from the thick tooth load feature 76 into the pocket area during the transitional rotation of the chain 44 from the separate drive sprocket 52 to the lower chain segment 44b. The pocket area can be tunable. For example, the recess area can be made relatively large to allow the roller 68 to deviate smoothly from the worn thick tooth load feature 76, which can additionally reduce or eliminate a smaller embodiment of the recess area.

A similar recess area can be defined with reference to the thin teeth 60. For example, the radially outermost range 77 of the thin-tooth guiding tip of the thin-tooth guiding tip 70, the radially outermost range 75 of the thin-tooth load characteristic and the outer configuration 81 of the thin-tooth guiding tip can be used to determine the thinness. The boundary of the tooth pocket area.

FIG. 11 is an enlarged view of the single drive sprocket 52 of FIG. 8. The view of FIG. 11 depicts the inner link assembly 66 engaged with the thin teeth 60. The inner link assembly 66 can be configured to cover the radially outermost area 77 of the thin tooth guide tip. The outer link assembly 64 can also be assembled to cover the radially outermost range 80 of the thick tooth guide tip. The sixth radial height R6 of the outer link assembly 64 may be greater than the fifth radial height of the thin teeth 60 and/or the fourth radial height of the thick teeth 62. In one embodiment, the sixth radial height R6 is also the radial height of the outermost range of the outer link assembly 64.

FIG. 11 depicts a tangent line V along a clearance feature 99 of the inner link assembly 66. The tangent line V can be defined as a line passing through the uppermost point of the gap feature 99 and the lowermost point of the gap feature 99. In one embodiment, the tangent line is defined as between a lower range E1 of a gap feature and an upper range E2 of a gap feature.

The gap feature 99 can be configured to provide a gap for the roller 68 to interact with other components of the drive arrangement 33. For example, the size and shape of the gap feature 99 can be set to allow the corresponding one of the plurality of rollers 68 to interact with the gap feature 99 in the third radial direction L of the load ramp 94 relative to the roller axis AA during the engagement of the drive train. Align or protrude through the gap feature 99.

The gap feature 99 can be used to define a gap area. The gap area may be larger than the recess area. For example, the gap area can be defined by a boundary similar to the recess area, but with the tangent line V replacing the load line B. The clearance feature 99 may provide a large amount of clearance for the disengagement of the roller 68 from the drive sprocket assembly 40. In one embodiment, the size and shape of the clearance feature 99 are set so as not to interfere with the thick teeth 62 during at least one of the drive train engagement and the drive train disengagement.

FIG. 12 is a partial top view of an embodiment of a separate drive sprocket 52 of the drive arrangement 33. FIG. Thick teeth 62 may include one or more width features. For example, the thick tooth 62 may include a chain retention feature that protrudes axially relative to the crank axis C. In one embodiment, the thick tooth 62 includes a thick tooth inner protrusion 61 and a thick tooth outer protrusion 63. The thick tooth protrusions 61, 63 may have uniform or asymmetric sizes. For example, the thick tooth outer protrusion 63 may axially protrude from the thick tooth 62 farther than the thick tooth inner protrusion 61.

The thick tooth guide tip 72 can be configured to facilitate chain guide and/or meshing. For example, the thick-tooth guide tip 73 may have a one-dimensional configuration to guide the chain 44 to engage when the chain is deflected. The thin-tooth guide tip 70 can be similarly assembled.

Fig. 13A is a side view of the outer side of the chain 44 of an embodiment of the drive configuration. The chain 44 may have a flat-top assembly. For example, the upper profile of the upper chain segment 44a may be linear across the plurality of inner link assemblies 66 and outer link assemblies 64. This combination of chain 44 can help increase the strength. For example, an embodiment of a chain with relatively thin link plates can use a flat top assembly to maintain sufficient strength to reliably transmit torque via the drive configuration 33.

The chain 44 may also include one or more connection and/or disconnection features. For example, the chain 44 may be provided with one or more of the connecting rods 45. In one embodiment, the connecting rod 45 provides toolless connection and disconnection of opposite ends of the chain 44.

The chain 44 may have various asymmetric planes. For example, as shown in FIG. 17, at least with regard to the flat top assembly discussed above, the chain 44 may be asymmetrical across a longitudinal roller centerline F. A centerline halfway between the pair of rollers 68 spanning the outer link assembly 64, the outer link assembly 64 of the chain 44 may also have asymmetry. For example, the outer link assembly 64 may include one or more of the outer inclined surfaces 67. The outer slope 67 can be configured to interact with other components of the drive arrangement 33. For example, the size and shape of the outer slope 67 can be set to cooperate with the shifting characteristics of the driven sprocket assembly 42 discussed above.

13B is a top view of the chain 44 of FIG. 13A, which depicts a schematic representation of the thick teeth 62 and the thin teeth 60 of a drive sprocket assembly 40 meshed with the chain 44. FIG. For illustration purposes, the teeth 60, 62 of the drive sprocket assembly 40 are arranged as if the drive sprocket assembly 40 has an infinite radius.

A space can be defined between the components of the chain. For example, the tooth receiving space may be defined between the inner link assembly 66 and the outer link assembly 64. The inner link assembly 66 may have a thick tooth receiving space whose size and shape are set to receive the thick tooth 62. The inner link assembly 66 can define an inner axial distance G in this space. For example, the inner axial distance G may be defined between an inner inner link plate 90 and an outer inner link plate 92 of the inner link assembly 66.

The outer link assembly 64 may have a size and shape set to receive a thin tooth receiving space of the thin tooth 60. The outer link assembly 64 can define an outer axial distance S in this space. For example, the outer axial distance S may be defined between an inner outer link plate 86 and an outer outer link plate 88 of the outer link assembly 64.

Figure 14 is a cross-sectional view of the chain 44 of Figure 13B taken along line 14-14. This cross-sectional view depicts the overlap of the load ramp 94 outside the roller 86 as in FIG. 10. The load slope 94 can be configured as a load characteristic receiving part. For example, the load ramp 94 may be configured to receive a load characteristic during the meshing process of the chain 44 and the drive sprocket assembly 40. In one embodiment, the load ramp 94 has an angled surface for receiving the thick tooth load feature 76. In another embodiment, the load ramp 94 has a convex surface that faces the thick tooth load feature 76, as shown in Figure 17D.

The display roller 68 has a roller width W (in FIG. 14). The roller width W can be complementary to the other components of the drive arrangement 33. For example, the roller width W may be equal to or greater than the width of the load characteristic of the drive sprocket assembly 40. In one embodiment, the roller width W is greater than each of the thin tooth load characteristic 74 and the thick tooth load characteristic 76.

The load slope 94 may have a width greater than the width W of the roller. For example, the load slope 94 may have a minimum width P1 of the load slope which is larger than the roll width W. The load slope 94 may also have a maximum width P3 of the load slope which is larger than the minimum width P1 of the load slope. Thus, the load ramp 94 may be configured to funnel or guide the thick tooth load feature 74 toward the roller surface 69.

At any point along the load slope 94, the effective width P2 of the load slope can be described as the width of the load slope 94 even at that point within the range of the roller surface 69. For example, the load slope length K shown in FIG. 16 corresponds to the maximum width P3 of the load slope at its radially outermost point, and corresponds to the effective width of the load slope P2 at its radially innermost point.

Referring again to FIG. 14, the inner link plates 90 and 92 may each include an inner link edge 96. The inner link edge 96 may be configured to interact with other features of the drive arrangement 33 (eg, the shifting features of the driven sprocket assembly 42 discussed above). In one embodiment, when the load ramp 94 extends to the axially outermost point of the inner link edge 96, the inner link edge 96 has or does not have an axial dimension relative to the roller axis AA.

The outer link plates 86 and 88 may have an outer link edge 98. The outer link edge 98 may be configured similarly to the inner link edge 96. For example, the outer link edge 98 may be configured to interact with the shift feature of the driven sprocket assembly 42. In one embodiment, the inner link edge includes an outer chamfer 67.

Figure 15 is an isometric view of the inner link assembly of the chain of Figure 13A. The load ramp 94 has a profile that is shown to extend widely along the circumference of the roller 68. Depending on the point at which the distance is measured along a line extending radially from the roller axis AA, the load ramp 94 may extend beyond the roller surface 69 at various distances.

Figure 16 is a cross-sectional view of the inner link assembly 66 of Figure 15 taken along line 16-16. The longitudinal roller centerline F of the inner link assembly 66 is shown passing through the roller axis C of the inner link pair of the roller 68. The longitudinal roller centerline may also define a third radial direction toward the gap feature 99, and along this direction, the roller 68 protrudes through the gap feature 99. A roller protrusion 99a can be defined as the distance that the roller surface 69 protrudes through the gap feature 99.

Show a gap feature lower range E1 below the centerline F of the longitudinal roller. The lower range E1 of the clearance feature is defined at a lowest point where it intersects with the clearance feature 99. The lower range E1 of the gap feature is shifted from the longitudinal roller centerline F by a gap feature offset Q, which defines the distance of one of the lowest points of the gap feature 99.

Show a gap feature upper range E2 above the centerline F of the longitudinal roller. The upper range E2 of the clearance feature is defined at an uppermost point where it intersects with the clearance feature 99. A gap feature height is defined between the upper range E2 of the gap feature and the lower range E1 of the gap feature. The upper range E2 of the gap feature can be shifted from the center line F of the longitudinal roller according to the gap feature offset Q. Alternatively, the upper range E2 of the gap feature may be positioned closer to or farther from the centerline F of the longitudinal roller than the lower range E1 of the gap feature. In one embodiment, the upper range E2 of the gap feature is the same as the centerline F of the longitudinal roller, and the entire range of the gap feature 99 is the same as or below the centerline F of the longitudinal roller.

A second radial direction line L extending from the roller axis AA is shown in FIG. 16. Along the second radial direction line L, the load slope length K is measured as discussed above. The second radial direction line L extends to meet the thick tooth contact point 73 of the thick tooth load feature 76 so that the load ramp length K is how much the load ramp 94 extends beyond the thick tooth load feature 76 on the second radial direction line L Far measurement.

The various inner roller distances will now be described. The inner distance of the roller may be uniform along the outer link assembly 64 and the inner link assembly 66. Describe the distance J1 in the first roller at one of the radial heights of the thick tooth contact squin 73. The inner distance J1 of the first roller describes the distance between the various lengths of the teeth 60, 62 that can be accommodated therebetween.

Describe the second roller inner distance J2 along the longitudinal roller centerline F. The second roller inner distance J2 is at a point of the largest roller width and a point of the smallest roller inner distance.

A minimum distance J3 in the recess can also be provided. For example, the minimum distance J3 in the pocket can describe a minimum gap between the features of the pocket, and the teeth 60 and 62 can be configured to engage between the features of the pocket.

FIG. 17A is a schematic cross-sectional view of the thick tooth 62 of the drive sprocket assembly 40 of FIG. 9 taken along the line 17A-17A. The views of FIGS. 17A to 17D correspond to the circumference below the first radial height R1 of the radially outermost range 77 of the thick tooth load characteristic at the radial height of the thick tooth contact point 73. At this radial height, the thick tooth 62 can be described in terms of its cross-sectional size.

The thick tooth inner protrusion 61 has a first inner axial protrusion width Y2. The thick tooth outer protrusion 63 has a first outer axial protrusion width Y3. The length of the thick tooth protrusions 61 and 63 can be described by a first axial protrusion length X2.

The thick tooth load characteristic 76 has a first load characteristic width Y4. The thick tooth load characteristic 76 also has a first load characteristic length X3.

The thick tooth 62 has a first thick tooth maximum width Y5. The maximum width Y5 of the first thick tooth can be described as the sum of the first inner axial protrusion width Y2, the first outer axial protrusion width Y3, and the first load characteristic width Y4. The thick tooth also has a first thick tooth maximum length X4.

17B is a schematic cross-sectional view of the thin teeth 60 of the drive sprocket assembly 40 of FIG. 9 taken along the line 17B-17B. The thin tooth 60 has a first thin tooth width X1 and a first thin tooth length Y1. The first thin tooth width Y1 may be equal to the first load characteristic width Y4. The first thin tooth length X1 may be equal to the first thick tooth maximum length X4.

FIG. 17C is a schematic cross-sectional view of the chain 44 of FIG. 13A taken along the line 17C-17C and corresponding to the schematic cross-sectional views of FIGS. 17A and 17B.

The first outer axial distance S1 between the inner surface of the inner outer link plate 86 and the outer outer link plate 88 is shown. The first outer axial distance S1 may be the same as the outer axial distance S or greater than the outer axial distance S.

The first inner axial distance G1 between the inner surface of the inner inner link plate 90 and the outer inner link plate 92 is shown. The first inner axial distance G1 may be the same as the inner axial distance G or greater than the inner axial distance G.

The distance M in the inclined plane between the opposed pairs of the inner inner link plates 90 is shown, and the distance M can also be measured between the opposed pairs of the outer inner link plates 92. The distance M within the slope can be compared with the first axial protrusion length X2 to determine the filling percentage of the first axial protrusion length X2. The filling percentage of the first axial protrusion length X2 may be equal to or substantially equal to other filling percentages. For example, the filling percentage of the first axial protrusion length X2 may be within 80% to 120% of one or more of the filling percentages based on other lengths shown and described. In one embodiment, the filling percentage of the first axial protrusion length X2 is within 90% to 110% of one or more of the shown and described filling percentages based on other lengths.

As shown in FIG. 16, the first roller inner distance J1. The first roller inner distance J1 can be compared with the slope inner distance M to calculate a longitudinal load slope length KK related to the load slope length K, as shown in FIG. 16 and described with reference to FIG. 16.

A load slope distance P between the pair of inner inner link plates 90 and outer inner link plates 92 in the outer link space is shown. The load slope distance P can be equal to the effective width P2 of the load slope as described above. The load slope distance P can be compared with the first load characteristic width Y4 to determine the filling percentage of the first load characteristic width Y4 within the load slope distance P. The filling percentage of the first load characteristic width Y4 within the load slope distance P may be equal to or substantially equal to other filling percentages. For example, the filling percentage may be within 80% to 120% of one or more of the displayed and described filling percentages based on other widths. In one embodiment, the filling percentage is within 90% to 110% of one or more of the displayed and described filling percentages based on other widths.

Fig. 17D is a schematic cross-sectional view of Fig. 17C combined with the schematic cross-sectional views of Figs. 17A and 17B.

The thick tooth 62 may have at least one of the tooth overlap portions 51. For example, the thick tooth load feature 76 may include a tooth overlap portion 51 defined as overlapping a space between a pair of inner inner link plates 90 and outer inner link plates 92. The tooth overlap portion 51 may also be included on the opposite side wing or rear side wing of the thick tooth 62. The overlapping portion 51 of the thick tooth load feature 76 can be used in the determination of the filling percentage within the load slope distance P as described above with reference to FIG. 17C.

18A is a schematic cross-sectional view of the thick teeth 62 of the drive sprocket assembly 40 of FIG. 9 taken along the line 18A-18A. The views of FIGS. 18A to 18D correspond to cross-sectional views taken at the second radial height R2 of the roller axis AA during the engagement of the roller 68 with the drive sprocket assembly 40.

The thick tooth 62 can be described with reference to its cross-sectional size at the second radial height R2. The thick tooth inner protrusion 61 has a second inner axial protrusion width Y7. The thick tooth outer protrusion 63 has a second outer axial protrusion width Y8. The length of the thick tooth protrusions 61 and 63 can be described by a second axial protrusion length X6.

The thick tooth guiding tip 72 has a second characteristic width Y9. The thick tooth guiding tip 72 also has a second characteristic length X7.

The thick tooth 62 has a second thick tooth maximum width YY. The maximum width YY of the second thick tooth can be described as the sum of the second inner axial protrusion width Y7, the second outer axial protrusion width Y8, and the second characteristic width Y9. The thick tooth also has a second thick tooth maximum length X8.

18B is a schematic cross-sectional view of the thin teeth 60 of the drive sprocket assembly 40 of FIG. 9 taken along the line 18B-18B. The thin tooth 60 has a second thin tooth width X5 and a second thin tooth length Y6. The second thin tooth length Y6 may be equal to the second characteristic width Y9. The second thin tooth width X5 may be equal to the second thick tooth maximum length X8.

Each of the dimensions of FIGS. 18A and 18B may be related to the dimensions of FIGS. 17A and 17B. For example, each of the second length and the second width of the thick tooth 62 and the thin tooth 60 may be less than or equal to each of the first length and the first width of the thick tooth 62 and the thin tooth 60 . In an embodiment, each of the second sizes is smaller than a corresponding first size.

18C is a schematic cross-sectional view of the chain 44 of FIG. 13A taken along the line 18C-18C and corresponding to the schematic cross-sectional views of FIGS. 18A and 18B.

The second outer axial distance S2 between the inner surface of the inner outer link plate 86 and the outer outer link plate 88 is shown. The second outer axial distance S2 may be the same as the outer axial distance S, greater than or smaller than the outer axial distance S. In one embodiment, the second outer axial distance S2 is smaller than the first outer axial distance S1 in FIG. 17C.

The second inner axial distance G2 between the inner surface of the inner inner link plate 90 and the outer inner link plate 92 is shown. The second inner axial distance G2 may be the same as the inner axial distance G, greater than or smaller than the inner axial distance G. In an embodiment, the second inner axial distance G2 is smaller than the first inner axial distance G1.

A gap distance N between opposite pairs of inner inner link plates 90 at the corresponding pairs of gap features 99 is shown. The gap distance N can also be measured between the opposed pairs of the outer inner chain plates 92. The gap distance N can be compared with the second axial protrusion length X7 to determine the filling percentage of the second axial protrusion length X7. The filling percentage of the first axial protrusion length X2 may be equal to or substantially equal to other filling percentages. For example, the filling percentage of the second axial protrusion length X7 may be within 80% to 120% of one or more of the filling percentages based on other lengths shown and described. In one embodiment, the filling percentage of the second axial protrusion length X7 is within 90% to 110% of one or more of the shown and described filling percentages based on other lengths.

As shown in FIG. 16, the second roller inner distance J2. The second roller inner distance J2 can be compared with the gap distance N to calculate the roller protrusion 99a, as shown in and described with reference to FIG. 16.

18D is a schematic cross-sectional view of FIG. 18C combined with the schematic cross-sectional views of FIGS. 18A and 18B.

The display roller 68 is weighted into the outer link space according to the distance of the roller protrusion 99a. This distance can be defined to the roller overlap portion 53 of the roller 68 in the outer link space.

As above, referring to FIGS. 17A to 17D and FIGS. 18A to 18D, various filling percentages are described. In an embodiment, the first load characteristic length X3 fills between 10% and 40% of the distance J1 in the first roller. In another embodiment, the first load characteristic length X3 fills between 20% and 30% of the distance J1 in the first roller. The filling percentage of the first load characteristic length X3 within the distance J1 within the first roller may correspond to the size and/or wear life of the thick tooth load characteristic 76.

The second characteristic length X7 filling the second roller inner distance J2 may be less than the first load characteristic length X3 filling the first roller inner distance J1. For example, the second characteristic length X7 can fill less than 20% of the second roller inner distance J2. In an embodiment, the second characteristic length X7 is filled with a distance J2 within the second roller that is less than or equal to 10%.

The first axial protrusion length X2 can fill a larger percentage of the first roller inner distance J1 than the first load characteristic length X3. For example, the first axial protrusion length X2 can fill between 30% and 60% of the distance J1 in the first roller. In one embodiment, the first axial protrusion length X2 fills between 35% and 50% of the distance J1 in the first roller.

The maximum width YY of the second thick tooth can be assembled to fill at least 70% of the second outer axial distance S2. In one embodiment, the maximum width of the second thick tooth is configured to fill at least 80% of the second outer axial distance S2. In another embodiment, the maximum width of the second thick tooth is configured to fill at least 85% of the second outer axial distance S2.

The second thin tooth width Y6 can be configured to fill at least 70% of the second inner axial distance G2. In one embodiment, the second thin tooth width is configured to fill at least 80% of the second inner axial distance G2. In another embodiment, the second thin tooth width is configured to fill at least 85% of the second inner axial distance G2.

At least a segmented portion of the thick tooth load feature 76 can be configured to fill at least 70% of the load slope distance P. In one embodiment, the first load characteristic width Y4 fills at least 70% of the effective width P2 of the load slope. In yet another embodiment, the thick tooth load feature 76 fills at least 75% of the load slope distance P. In yet another embodiment, the thick tooth load feature 76 fills at least 80% of the load slope distance P. The thick tooth load feature 76 can be configured to fill the axial distance G within a similar percentage.

As described above, the percentage filling of the width of the thick tooth 62 can be related to the percentage filling of the width of the thick tooth load feature 76. For example, the percentage filling of the first load characteristic width Y4 within the load slope distance P may be within 80% to 120% of the percentage filling of the first thick tooth maximum width Y5 within the first outer axial distance S1. In one embodiment, the percentage filling of the first load characteristic width Y4 within the load slope distance P is within 90% to 110% of the percentage filling of the first thick tooth maximum width Y5 within the first outer axial distance S1. Also, in one embodiment, these equal percentage fillings are equal.

19 is a schematic cross-sectional view of the gear transmission 48 of an embodiment of the drive arrangement 33. The rear gear transmission 48 may be attached to the frame 25 by a link 55 such as a parallelogram link. The rear gear transmission may include a guide wheel 54 and a tension wheel 56. The tension wheel 56 can be constrained by a cage 57 at a set radial distance from the guide wheel 54 with respect to the tension axis T.

The rear gear transmission 48 can be controlled in the tension direction T1 and the relaxation direction T2. In one embodiment, the rear gear transmission 48 is configured for relative free movement in the tension direction T1 and relative restricted movement in the relaxation direction T2. For example, a clutch or shock absorber may be used to control the movement of the rear gear transmission 48. In this way, the tension on the lower chain segment 44b can be maintained in response to large shocks caused by rough terrain, while still allowing relatively small and/or slow shifting movements.

The rear gear transmission 48 may include a fluid damper assembly 37. The fluid shock absorber assembly 37 can be configured to control the movement of the tension wheel 56 in the tension direction T1 and the relaxation direction T2. For example, the fluid shock absorber assembly 37 may be configured with a first chamber 47 and a second chamber 49 that communicate across one or more flow paths. In one embodiment, the fluid communication restriction from the second chamber 49 to the first chamber 47 is less than the fluid communication restriction from the first chamber 47 to the second chamber 49. For example, the flow rate of the communication from the second chamber 49 to the first chamber 47 may be greater than the flow rate of the communication from the first chamber 47 to the second chamber 49. In one embodiment, a valve 43 is provided to facilitate the flow from the second chamber 49 to the first chamber 47. The valve 43 may be a spring type.

The drive configuration 33 may have any of the features and elements as shown and described. The description of the embodiments described herein is intended to provide a general understanding of the structure of the various embodiments. These descriptions are not intended to serve as a complete description of all the elements and features of devices and systems that utilize the structures or methods described herein. After reviewing the content of this disclosure, many other embodiments may be obvious to those familiar with the art. Other embodiments can be utilized and derived from the content of this disclosure, so that structural and logical substitutions and changes can be made without departing from the scope of the content of this disclosure. In addition, the illustrations are only representative and may not be drawn to scale. It is possible to zoom in on some proportions in the figure while minimizing other proportions. Therefore, the content and drawings of this disclosure should be regarded as illustrative rather than restrictive.

Although this specification contains many details, these should not be construed as limitations on the scope of the present invention or the content that can be claimed, but on the contrary, should be construed as specific descriptions of the features of specific embodiments of the present invention. Certain features described in this specification in the context of separate embodiments can also be implemented in combination in a single embodiment. Conversely, various features described in the context of a single embodiment can also be implemented in multiple embodiments individually or in any suitable subcombination. In addition, although features can be described above as acting in certain combinations and even claimed as such at the beginning, one or more features from the claimed combination can be deleted from the combination in some cases, and the claimed combination can be directed to one Sub-combination or a change in a sub-combination.

Similarly, although operations and/or actions are depicted in the drawings in a specific order and described herein, this should not be understood as requiring that these operations be performed in the specific order or sequence shown or that all descriptions should be performed The operation to achieve the desired result. In some cases, multitasking and parallel processing may be advantageous. In addition, the separation of various system components in the embodiments described above should not be construed as requiring such separation in all embodiments, and it should be understood that any described program components and systems can usually be integrated in a single software product Together or packaged into multiple software products.

One or more embodiments of the present disclosure may be individually and/or collectively referred to herein by the term "invention", which is only for convenience and is not intended to voluntarily limit the scope of this application to any specific invention or invention Sex concept. In addition, although specific embodiments have been illustrated and described herein, it should be understood that any subsequent configuration designed to achieve the same or similar purpose may replace the specific embodiments shown. This disclosure is intended to cover any and all subsequent adaptations or changes of various embodiments. After reviewing the description, the combination of the above embodiments and other embodiments not specifically described herein are obvious to those familiar with the art.

The abstract is provided to comply with 37 C.F.R. §1.72(b), with the following understanding: it will not be used to explain or limit the scope or meaning of the patent application. In addition, in the foregoing embodiments, for the purpose of streamlining the content of the disclosure, various figures may be grouped together or described in a single embodiment. The content of this disclosure should not be construed as reflecting that the claimed embodiment requires more features than explicitly enumerated in the scope of each patent application. On the contrary, as reflected in the scope of the following patent applications, the subject matter of the present invention may be directed to not all features of any of the disclosed embodiments. Therefore, the following patented scopes are incorporated into the embodiments, in which each patented scope independently defines the separately claimed subject matter.

It is intended that the foregoing detailed description is to be regarded as illustrative rather than restrictive, and it should be understood that the scope of the following patent applications including all equivalents is intended to define the scope of the present invention. The scope of the patent application should not be construed as being limited to the order or elements described, unless there is a description to achieve that effect. Therefore, all embodiments within the scope and spirit of the following patent applications and their equivalent content are claimed as the present invention.

20: Front brake 21: Bicycle 22: Rear brake 24: Handlebar assembly 25: Frame 26: front suspension 27: front wheel 28: rear suspension 29: rear wheel 30: Adjustable seat cushion assembly 31: Flange 32: Saddle 33: Drive configuration 34: Seat stigma 35: Tires 36: Upper part of the seat post 37: Fluid shock absorber assembly 38: Lower part of the seat post 39: seat tube 40: drive sprocket assembly 40a: first drive sprocket 40b: second drive sprocket 41: Sprocket installation part 42: driven sprocket assembly 43: Valve 44: chain 44a: Upper chain segment 44b: Lower chain segment 45: connecting rod 46: crank 47: first chamber 48: Rear gear transmission 49: second chamber 50: Front gear transmission 51: tooth overlap 52: drive sprocket 53: Roll overlapping part 54: guide wheel 55: connecting rod 56: Tension wheel 57: cage 58: Chain engaging part 60: Thin teeth 61: Inner protrusion of thick tooth 62: thick tooth 63: Outer protrusion of thick tooth 64: Outer link assembly 66: inner link assembly 67: external slope 68: Roll 69: roller surface 70: Thin tooth guide tip 72: Thick tooth guide tip 73: Thick tooth contact point 74: Thin tooth load characteristics 75: Thin tooth load characteristic radial outermost range 76: Thick tooth load characteristics 77: Thick tooth load characteristic radial outermost range 78: The outermost radial range of the thin tooth guide tip 79: Thin tooth contact point 80: Thick tooth guide tip radial outermost range 81: Thin tooth guide tip outer configuration 86: inner outer chain plate 88: Outer outer chain plate 90: Inside inner chain plate 92: Outer inner chain plate 94: Load slope 96: inner link edge 98: outer link edge 99: Gap feature 99a: Roller protrusion 100: riding surface A: Direction AA: Roller axis C: crank axis D: Drive direction E1: Lower range of clearance feature E2: Upper range of clearance feature F: Longitudinal roller centerline G: inner axial distance G1: The first inner axial distance G2: The second inner axial distance J1: The inner distance of the first roll J2: the distance within the second roll J3: The minimum distance in the recess K: length of load slope KK: Length of longitudinal load slope M: Distance within the slope N: gap distance P: Load slope distance P1: Minimum width of load slope P2: Effective width of load slope P3: Maximum width of load slope Q: Offset R1: first radial height R2: second radial height R3: third radial height R4: Fourth radial height R5: fifth radial height R6: sixth radial height R7: seventh radial height R8: Eighth radial height S: outer axial distance S1: The first outer axial distance S2: The second outer axial distance T1: Tension direction T2: slack direction W: Roll width X1: width of the first thin tooth X2: the length of the first axial protrusion X3: First load characteristic length X4: Maximum length of the first thick tooth X5: the width of the second thin tooth X6: the length of the second axial protrusion X7: second characteristic length X8: The maximum length of the second thick tooth Y1: Length of the first thin tooth Y2: first inner axial protrusion width Y3: The first outer axial protrusion width Y4: first load characteristic width Y5: Maximum width of the first thick tooth Y6: The width of the second thin tooth Y7: The second inner axial protrusion width Y8: The second outer axial protrusion width Y9: second feature width YY: The maximum width of the second thick tooth Z: Rear wheel axis

Figure 1 is a side view of a road-type bicycle using a driving configuration;

Figure 2 is a side view of a cross-country bicycle using a driving configuration;

Figure 3 is a schematic side view of a drive configuration with multiple drive sprockets;

Figure 4 is a schematic side view of a drive configuration with a single drive sprocket;

Fig. 5A is a top schematic view of the driving configuration of Fig. 4 in a driving state;

Figure 5B is a top schematic view of the drive configuration of Figure 4 in a gear shift state;

Figure 6 is a side view of the outer side of a drive sprocket in a drive configuration;

Figure 7 is a side view of the inner side of the drive sprocket of Figure 6;

Figure 8 is an external side view of a drive sprocket depicting the engagement of the chain assembly;

Figure 9 is an enlarged view of the drive sprocket of Figure 8;

Figure 10 is an enlarged view of the drive sprocket of Figure 8;

Figure 11 is an enlarged view of the drive sprocket of Figure 8;

Figure 12 is a partial top view of a drive sprocket in a drive configuration;

Figure 13A is a side view of the outer side of a chain of a drive configuration;

Figure 13B is a top view of the chain of Figure 13A depicting a schematic representation of the teeth of a drive sprocket meshing with the chain;

Figure 14 is a cross-sectional view of the chain of Figure 13B taken along line 14-14;

Figure 15 is an isometric view of the inner link assembly of the chain of Figure 13A;

Figure 16 is a cross-sectional view of the inner chain link assembly of Figure 15 taken along line 16-16;

Figure 17A is a schematic cross-sectional view of the thick teeth of the drive sprocket of Figure 9 taken along the line 17A-17A;

Figure 17B is a schematic cross-sectional view of the thin teeth of the drive sprocket of Figure 9 taken along the line 17B-17B;

17C is a schematic cross-sectional view of the chain of FIG. 13A along the line 17C-17C and corresponding to the schematic cross-sectional views of FIGS. 17A and 17B;

17D is a schematic cross-sectional view of FIG. 17C combined with the schematic cross-sectional views of FIGS. 17A and 17B;

Figure 18A is a schematic cross-sectional view of the thick teeth of the drive sprocket of Figure 9 taken along the line 18A-18A;

Figure 18B is a schematic cross-sectional view of the thin teeth of the drive sprocket of Figure 9 taken along the line 18B-18B;

18C is a schematic cross-sectional view of the chain of FIG. 13A along the line 18C-18C and corresponding to the schematic cross-sectional views of FIGS. 18A and 18B;

18D is a schematic cross-sectional view of FIG. 18C combined with the schematic cross-sectional views of FIGS. 18A and 18B; and

Fig. 19 is a schematic cross-sectional view of a gear transmission of a driving configuration.

After considering the following detailed description, other aspects and advantages of the embodiments disclosed herein will become apparent, wherein similar or identical structures have similar or identical reference numerals.

20: Front brake

21: Bicycle

22: Rear brake

24: Handlebar assembly

25: Frame

27: front wheel

29: rear wheel

31: Flange

32: Saddle

33: Drive configuration

34: Seat stigma

35: Tires

40: drive sprocket assembly

42: driven sprocket assembly

44: chain

46: crank

48: Rear gear transmission

50: Front gear transmission

52: drive sprocket

100: riding surface

Claims (13)

A driving configuration for a bicycle, comprising: a crank, which can rotate around a crank axis and having a crank mounting part; a driving sprocket, comprising: a sprocket mounting part attached to the crank mounting part ; A chain meshing part, including: a plurality of thin teeth; a plurality of thick teeth, each of the plurality of thick teeth includes: a load characteristic; a guide tip, which is arranged radially outward from the load characteristic ; And a recess area, which is bounded by each of the following: a line extending from the crank axis in a first radial direction through a radially outermost range of the load feature; a circle, which is guided by the A radially outermost range of the leading tip is defined by a radial distance from the crank axis; and an outer configuration of the guiding tip, which is in the radially outermost range of the load characteristic and the guiding tip Between the radially outermost range of the part; and a chain, which is assembled to engage with the chain engaging portion of the drive sprocket, the chain includes: a plurality of outer chain plates; a plurality of rollers, the plurality of Each of the rollers is axially arranged relative to a roller axis between one of the outer link plates; and a plurality of inner link plates are axially arranged relative to the roller axis in the plurality of Between an outer chain plate and the plurality of rollers, wherein each of the plurality of inner chain plates includes: a load slope, the size and shape of which are set to be able to be in phase during the engagement of the drive train For a second radial direction of the roller axis, a corresponding roller that extends beyond the load characteristic of the corresponding thick tooth of the plurality of thick teeth in the plurality of rollers; characterized in that the plurality of Each inner link plate in the inner link plate further includes: a gap feature, the size and shape of which are set to allow the corresponding roller of the plurality of rollers to be in engagement with the drive system when the load slope is relative to the roller axis A third radial direction is aligned with the clearance feature or protrudes beyond the clearance feature. The drive configuration according to claim 1, wherein at a low radial height of a load contact area with respect to the crank axis, during the engagement of the drive train, a first load characteristic length is between the plurality of rollers The low radial height is within 20% to 30% of the inner distance of one of the first rollers. The drive configuration according to claim 2, wherein during the engagement of the drive train, at a high radial height of a roller center line relative to the crank axis, a second load characteristic length is less than or equal to the plurality of rollers It is 10% of the distance inside a second roller at the high radial height. The driving arrangement according to claim 2, wherein at the low radial height, one of the thick teeth has an axial protrusion within 35% to 50% of the distance within the first roller A first protrusion length. The driving arrangement according to claim 1, wherein at a high radial height, one of the thick teeth has a first axial protrusion and a second axial protrusion describing one of the thick teeth The maximum width, the maximum width of the thick tooth fills at least 70% of an outer axial distance, and the outer axial distance is defined between a first pair of outer link plates and a second pair of outer link plates. Between the outer chain plates. The driving configuration according to claim 5, wherein at the high radial height, the plurality of thin teeth have a maximum thin width filling at least 70% of an inner axial distance, and the inner axial distance defines Between a first pair of inner link plates and a second pair of inner link plates of one of the plurality of inner link plates. The drive configuration described in claim 1 further includes a gap area bounded by one of the following: A tangent line, which is described by an uppermost point and a lowermost point of the gap feature; the circumference, which is defined by a radial distance from a radially outermost range of the guiding tip to the crank axis; and An outer configuration of the guiding tip is located between the intersection of the tangent line and the load characteristic and the radially outermost range of the guiding tip; wherein the gap area is larger than the recess area. The driving arrangement according to claim 1, wherein each of the plurality of thick teeth further comprises: an axial protrusion arranged circumferentially outside the load characteristic in a circumferential direction opposite to a driving direction. The driving configuration according to claim 1, wherein the driving configuration further includes: a driven sprocket assembly, which includes at least twelve driven sprockets; a gear transmission, which includes: a guide wheel; a force wheel , Which can rotate around a pulling axis; and a fluid shock absorber assembly, which includes: a flow diameter, which is configured to facilitate a first flow rate from a first chamber to a second chamber The flow of the chamber; and a valve configured to facilitate the flow from the second chamber to the first chamber at a second flow rate greater than the first flow rate; and wherein the chain also passes It is assembled to mesh with the driven sprocket assembly. The driving configuration according to claim 1, wherein the load slope is assembled as a load characteristic receiving portion, and one of the load characteristic widths fills at least 70% of an inner axial distance, and the inner axial distance defines The first pair of inner link plates in one of the plurality of inner link plates Between the load characteristic receiving portion and the load characteristic receiving portion of a second pair of inner link plates. The driving configuration according to claim 10, wherein the load characteristic width fills at least 75% of the inner axial distance. The driving configuration according to claim 10, wherein the load characteristic width fills at least 80% of the inner axial distance. The driving configuration according to claim 10, wherein the maximum width of one of the plurality of thick teeth fills a percentage of an outer axial distance, and the outer axial distance is defined in one of the plurality of outer chain plates Between a pair of outer link plates and a second pair of outer link plates, and the percentage of the outer axial distance is 90% to the percentage filled by the load characteristic width of the inner axial distance Within 110%.

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