Bicycle derailleur system

Abstract

The present disclosure relates to a self-propelled transmission comprising: an axle; at least one sun gear rotatably mounted around the axle; at least one clutch mechanism configured to selectively prevent rotation of the at least one sun gear about the axle in a first rotational direction in a first mode and to selectively prevent rotation of the at least one sun gear about the axle in an opposite second rotational direction in a second mode; a camshaft mounted inside the axle for actuating the at least one clutch mechanism; wherein each clutch mechanism includes a first pawl and a second pawl configured to be actuated by the camshaft such that the first pawl is selectively engaged with the respective sun gear in a first mode and the second pawl is selectively engaged with the respective sun gear in a second mode.

Description

TECHNICAL FIELD

[0001] The invention relates to a bicycle derailleur system, for example for a human powered vehicle such as a bicycle. BACKGROUND

[0002] Bicycle derailleur systems are known per se. Many bicycle derailleur systems are configured to provide a plurality of different gear ratios.

[0003] One class of known bicycle derailleur systems is based on a chain connecting a front sprocket and a rear sprocket, wherein the rear sprocket is one of a plurality of rear sprockets, for example incorporated in a tower group, and provided with a rear derailleur to provide selectable different gear ratios. Alternatively or additionally, the front sprocket is one of a plurality of front sprockets, and provided with a front derailleur to provide selectable different gear ratios.

[0004] Another class of known bicycle derailleur systems uses a closed derailleur. Such a closed derailleur can be for example an internally geared bicycle hub derailleur. Such a closed derailleur can be an internally geared crank unit. A closed derailleur can be used in combination with a derailleur system.

[0005] A possible disadvantage of current closed derailleur systems is that there are almost no different gear ratios. Current closed derailleur systems with more gear ratios generally have the disadvantage of being heavy. SUMMARY

[0006] It is an object to propose an improved bicycle derailleur for a human powered vehicle or a light electric vehicle. It will be understood that the bicycle derailleur can be used in various vehicles, for example a bicycle or other human powered vehicle or light electric vehicle.

[0007] According to an aspect, there is provided a bicycle derailleur comprising a bridge. The bridge can for example be a wheel bridge. The derailleur can be an internally geared hub derailleur. The bridge can for example be a shaft in a crank derailleur, for example a countershaft. The derailleur can be a crank derailleur unit. The bridge has a central axis extending in its longitudinal direction. The bridge can be configured to be fixed against rotation. The bridge can for example be non-rotatably fixed to a bicycle frame. The derailleur comprises at least one sun gear rotatably mounted around the bridge. The derailleur comprises at least one clutch mechanism configured for selectively preventing rotation of the at least one sun gear around the bridge in a first rotational direction in a first mode, and for selectively preventing rotation of the at least one sun gear around the bridge in an opposite second rotational direction in a second mode. The derailleur comprises a camshaft mounted inside the bridge for actuating the at least one clutch mechanism. Each clutch mechanism comprises a first pawl and a second pawl configured to be actuated by the camshaft such that the first pawl selectively engages with the respective sun gear in the first mode, and the second pawl selectively engages with the respective sun gear in the second mode. This provides the advantage that the sun gear can be selectively prevented from rotating in two different rotational directions. Torque transmission to the sun gear can thus be selectively achieved in two different rotational directions.

[0008] Optionally, the derailleur comprises a further sun gear and a further clutch mechanism. The further clutch mechanism can comprise a third pawl configured to be actuated by the camshaft such that the third pawl selectively engages with the further sun gear in a third mode.

[0009] Optionally, the first pawl and the second pawl are configured to each pivot about a respective pivot axis.

[0010] Optionally, the at least one clutch mechanism comprises a plurality of clutch mechanisms. Optionally, in each clutch mechanism, the first pawl and the second pawl are configured for each pivoting about a respective pivot axis. Optionally, for different ones of the plurality of clutch mechanisms, the radial distance between the pivot axis and the central axis is different. This provides the advantage that a larger radial distance can be selected for clutch mechanisms that need to transmit higher torque.

[0011] Optionally, the at least one sun gear is a plurality of sun gears. Optionally, the bridge has different outer radii at the location of different ones of the plurality of sun gears. Optionally, the sun gears have inner radii corresponding to the outer radii of the bridge. This provides the advantage that a larger diameter can be selected for parts of the bridge and sun gears that need to transmit higher torque.

[0012] Optionally, the first position of the first pawl and the second pawl of at least one of the clutch mechanisms is rotated about the central axis relative to the second position of the first pawl and the second pawl of at least one other of the clutch mechanisms. In this way, the clutch mechanisms can be actuated by a camshaft comprising a single notch profile for actuating a plurality of clutch mechanisms. The single notch profile can comprise one cam or a plurality of cams extending axially along the camshaft. The single notch profile, e.g. the cam or the plurality of cams, can extend along a line parallel to the central axial axis of the camshaft.

[0013] According to an aspect, there is provided a bicycle derailleur comprising a bridge. The bridge can be a wheel bridge, for example. The derailleur can be an internally geared hub derailleur. The bridge can be a shaft, e.g. a countershaft, in a crank derailleur, for example. The derailleur can be a crank derailleur unit. The bridge has a central axis extending along its longitudinal direction. The bridge can be configured to be fixed against rotation. The bridge can be non-rotatably fixed to a bicycle frame, for example. The bridge can be used to support torque from a sun gear onto the frame. The derailleur comprises a plurality of sun gears rotatably mounted about the bridge. The derailleur comprises a plurality of clutch mechanisms for selectively preventing one or more of the plurality of sun gears from rotating about the bridge in at least one rotational direction. The derailleur comprises a camshaft mounted inside the bridge for actuating the plurality of clutch mechanisms. Each clutch mechanism comprises at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with a respective sun gear, the at least one pawl being configured to pivot about a pivot axis. The radial distance between the pivot axis and the central axis is different for different ones of the plurality of clutch mechanisms.

[0014] Optionally, the bridge has different outer radii at the positions of different ones of the plurality of sun gears.

[0015] Optionally, the first position of the at least one pawl of at least one of the clutch mechanisms is rotated about the central axis relative to the second position of the at least one pawl of at least one other of the clutch mechanisms.

[0016] Optionally, for each clutch mechanism, the at least one pawl comprises a first pawl and a second pawl configured to be actuated by the camshaft such that the first pawl selectively engages with the respective sun gear in a first mode and the second pawl selectively engages with the respective sun gear in a second mode. Each clutch mechanism can be configured to selectively prevent the at least one sun gear from rotating about the bridge in a first rotational direction in the first mode and to selectively prevent the at least one sun gear from rotating about the bridge in an opposite second rotational direction in the second mode.

[0017] Optionally, the transmission includes another sun gear and another clutch mechanism. The another clutch mechanism can include a third pawl configured to be actuated by the camshaft such that the third pawl selectively engages with the another sun gear in a third mode.

[0018] According to another aspect, there is provided a bicycle transmission including a bridge. The bridge can be, for example, a wheel bridge. The transmission can be an internally geared hub transmission. The bridge can be, for example, a shaft, such as a countershaft, in a derailleur. The transmission can be a derailleur unit. The bridge has a central axis extending along its longitudinal direction. The bridge can be configured to be fixed against rotation. The bridge can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a plurality of sun gears rotatably mounted about the bridge. The transmission includes a plurality of clutch mechanisms for selectively preventing one or more of the plurality of sun gears from rotating about the bridge in at least one rotational direction. The transmission includes a camshaft mounted inside the bridge for actuating the plurality of clutch mechanisms. The bridge has different outer radii at locations of different ones of the plurality of sun gears.

[0019] Optionally, each clutch mechanism includes at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with the corresponding sun gear.

[0020] Optionally, a first position of the at least one pawl of at least one of the clutch mechanisms is rotated about the central axis relative to a second position of the at least one pawl of at least another of the clutch mechanisms.

[0021] Optionally, the transmission includes another sun gear and another clutch mechanism. The another clutch mechanism can include a third pawl configured to be actuated by the camshaft such that the third pawl selectively engages with the another sun gear in a third mode.

[0022] According to an aspect, there is provided a bicycle derailleur comprising a bridge. The bridge may, for example, be a wheel bridge. The derailleur may, for example, be an internally geared hub derailleur. The bridge may, for example, be a shaft, such as a countershaft, in a crank derailleur. The derailleur may, for example, be a crank derailleur unit. The bridge has a central axis extending along a longitudinal direction thereof. The bridge can be configured to be fixed against rotation. The bridge may, for example, be non-rotatably fixed to a bicycle frame. The derailleur comprises a plurality of sun gears rotatably mounted about the bridge. The derailleur comprises a plurality of clutch mechanisms for selectively preventing one or more of the plurality of sun gears from rotating about the bridge in at least one rotational direction. The derailleur comprises a camshaft mounted inside the bridge for actuating the plurality of clutch mechanisms. Each clutch mechanism comprises at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with a respective sun gear. A first position of the at least one pawl of at least one of the clutch mechanisms is rotated about the central axis relative to a second position of the at least one pawl of at least another of the clutch mechanisms. In this way, the clutch mechanisms can be actuated by a camshaft which can comprise a single notched profile for actuating the plurality of clutch mechanisms. The single notched profile may, for example, comprise one cam or a plurality of cams extending axially along the camshaft. The single notched profile, for example, the cam or the plurality of cams, can extend along a line parallel to a central axial axis of the camshaft.

[0023] Optionally, each clutch mechanism is configured to selectively prevent the respective sun gear from rotating about the bridge in a first rotational direction in a first mode, and to selectively prevent the respective sun gear from rotating about the bridge in an opposite second rotational direction in a second mode.

[0024] Optionally, for each clutch mechanism, the at least one pawl comprises a first pawl and a second pawl configured to be actuated by the camshaft such that the first pawl selectively engages with the respective sun gear in the first mode, and the second pawl selectively engages with the respective sun gear in the second mode.

[0025] Optionally, the derailleur comprises a further sun gear and a further clutch mechanism. The further clutch mechanism can comprise a third pawl configured to be actuated by the camshaft such that the third pawl selectively engages with the further sun gear in a third mode.

[0026] According to one aspect, there is provided a bicycle derailleur comprising a bridge. The bridge may, for example, be a wheel bridge. The derailleur may, for example, be an internally geared hub derailleur. The bridge may, for example, be a shaft, such as a countershaft, in a crank derailleur. The derailleur may, for example, be a crank derailleur unit. The bridge has a central axis extending longitudinally therealong. The bridge can be configured to be fixed against rotation. The bridge may, for example, be non-rotatably fixed to a bicycle frame. The derailleur comprises a sun gear rotatably mounted about the bridge. The derailleur comprises a clutch mechanism for selectively preventing rotation of the sun gear about the bridge in at least one rotational direction. The derailleur comprises a cam shaft having a cam for actuating the clutch mechanism. The clutch mechanism comprises at least one pawl hingedly supported in a pocket of the bridge such that the cam can selectively pivot the at least one pawl radially to engage with the sun gear to thereby prevent rotation of the sun gear relative to the bridge in a first rotational direction. The at least one pawl is movable tangentially in the pocket to allow the pawl to move tangentially and radially inwardly relative to the cam to thereby allow the sun gear to freewheel in a second rotational direction, the opposite rotational direction. Thus, the at least one pawl may, for example, be pivoted radially outwardly such that the at least one pawl engages with the sun gear to prevent rotation of the sun gear relative to the bridge in the first rotational direction. The at least one pawl may, for example, be pivoted radially inwardly such that the at least one pawl disengages from the sun gear to thereby allow rotation of the sun gear relative to the bridge in the first rotational direction. Rotation of the sun gear in the second rotational direction can tangentially move the at least one pawl in the second rotational direction when the at least one pawl is pivoted radially outwardly to engage with the sun gear to thereby prevent rotation of the sun gear relative to the bridge in the first rotational direction, allowing the pawl to be pivoted radially inwardly to disengage from the sun gear to thereby allow the sun gear to freewheel in the second rotational direction.

[0027] Optionally, the derailleur, for example the clutch mechanism, comprises a spring for biasing the at least one pawl radially inwardly.

[0028] Optionally, the derailleur, for example the clutch mechanism, comprises a spring for biasing the at least one pawl tangentially into the pocket, for example such as against a radial end wall of the pocket.

[0029] Optionally, the derailleur, for example the clutch mechanism, comprises a spring having an arm extending about a radially outer surface of the at least one pawl for biasing the at least one pawl radially inwardly.

[0030] According to an aspect, there is provided a bicycle derailleur comprising a bridge. The bridge may, for example, be a wheel bridge. The derailleur may, for example, be an internally geared hub derailleur. The bridge may, for example, be a shaft, such as a countershaft, in a crank derailleur. The derailleur may, for example, be a crank derailleur unit. The bridge has a central axis extending along its longitudinal direction. The bridge can be configured to be fixed against rotation. The bridge may, for example, be non-rotatably fixed to a bicycle frame. The derailleur comprises a sun gear rotatably mounted about the bridge. The derailleur comprises a clutch mechanism for selectively preventing rotation of the sun gear about the bridge in at least one rotational direction. The derailleur comprises a cam shaft having a cam for actuating the clutch mechanism. The clutch mechanism comprises a first pawl and a second pawl, each pawl being hingedly supported in a respective first and second pocket of the bridge, such that the cam can selectively pivot the first pawl radially to engage with the sun gear to prevent rotation of the sun gear relative to the bridge in a first rotational direction, or pivot the second pawl radially to engage with the sun gear to prevent rotation of the sun gear relative to the bridge in a second, opposite, rotational direction. The first pawl is tangentially movable in the first pocket to allow the first pawl to move tangentially and radially inwards relative to the cam to allow the sun gear to freewheel in the second rotational direction; and wherein the second pawl is tangentially movable in the second pocket to allow the second pawl to move tangentially and radially inwards relative to the cam to allow the sun gear to freewheel in the first rotational direction.

[0031] In this way, in the first mode, the first pawl can be pivoted, for example radially outward, such that the first pawl engages the sun gear to prevent the sun gear from rotating relative to the axle in the first rotational direction. The first pawl can be pivoted, for example radially inward, such that the first pawl disengages the sun gear, thereby allowing the sun gear to rotate relative to the axle in the first rotational direction. In the second mode, the second pawl can be pivoted, for example radially outward, such that the second pawl engages the sun gear to prevent the sun gear from rotating relative to the axle in the second rotational direction. The second pawl can be pivoted, for example radially inward, such that the second pawl disengages the sun gear, thereby allowing the sun gear to rotate relative to the axle in the second rotational direction. In the first mode, when the first pawl is pivoted, for example radially outward, to engage the sun gear to prevent the sun gear from rotating relative to the axle in the first rotational direction, rotation of the sun gear in the second rotational direction can tangentially move the first pawl in the second rotational direction, allowing the first pawl to be pivoted, for example radially inward, out of engagement with the sun gear, thereby allowing the sun gear to freewheel in the second rotational direction. In the second mode, when the second pawl is pivoted, for example radially outward, to engage the sun gear to prevent the sun gear from rotating relative to the axle in the second rotational direction, rotation of the sun gear in the first rotational direction can tangentially move the second pawl in the first rotational direction, allowing the second pawl to be pivoted, for example radially inward, out of engagement with the sun gear, thereby allowing the sun gear to freewheel in the first rotational direction. In this way, the transmission allows the sun gear to be prevented from rotating in the first rotational direction while allowing the sun gear to freewheel in the second rotational direction in the first mode; and to be prevented from rotating in the second rotational direction while allowing the sun gear to freewheel in the first rotational direction in the second mode.

[0032] Optionally, the first and / or second pawl is L-shaped. The first and / or second pawl can have a first body portion extending substantially tangentially to the outer surface of the axle; and a second body portion extending substantially radially inward from the first body portion. The first body portion can have a proximal end proximate the pivot axis of the pawl and a distal end having an engagement surface for engaging an engagement surface of the sun gear. The second body portion can be connected to the distal end of the pawl. The second body portion can carry one or more bearing surfaces as described above. The cam shaft can pivot the pawl radially outward by positioning a cam of the cam shaft under the bearing surface. Tangential movement of the pawl can move the bearing surface away from the cam, allowing the pawl to pivot radially inward.

[0033] Optionally, the transmission includes one or more springs for biasing the first pawl and the second pawl radially inward.

[0034] Optionally, the transmission includes one or more springs for biasing the first pawl tangentially into the first pocket and for biasing the second pawl tangentially into the second pocket.

[0035] Optionally, the transmission comprises a single spring for biasing the first pawl and the second pawl radially inwards, biasing the first pawl tangentially into the first pocket, and biasing the second pawl tangentially into the second pocket.

[0036] Optionally, the transmission comprises a spring having a helically wound section, a first arm extending from a first end of the helically wound section, and a second arm extending from a second end of the helically wound section, wherein a distal end of the first arm is connected to the first pawl, and a distal end of the second arm is connected to the second pawl.

[0037] Optionally, the first arm and the second arm together wrap around the axle more than 360 degrees, such that the first arm pushes the second pawl radially inwards, and the second arm pushes the first pawl radially inwards.

[0038] Optionally, the transmission comprises a plurality of sun gears.

[0039] For each of the above aspects, the following can apply.

[0040] Optionally, the first pawl and the second pawl are separate objects. The first pawl and the second pawl can be connected to each other, for example such that they move in unison. Optionally, the first pawl and the second pawl are formed together as a single body. Thus, the first pawl and the second pawl can together form an integral component.

[0041] Optionally, the transmission comprises one or more bearings, for example rolling bearings or sliding bearings, forming the contact point between the camshaft and the respective pawl. Optionally, the pawl comprises one or more bearings for engaging a cam of the camshaft. Optionally, each pawl comprises two bearings, each bearing engaging a different cam section of the camshaft. The bearings reduce friction between the camshaft and the respective pawl. This can enhance the ease of actuating the pawls. This may, for example, reduce the torque required to rotate the camshaft.

[0042] Optionally, the transmission comprises one or more bearings, for example rolling bearings and / or sliding bearings, mounted for supporting the camshaft inside the axle.

[0043] According to an aspect, there is provided a bicycle derailleur comprising a bridge. The bridge may, for example, be a wheel bridge. The derailleur may, for example, be an internally geared hub derailleur. The bridge may, for example, be a shaft, such as a countershaft, in a derailleur unit. The derailleur may, for example, be a derailleur unit. The bridge has a central axis extending longitudinally therealong. The bridge can be configured to be fixed against rotation. The bridge may, for example, be non-rotatably fixed to a bicycle frame. The derailleur comprises a sun gear rotatably mounted about the bridge. The derailleur comprises a clutch mechanism for selectively preventing rotation of the sun gear about the bridge in at least one rotational direction. The derailleur comprises a cam shaft having a cam for actuating the clutch mechanism. The clutch mechanism comprises at least one pawl hingedly supported in a pocket of the bridge such that the cam can selectively pivot the at least one pawl radially to engage with the sun gear to thereby prevent rotation of the sun gear relative to the bridge in a first rotational direction. The at least one pawl is movable tangentially in the pocket to allow the pawl to move tangentially and radially inwardly relative to the cam to thereby allow the sun gear to freewheel in a second, opposite, rotational direction. Thus, the sun gear can be free to rotate at least in the first rotational direction when the pawl is pivoted out of engagement with the sun gear. When the pawl is pivoted into engagement with the sun gear, rotation of the sun gear in the first rotational direction is prevented, but freewheeling of the sun gear in the second rotational direction is possible.

[0044] Optionally, the derailleur comprises a spring having an arm extending about a radially outer surface of the at least one pawl for biasing the at least one pawl radially inwardly.

[0045] Optionally, the derailleur comprises a spring for biasing the at least one pawl tangentially against a tangential end wall of the pocket.

[0046] According to one aspect, there is provided a bicycle derailleur comprising a bridge. The bridge may, for example, be a wheel bridge. The derailleur may be an internally geared hub derailleur. The bridge may, for example, be a shaft, such as a countershaft, in a crank derailleur. The derailleur may be a crank derailleur unit. The bridge has a central axis extending longitudinally therealong. The bridge can be configured to be fixed against rotation. The bridge may, for example, be fixed non-rotatably to a bicycle frame. The derailleur comprises a sun gear rotatably mounted about the bridge. The derailleur comprises a clutch mechanism for selectively preventing rotation of the sun gear about the bridge in at least one rotational direction. The derailleur comprises a cam shaft having a cam for actuating the clutch mechanism. The clutch mechanism comprises a first pawl and a second pawl, each pawl being hingedly supported in a respective first and second pocket of the bridge, such that the cam can selectively pivot the first pawl radially to engage with the sun gear to prevent rotation of the sun gear relative to the bridge in a first rotational direction, or pivot the second pawl radially to engage with the sun gear to prevent rotation of the sun gear relative to the bridge in a second, opposite, rotational direction. The first pawl is tangentially movable in the first pocket to allow the first pawl to move tangentially and radially inwards relative to the cam to allow the sun gear to freewheel in the second rotational direction; and wherein the second pawl is tangentially movable in the second pocket to allow the second pawl to move tangentially and radially inwards relative to the cam to allow the sun gear to freewheel in the first rotational direction. Thus, the derailleur allows selective prevention of rotation of the at least one sun gear about the bridge in a first rotational direction, while allowing freewheeling in a second rotational direction, in a first mode; and selective prevention of rotation of the at least one sun gear about the bridge in the second rotational direction, while allowing freewheeling in the first rotational direction, in a second mode.

[0047] Optionally, tangential movement of the first or second pawl moves the pawl beyond the cam, such that radial inwards pivoting of the pawl beyond the cam is possible.

[0048] Optionally, the derailleur comprises one or more springs for biasing the first and second pawls radially inwards.

[0049] Optionally, the derailleur comprises one or more springs for biasing the first pawl tangentially into the first pocket and for biasing the second pawl tangentially into the second pocket.

[0050] Optionally, the derailleur comprises a single spring for biasing the first and second pawls radially inwards, biasing the first pawl tangentially into the first pocket, and biasing the second pawl tangentially into the second pocket.

[0051] Optionally, the transmission comprises a spring having a helically wound section, a first arm extending from a first end of the helically wound section, and a second arm extending from a second end of the helically wound section, wherein a distal end of the first arm is connected to the first pawl, and a distal end of the second arm is connected to the second pawl.

[0052] Optionally, the first arm and the second arm together wrap around the axle more than 360 degrees, such that the first arm pushes the second pawl radially inwards, and the second arm pushes the first pawl radially inwards.

[0053] Optionally, the transmission comprises a plurality of sun gears, having associated.

[0054] Optionally, the first pawl and the second pawl are separate objects. The first pawl and the second pawl can be connected to each other, for example such that they move in unison. Optionally, the first pawl and the second pawl are formed together as a single body. Thus, the first pawl and the second pawl can together form an integral component.

[0055] According to an aspect, there is provided a bicycle transmission comprising an axle. The axle can for example be a wheel axle. The transmission can be an internally geared hub transmission. The axle can for example be a shaft, e.g. a countershaft, in a derailleur. The transmission can be a derailleur unit. The axle has a central axis extending longitudinally along the axle. The axle is configured to be fixed against rotation. The axle can for example be non-rotatably fixed to a bicycle frame. The transmission comprises at least one sun gear rotatably mounted around the axle. The transmission comprises at least one clutch mechanism for selectively preventing rotation of the at least one sun gear in at least one rotational direction around the axle. The transmission comprises a camshaft mounted inside the axle for actuating the at least one clutch mechanism. The transmission comprises one or more bearings mounted for supporting the camshaft inside the axle.

[0056] Optionally, the bearings are rolling bearings or sliding bearings.

[0057] For any of the aspects described above, the following can apply.

[0058] Optionally, the camshaft comprises a plurality of cams in a longitudinal direction of the camshaft, each cam for engaging a pawl associated with a consecutive sun gear of the plurality of sun gears, wherein the cams are aligned with each other along a single line parallel to the central axis.

[0059] Optionally, the plurality of sun gears mesh with stepped planetary gears carried by a planetary carrier. Optionally, each sun gear of the plurality of sun gears meshes with a planetary gear portion of a stepped planetary gear carried by the planetary carrier. Optionally, each planetary gear portion has a different radius. Optionally, at least one planetary gear portion meshes with a ring gear.

[0060] Optionally, the transmission comprises a switching mechanism arranged to be adjustable between a first state for establishing torque transfer from the transmission input to the ring gear and from the planet carrier to the transmission output and a second state for establishing torque transfer from the transmission input to the planet carrier and from the ring gear to the transmission output.

[0061] Optionally, the switching mechanism comprises a first actuatable clutch in a transmission path between the transmission input and the planet carrier, a first free wheel in a transmission path between the transmission input and the ring gear; and a second actuatable clutch in a transmission path between the ring gear and the transmission output, and a second free wheel in a transmission path between the planet carrier and the transmission output.

[0062] Optionally, the camshaft is further configured for actuating the switching mechanism. Optionally, the camshaft comprises one or more grooves for actuating the switching mechanism. Optionally, the camshaft is configured for moving the selector axially from the first position to the second position or from the second position to the first position, wherein the first actuatable clutch and / or the second actuatable clutch is configured to switch from a coupled state to a decoupled state or from a decoupled state to a coupled state upon movement of the selector.

[0063] Optionally, the transmission comprises a driving mechanism for selectively moving one or more selectors from their first position to their second position or from their second position to their first position.

[0064] Optionally, the driving mechanism is configured for driving intermediates, each intermediate being individually elastically connected to a selector.

[0065] Optionally, the grooves of the camshaft are configured for driving a plurality of pins along the camshaft in a longitudinal direction, each pin being associated with one of the selectors or one of the intermediates.

[0066] Optionally, the selector is arranged to selectively be in a clamping or a non-clamping mode, the selector having a first portion of a first outer diameter and a second portion of a second outer diameter, wherein the first outer diameter is larger than the second outer diameter, wherein the selector is axially movable between a first position and a second position; wherein when the selector is in the first position, the selector is in the clamping mode, arranged to allow clamping of at least one actuation member of a clutch or brake system; and wherein when the selector is in the second position, the selector is in the non-clamping mode, arranged to not engage the at least one actuation member.

[0067] According to an aspect, there is provided a bicycle derailleur comprising a bridge. The bridge can for example be a wheel bridge. The derailleur can be an internally geared hub derailleur. The bridge can for example be a shaft, e.g. a countershaft, in a crank derailleur. The derailleur can be a crank derailleur unit. The bridge is configured to be fixed against rotation. The bridge can for example be non-rotatably fixed to a bicycle frame. The derailleur comprises at least one sun gear rotatably mounted about the bridge. The derailleur comprises at least one clutch mechanism for selectively preventing rotation of the at least one sun gear about the bridge in at least one rotational direction. The derailleur comprises a camshaft mounted inside the bridge for actuating the at least one clutch mechanism. Mounting the camshaft inside the bridge can provide for efficient actuation of the at least one clutch mechanism.

[0068] Optionally, the derailleur comprises an electromechanical actuator, e.g. an electric motor, configured for moving, e.g. rotating, the camshaft. The electromechanical actuator, e.g. electric motor, can be positioned on or in the bridge. Providing the electromechanical actuator in the bridge can facilitate providing the derailleur with design freedom.

[0069] Optionally, the at least one sun gear is a plurality of sun gears rotatably mounted about the bridge. Optionally, the at least one clutch mechanism comprises a plurality of clutch mechanisms. The plurality of clutch mechanisms can be configured for selectively preventing rotation of one or more of the plurality of sun gears about the bridge in at least one rotational direction. Optionally, each clutch mechanism of the plurality of clutch mechanisms is configured for selectively preventing rotation of an associated one of the plurality of sun gears about the bridge in at least one rotational direction. Optionally, the camshaft comprises a single cam profile for actuating the plurality of clutch mechanisms.

[0070] According to an aspect, there is provided a bicycle derailleur comprising a bridge. The derailleur comprises a clutch mechanism about and / or inside the bridge; the derailleur comprises an electromechanical actuator, e.g. an electric motor, in the bridge and configured for actuating the clutch mechanism. The bridge can for example be a wheel bridge. The derailleur can be an internally geared hub derailleur. The bridge can for example be a shaft, e.g. a countershaft, in a crank derailleur. The derailleur can be a crank derailleur unit.

[0071] Optionally, the derailleur comprises a camshaft configured to be moved by the electromechanical actuator, the camshaft being configured for actuating the clutch mechanism. The camshaft can be mounted inside the bridge.

[0072] Optionally, the bridge is configured to be fixed against rotation. The bridge can for example be non-rotatably fixed to a bicycle frame. The derailleur can further comprise at least one sun gear rotatably mounted about the bridge, wherein the clutch mechanism is configured for selectively preventing rotation of the at least one sun gear about the bridge in at least one rotational direction.

[0073] Optionally, the at least one sun gear comprises a plurality of sun gears rotatably mounted about the axle. Optionally, the transmission comprises a plurality of clutch mechanisms. The plurality of clutch mechanisms can be configured for selectively preventing one or more of the plurality of sun gears from rotating about the axle in at least one rotational direction. Optionally, each of the plurality of clutch mechanisms is configured for selectively preventing an associated one of the plurality of sun gears from rotating about the axle in at least one rotational direction. Optionally, the camshaft comprises a single notched profile for actuating the plurality of clutch mechanisms.

[0074] According to an aspect, there is provided a bicycle transmission comprising an axle. The axle can be a wheel axle, for example. The transmission can be an internally geared hub transmission. The axle can be a shaft in a derailleur transmission, for example, such as a secondary axle. The transmission can be a derailleur unit. The axle is configured to be fixed against rotation. The axle can be non-rotatably fixed to a bicycle frame, for example. The transmission comprises a plurality of sun gears rotatably mounted about the axle. The transmission comprises a plurality of clutch mechanisms for selectively preventing one or more of the plurality of sun gears from rotating about the axle in at least one rotational direction. The transmission comprises a camshaft comprising a single notched profile for actuating the plurality of clutch mechanisms. The single notched profile can comprise one cam or a plurality of cam segments extending axially along the camshaft. The single notched profile, e.g. the cam or the plurality of cam segments, can extend along a line parallel to a central axial axis of the camshaft.

[0075] Optionally, the camshaft is mounted inside the axle.

[0076] Optionally, the transmission comprises an electromechanical actuator, such as an electric motor, configured for moving, e.g. rotating, the camshaft. The electromechanical actuator, such as the electric motor, can be positioned on or in the axle.

[0077] The following can apply for a transmission according to any of the above aspects.

[0078] Optionally, each clutch mechanism comprises at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages a respective sun gear. The pawl engaged with the respective sun gear can selectively prevent the respective sun gear from rotating about the axle in at least one rotational direction.

[0079] Optionally, the at least one pawl is configured to move in a radial direction relative to the axle. The pawl can engage the respective sun gear when in a radially outward position. The pawl can disengage the respective sun gear when in a radially inward position.

[0080] Optionally, each clutch mechanism has a selection bushing associated therewith. The camshaft can comprise one or more grooves for axially moving the selection bushing.

[0081] Optionally, an elastic member, e.g. a compliance mechanism, is included, which connects the camshaft and the electromechanical actuator. The elastic member can be pre-tensioned in two opposite directions.

[0082] Optionally, the derailleur comprises an electric drive for propelling or assisting in propelling the bicycle. The electric drive can be concentrically mounted inside and / or outside the axle. The electric drive can for example be concentrically mounted to the central axis of a hub derailleur comprising the bicycle derailleur. The electric drive can be mounted on another axle, e.g. parallel to the axle. The electric drive can for example be concentrically mounted to the crank axis of a crank derailleur comprising the bicycle derailleur. Optionally, the electric drive comprises an electric motor. Optionally, the electric drive comprises a planetary gear set.

[0083] Optionally, the camshaft or the electric drive comprises a rotation sensor and / or a position sensor.

[0084] Optionally, the derailleur comprises control electronics for controlling the electromechanical actuator. The control electronics can be mounted away from the drive side or non-drive side hub bearing.

[0085] According to an aspect, a bicycle derailleur is provided, which comprises an axle. The axle can for example be a wheel axle. The derailleur can be an internally geared hub derailleur. The axle can for example be a shaft, e.g. a countershaft, in a crank derailleur. The derailleur can be a crank derailleur unit. The axle is configured to be fixed against rotation. The axle can for example be non-rotatably fixed to a bicycle frame. The derailleur comprises at least one sun gear rotatably mounted around the axle. The derailleur comprises at least one clutch mechanism configured to selectively prevent rotation of the at least one sun gear around the axle in a first rotational direction in a first mode, and to selectively prevent rotation of the at least one sun gear around the axle in a second, opposite rotational direction in a second mode. The first mode is also referred to herein as a first configuration. The second mode is also referred to herein as a second configuration. It will be understood that in the first mode, the at least one sun gear can be free to rotate around the axle in the second rotational direction. It will be understood that in the second mode, the at least one sun gear can be free to rotate around the axle in the first rotational direction.

[0086] Optionally, the at least one clutch mechanism is configured to allow free rotation of the sun gear around the axle in at least one or preferably both rotational directions in a third mode. The third mode is also referred to herein as a third configuration.

[0087] Optionally, the at least one clutch mechanism is configured to be actively electronically actuated to select the respective mode of the clutch mechanism.

[0088] Optionally, the at least one sun gear comprises at least two or at least three sun gears rotatably mounted about the axle. The at least one clutch mechanism can comprise a respective clutch mechanism associated with each of the sun gears for selecting the at least first mode and second mode. Thus, each sun gear can have an associated clutch mechanism. Each sun gear can be associated with one of the clutch mechanisms and each clutch mechanism can be associated with one of the sun gears.

[0089] Optionally, the at least two or at least three sun gears have different diameters and are connected by at least one stepped planetary gear rotatably mounted within the carrier. The bicycle derailleur can comprise a ring gear meshing with one of the planetary gears of the stepped planetary gear.

[0090] Optionally, the input of the derailleur is connectable to the ring gear or to the carrier of the planetary gear set. The input of the derailleur can be connected to the ring gear via a freewheel or one-way bearing. The input of the derailleur can be connected to the carrier via a first actuatable clutch mechanism. Optionally, the output of the derailleur is connectable to the ring gear or to the carrier of the planetary gear set. The carrier can be connected to the output of the derailleur via a freewheel or one-way bearing. The ring gear can be connected to the output of the derailleur via a second actuatable clutch mechanism. The first and second actuatable clutches can be part of a switching mechanism. This allows selectively connecting the input to the carrier and the ring gear to the output or connecting the input to the ring gear and the carrier to the output. Thus, the number of available gear ratios can be increased. It is also possible to connect both the input and the output to the carrier or to the ring gear to provide a unit gear ratio.

[0091] Optionally, the or each clutch mechanism comprises a first pawl and a second pawl configured to be actuated by a cam shaft such that in the first mode the first pawl selectively engages with the respective sun gear and in the second mode the second pawl selectively engages with the respective sun gear.

[0092] Optionally, at least one of the clutch mechanisms comprises a passive one-way clutch or one-way bearing to create the first mode or the second mode.

[0093] Optionally, the camshaft is mounted inside the axle for actuating the at least one clutch mechanism. Optionally, the camshaft mounted inside the axle is configured to actuate a respective one of the at least one clutch mechanism. In this way, the camshaft can actuate multiple clutch mechanisms. Optionally, the camshaft mounted inside the axle is configured for actuating a first and a second actuable clutch mechanism. In this way, the camshaft can actuate the connection of the input and output of the transmission with the ring gear and the planet carrier as described above.

[0094] Optionally, the at least one clutch mechanism is designed such that it can be disengaged from the sun gear under load of a torque in at least one direction.

[0095] Optionally, the pawls are designed such that they disengage under a torque load acting on the sun gear and the camshaft is configured to allow anti-disengagement.

[0096] Optionally, there is a roller bearing between the camshaft and the pawls.

[0097] Optionally, there is at least one roller bearing between the camshaft and the axle.

[0098] According to an aspect, there is provided a bicycle transmission, e.g. according to any of the aspects described above, comprising a hub shell for connection to a bicycle wheel. The transmission comprises an axle. The transmission comprises a driver part configured for connection to one or more sprockets. The driver part is mounted to the axle via a first bearing. The hub shell is mounted to the axle via a second bearing and to the driver part via a third bearing. The transmission comprises a transmission system providing a plurality of selectable different gear ratios between the driver and the hub shell. The transmission system is positioned between the second bearing and the third bearing. The transmission comprises an electromechanical actuator for actuating a shift from one gear ratio to another. The transmission comprises control electronics for controlling the electromechanical actuator. The control electronics are positioned outside the second bearing as seen from the transmission system.

[0099] According to an aspect, there is provided a bicycle derailleur, e.g. according to any of the aspects described above, comprising a hub shell for connection to a bicycle wheel. The derailleur comprises a wheel bridge. The derailleur comprises a driver portion for connection to one or more sprockets, wherein the driver portion is mounted to the wheel bridge via a first bearing, and wherein the hub shell is mounted to the wheel bridge via a second bearing and to the driver portion via a third bearing, wherein the hub shell encloses a first cavity between the second bearing and the third bearing. The derailleur comprises a derailleur system providing a plurality of selectable different gear ratios between the driver and the hub shell, the derailleur system being positioned in the first cavity. The derailleur comprises an electromechanical actuator for actuating a shift from one gear ratio to another. The derailleur comprises control electronics for controlling the electromechanical actuator. The control electronics are positioned outside the first cavity.

[0100] Optionally, the hub shell extends beyond the second bearing and encloses the control electronics from the view of the derailleur system.

[0101] Optionally, the control electronics are mounted, e.g. fixed, on the shaft, e.g. concentrically.

[0102] Optionally, the control electronics comprise at least one of a controller, a generator, a battery, a PCB, a wireless receiver / transmitter, an antenna, an LED, a charging plug, a connector or a microchip.

[0103] Optionally, the control electronics are mounted inside, behind and / or connected to a plastic housing.

[0104] Optionally, the hub shell comprises an inner hub shell housing the shaft and an outer hub shell configured for connection to the wheel, e.g. to the rim via spokes. Optionally, the control electronics are positioned to be replaceable upon removal of the inner hub shell from the outer hub shell.

[0105] According to an aspect, there is provided a bicycle derailleur hub comprising a bicycle derailleur according to any of the aspects described above.

[0106] According to an aspect, there is provided a bicycle crank derailleur comprising a bicycle derailleur according to any of the aspects described above.

[0107] According to an aspect, there is provided a bicycle comprising a bicycle derailleur hub and / or a bicycle crank derailleur.

[0108] It will be understood that any of the aspects, features and options described herein can be combined. BRIEF DESCRIPTION OF DRAWINGS

[0109] Embodiments of the present application will now be described in detail with reference to the accompanying drawings, in which:

[0110] Embodiments of the present application will now be described in detail with reference to the accompanying drawings, in which:Figure 1 An example of a derailleur is shown;

[0111] Figure 2 An example of a derailleur is shown;

[0112] Figures 3A-3C An example of an actuator is shown;

[0113] Figures 4A-4I An example of a shift sequence is shown;

[0114] Figure 5A An example of a freewheel clutch is shown;

[0115] Figure 5B An example of an actuatable bi-directional clutch mechanism is shown;

[0116] Figure 6A An example of an actuatable clutch of a shift mechanism is shown; Figure 6B

[0117] An example of an actuatable clutch of a shift mechanism is shown; Figure 7A Figure 7B An example of an actuator is shown;

[0118] Figure 8A An example of a spring is shown;

[0119] Figure 8B An example of a clutch is shown;

[0120] Figure 9A An example of a selector is shown; Figure 9B

[0121] An example of a selector is shown; Figure 10A Figure 10B An example of a bushing is shown;

[0122] Figure 10C An example of a bushing is shown;

[0123] Figure 11A An example of a selector is shown; Figure 11B Figure 11C An example of a bicycle is shown; and

[0124] Figure 12 An example of a derailleur is shown.

[0125] An example of a derailleur is shown. Figure 13 DETAILED DESCRIPTION

[0126] Figure 1 An example of a derailleur is shown. Figure 2 Figure 13 ​​​​A schematic example of a bicycle derailleur 1000 for a human powered vehicle or a light electric vehicle, such as a bicycle, is shown. In Figure 1 and Figure 2 an example, the derailleur 1000 is embodied as a hub derailleur, but it will be appreciated that the derailleur can also be embodied as a crank derailleur as shown in Figure 13 The derailleur 1000 comprises a derailleur input I and a derailleur output O.

[0127] Reference is now made to Figure 1 and Figure 2 Here, the derailleur input I is connected to a rear sprocket 3 for engaging a chain or belt of a chain or belt drive mechanism 300. The sprocket 3 can be part of a freewheel set, for example comprising two or three sprockets. In one particular example, the freewheel set comprises at most two or at most 3 sprockets. In embodiments of a crank derailleur, the derailleur input I can be connected to a crank of the bicycle. Here, the derailleur output O is connected to a hub shell 51 which in turn can be connected to a driven wheel of the bicycle. In embodiments of a crank derailleur, the derailleur output O can be connected to a front sprocket of the chain or belt drive mechanism 300.

[0128] The derailleur 1000 comprises a derailleur system 100, here a planetary gear set 100, arranged for providing a speed reduction and / or an increase between the input I and the output O. The planetary gear set 100 comprises a ring gear 128 and a carrier 126 carrying one or more planetary gears 127. In this example, the carrier 126 carries one or more stepped planetary gears 127 having a plurality of planetary gear portions 127i with different planetary radii. In this example, the stepped planetary gears have four planetary gear portions 127a, 127b, 127c, 127d. The ring gear 128 meshes with one of the different planetary radii 127i. Here, the ring gear 128 meshes with the third planetary gear portion 127c. The planetary gear set 100 further comprises a plurality of different sun gears 129i. The plurality of sun gears meshes with the plurality of different planetary radii 127i, respectively. Here, the plurality of sun gears comprises four sun gears 129a, 129b, 129c, 129d. Note that in this example, the sun gears 129i are positioned such that their diameter gradually increases from one end of the axle 30 to the other end. This can be beneficial in combination with a gradual increase of the diameter of the axle 30 corresponding to the increase of the diameter of the sun gears as described below. The same applies to the planetary gear portions 127i. However, it is also possible to position the sun gear 129d with the smallest diameter between two sun gears with a larger diameter. This can provide a compact construction. Similarly, positioning the planetary gear portion 127d with the largest diameter between two planetary gear portions with a smaller diameter can provide a compact construction.

[0129] The sun gear 129i is rotatably arranged around the fixed axle 30. The fixed axle 30 can be mounted to the bicycle frame for supporting the torque thereon. Thus, the axle can be rotatably fixed to the frame.

[0130] The transmission 1000 comprises a switching mechanism. The switching mechanism comprises a first actuatable clutch mechanism S1 and a second actuatable clutch mechanism S2. The first actuatable clutch mechanism S1 is arranged in the transmission path between the transmission input I and the planet carrier 126. The second actuatable clutch mechanism S2 is arranged in the transmission path between the ring gear 128 and the transmission output O. The transmission 1000 further comprises a first freewheel 11 in the transmission path between the transmission input I and the ring gear 128. Thus, the first freewheel 11 is parallel to the first actuatable clutch mechanism S1. The transmission 1000 further comprises a second freewheel 12 in the transmission path between the planet carrier 126 and the transmission output O. Thus, the second freewheel 12 is in parallel to the second actuatable clutch mechanism S2.

[0131] The first switching mechanism is configured to selectively be in a first state or a second state. In the first state, the first actuatable clutch mechanism S1 and the second actuatable clutch mechanism S2 are both in an open state. Thus, in the first state, torque can be transmitted from the transmission input I via the first freewheel 11 to the ring gear 128 and from the planet carrier 127 via the second freewheel 12 to the transmission output O.

[0132] In this state, the planetary gear set 100 provides a speed reduction from the ring gear 128 to the planet carrier 126 according to the relative sizes of its cooperating rotating components.

[0133] In the second state of the switching mechanism, the first actuatable clutch mechanism S1 and the second actuatable clutch mechanism S2 are both in a closed state. Thus, in the second state, torque can be transmitted from the transmission input I via the first actuatable clutch mechanism S1 to the planet carrier 126 and from the ring gear 128 via the second actuatable clutch mechanism S2 to the transmission output O. The first freewheel 11 and the second freewheel 12 are free to spin in the second state. In the second state, the planetary gear set 100 provides a speed increase from the planet carrier 126 to the ring gear 128 according to the relative sizes of its cooperating rotating components.

[0134] Here, the transmission 1000 further comprises a third freewheel 13 arranged in series with the first actuatable clutch S1 and a fourth freewheel 14 arranged in series with the second actuatable clutch S2. The third and fourth freewheels 13 and 14 can prevent the transmission 1000 from locking up when the bicycle rolls backwards.

[0135] The switching mechanism enables reversing the transmission path through the planetary gear set 100, e.g. from the ring gear 128 to the carrier 126, or vice versa, thereby effectively increasing the range of transmission ratios of the overall transmission 1000. In a first state of the switching mechanism, the transmission 1000 operates in a step-down transmission ratio, reducing the rotational speed from the input I to the output O. In a second state of the switching mechanism, the transmission 1000 operates in a step-up transmission ratio, increasing the rotational speed from the input I to the output O.

[0136] The switching mechanism can also be arranged to selectively be in a third state. In the third state, the first actuatable clutch mechanism S1 can be in its closed state, while the second actuatable clutch mechanism S2 is in its open state, or vice versa. In the third state, the transmission input I and the transmission output O are coupled to the same rotational component of the planetary gear set 100, e.g. both to the carrier 126 or both to the ring gear 128. In the third state, the transmission can operate according to a unit transmission ratio, e.g. a 1 : 1 transmission ratio.

[0137] The transmission 1000 further comprises a clutch mechanism. The clutch mechanism is arranged for selectively engaging a selected one of the plurality of sun gears 129i with the fixed axle 30. Hence, the clutch mechanism comprises a plurality of actuatable bi-directional clutch mechanisms Ci. In this example, the plurality of actuatable bi-directional clutch mechanisms Ci comprises four actuatable bi-directional clutch mechanisms C1, C2, C3, C4. Each actuatable bi-directional clutch mechanism Ci is associated with a respective sun gear 129i for engaging the associated sun gear 129i with the fixed axle 30 in a selected one of two opposite rotational directions. Each actuatable bi-directional clutch mechanism Ci is arranged to be selectively in a first configuration or a second configuration. In the first configuration, the actuatable bi-directional clutch mechanism Ci prevents the respective sun gear 129i from rotating about the fixed axle 30 in a first rotational direction. Herein, preventing the respective sun gear 129i from rotating about the fixed axle 30 in the first rotational direction is also referred to as braking the respective sun gear 129i in the first rotational direction. In the second configuration, the actuatable bi-directional clutch mechanism C2.i prevents the respective sun gear 129i from rotating about the fixed axle 30 in a second rotational direction. Herein, preventing the respective sun gear 129i from rotating about the fixed axle 30 in the second rotational direction is also referred to as braking the respective sun gear 129i in the second rotational direction. The direction in which the sun gear 129i is to be braked depends on the state of the switching mechanism. For example, if the switching mechanism is in its first state, a selected one of the actuatable bi-directional clutch mechanisms Ci can prevent the respective sun gear 129a from rotating in the second rotational direction, whereas if the switching mechanism is in its second state, a selected one of the actuatable bi-directional clutch mechanisms Ci can prevent the respective sun gear 129a from rotating in the first rotational direction.

[0138] When the transmission input I is driven about the fixed axle 30 in the first rotational direction R1 and the switching mechanism is in the first state, the ring gear 128 is also driven in the first rotational direction and, by means of the stepped planetary gear 127, a rotational force is induced on the sun gears 129i in the second opposite rotational direction. By means of braking a selected one of the sun gears 129i in the second rotational direction with a corresponding one of the clutch mechanisms Ci, torque can be transmitted from the ring gear 128 to the carrier 126 according to a reduction drive ratio. However, when the transmission input I is driven about the fixed axle 30 in the first rotational direction and the switching mechanism is in the second state, the carrier 126 is also driven in the first rotational direction and, by means of the stepped planetary gear 127, a rotational force is induced on the sun gears 129i in the first rotational direction. By means of braking a selected one of the sun gears 129i in the first rotational direction with a corresponding one of the clutch mechanisms Ci, torque can be transmitted from the carrier 126 to the ring gear 128 according to an overdrive ratio.

[0139] In each of the first and second configurations, the actuatable bi-directional clutch mechanism Ci can be arranged to prevent the sun gear 129 from rotating in one direction, e.g. by freewheeling, while allowing the sun gear to rotate in the opposite rotational direction. Thus, in the first configuration, the actuatable bi-directional clutch mechanism Ci can be configured to allow the sun gear 129i to freewheel in the second rotational direction, while preventing the sun gear 129i from rotating in the first rotational direction. Further, in the second configuration, the actuatable bi-directional clutch mechanism Ci can be configured to allow the sun gear 129i to freewheel in the first rotational direction, while preventing the sun gear 129i from rotating in the second rotational direction.

[0140] One or more of the actuatable bi-directional clutch mechanisms Ci can also be selectively adjusted to a third configuration. In the third configuration, the actuatable bi-directional clutch mechanism Ci can allow the respective sun gear 129i to freely rotate in both rotational directions about the fixed axle 30. For example, while one of the actuatable bi-directional clutch mechanisms Ci is in the first or second configuration, the other ones of the actuatable bi-directional clutch mechanisms can be in the third configuration.

[0141] If the switching mechanism is in its third state, one or more (e.g. all) of the actuatable bi-directional clutch mechanisms Ci can be configured to be adjustable to the third configuration to allow the ring gear 128 and the planet carrier 126 to rotate in the same direction about the fixed axle 30. In this way, the transmission 1000 can provide a unit transmission ratio between the input I and the output O. If the switching mechanism is in its third state, one or more of the actuatable bi-directional clutch mechanisms Ci can also be adjustable to the second configuration to allow the ring gear 128 and the planet carrier 126 to rotate in the same direction about the fixed axle 30 in the first rotational direction.

[0142] It is possible that one (or more) of the actuatable bi-directional clutch mechanisms Ci is a biased actuatable bi-directional clutch mechanism configured to default in the second configuration and configured to be actively actuated to the first configuration. The biased actuatable bi-directional clutch mechanism can be configured to not have a third configuration. The biased actuatable bi-directional clutch mechanism can be used to prevent that all actuatable bi-directional clutch mechanisms are in the third configuration when the switching mechanism is in the first or second state, which can cause a state in which no torque is transmitted by the transmission. Further, the biased actuatable bi-directional clutch mechanism Ci can be configured to allow the sun gear 129i to freewheel in the first rotational direction, while preventing the sun gear 129i from rotating in the second rotational direction. It is also possible that one (or more) of the actuatable bi-directional clutch mechanisms Ci is a biased actuatable bi-directional clutch mechanism configured to default in the first configuration and configured to be actively actuated to the second configuration.

[0143] In Figure 1 and Figure 2 the planetary gear set 100 comprises four sun gears 129a, 129b, 129c, 129d which are in mesh with four corresponding planetary gear radii 127a, 127b, 127c, 127d of the stepped planetary gear 127. Further, the plurality of clutch mechanisms Ci comprises four actuable bidirectional clutch mechanisms C1, C2, C3, C4 which are arranged to selectively clutch the respective sun gear 129a, 129b, 129c, 129d from the fixed axle 30. An eight- or nine-speed transmission 1000 can thus be obtained. For the nine-speed transmission 1000, exemplary clutch states of the shift mechanism (first and second actuable clutch mechanisms S1, S2) and the clutch mechanisms (actuable bidirectional clutch mechanisms C1, C2, C3, C4) are summarized in Table 1.

[0144]

[0145] For the case that the first actuable bidirectional clutch mechanism C1 is a biased actuable bidirectional clutch mechanism, exemplary clutch states of the shift mechanism (first and second actuable clutch mechanisms S1, S2) and the clutch mechanisms (actuable bidirectional clutch mechanisms C1, C2, C3, C4) of the nine-speed transmission 1000 are summarized in Table 2.

[0146]

[0147] In Tables 1 and 2, the transmission 1000 can be operated in accordance with the unit transmission ratio, but this gear can optionally be omitted. The shift mechanism may, for example, not comprise a third state, but can only be adjusted between a first and a second state. Without unit shifting, the first and second actuable clutches S1, S2 can be actuated synchronously with each other while switching the two clutches S1, S2 between their closed and open states. This can simplify the actuation construction. The benefit of the unit gear is an increase in the transmission ratio range. Further, with unit shifting, each upshift or downshift to an adjacent higher or lower gear can only involve switching one of the first and second actuable clutch mechanisms S1, S2.

[0148] In Tables 1 and 2, the actuable bidirectional clutch mechanisms further comprise an optional third configuration. Alternatively, the actuable bidirectional clutch mechanisms Ci can only be adjusted between a first and a second configuration. Figure 1 and Figure 2The same transmission can also be used to provide a five-speed transmission. For a five-speed reduction transmission, the clutch mechanisms C1, C2, C3, and C4 can omit the first configuration, i.e., provide the second and third configurations. For a five-speed increase transmission, the clutch mechanisms C1, C2, C3, and C4 can omit the second configuration, i.e., provide the first and third configurations. Similarly, for a five-speed transmission, one of the clutches C1, C2, C3, and C4 (e.g., C1) can be a freewheel.

[0149] Without clutches S1 and S2, we can use only gears 1 to 4, or only gears 5 to 9, where gear 5 is in a freewheel state.

[0150] There is no clutch between C1 and C4; it is a three-speed transmission.

[0151] exist Figure 1 and Figure 2 In this example, axle 30 has a central axis A. Axle 30 may be, for example, a wheel axle or countershaft in a crank transmission. Actuators for actuating clutch mechanisms C1, C2, C3, and C4 are mounted inside axle 30. In this example, the actuator is an electromechanical actuator. In this example, the electromechanical actuator includes an electric motor 32. The actuator in this example includes a camshaft 34 mounted inside axle 30 for actuating clutch mechanisms C1, C2, C3, and C4. The electromechanical actuator 32 is configured to rotate the camshaft 34 inside axle 30.

[0152] Figure 13 A schematic example of a bicycle derailleur 1000, embodied as a crank-driven derailleur, for use in a human-powered vehicle or a light electric vehicle (e.g., a bicycle), is shown. An axle 30 is non-rotatably connected to the housing 308 of the crank-driven derailleur. The axle 30 is offset from and parallel to the crank axle 1004. In this example, the crank axle 1004 includes a first pulley 302, and a second pulley 304 is mounted to the input section I of the derailleur for driving the input section. Here, the input section is driven by a belt 306. It should be understood that the input section I of the derailleur can also be driven by a chain, universal joint, offset gear, etc. The output section of the derailleur is connected to a front sprocket 1009 for engaging the chain or belt of the chain or belt drive mechanism 300. Here, the front sprocket 1009 is offset relative to the crank axle 1004. It is evident that the front sprocket 1009 can also be coaxial with the crank axle 1004. The derailleur 1000 in this example is similar to the reference... Figure 1 and Figure 2The described transmission. In this example, an electric motor 310 is provided in the housing 308. Here the electric motor 310 drives the transmission input I, in particular via a belt 306. The transmission ratio from the crank bridge 1004 to the transmission input I is chosen to be a speed-increasing transmission ratio, in order to reduce the torque on the transmission 100. The speed-increasing transmission ratio from the crank bridge to the transmission input can for example be about 2.5 or less.

[0153] Figure 3A An example of an actuator is shown. In Figure 3A , an electromechanical actuator 32 and a camshaft 34 are visible. Here, the camshaft comprises a plurality of cams Ni, in particular six cams N1, N2, N3, N4, N5, N6. Here, the camshaft 34 comprises a single recess profile for actuating the plurality of clutch mechanisms. The single recess profile is formed by the plurality of cams Ni extending in an axial direction of the camshaft 34. In this example, the single recess profile, e.g. the plurality of cams Ni, extends along a line parallel to a central axial axis A of the camshaft 34.

[0154] Figure 3B An actuator of Figure 3A is shown, wherein pawls Pi, in particular pawls P1, P2A, P2B, P3A, P3B, P4A, P4B are shown. Each clutch mechanism C1, C2, C3, C4 comprises one or more pawls Pi configured to be actuated by the camshaft 34. In this example, the second clutch mechanism C2, the third clutch mechanism C3 and the fourth clutch mechanism C4 each comprise a first pawl PiA and a second pawl PiB configured to be actuated by the camshaft 34, such that in a first mode the first pawl PiA is selectively engaged with the respective sun gear 129i and in a second mode the second pawl PiB is selectively engaged with the respective sun gear 129i.

[0155] In this example, each pawl Pi comprises two bearing surfaces Pis which are supported on the cam shaft 34 and can be lifted by the cams Ni. Here, the bearing surfaces Pis are formed as bearings, for example roller bearings or sliding bearings. In this example, the first pawl P1 of the first clutch mechanism C1 comprises two bearing surfaces, here two rolling bearings P1s. The bearing surfaces P1s are supported on the cam shaft 34 and are lifted by the cams N1 and N2. Here, a circumferential groove is provided between the cams N1 and N2 on the cam shaft 34 as a gap for the first pawl P1. In this example, the first pawl P2A and the second pawl P2B of the second clutch mechanism C2 each comprise two bearing surfaces, here two roller bearings P2As, P2Bs. The bearing surfaces P2As, P2Bs are supported on the cam shaft 34 and are lifted by the cams N2 and N3. A circumferential groove is provided here in the cam shaft 34 between the cams N2 and N3 as a gap for the first pawl P2A and the second pawl P2B. In this example, the first pawl P3A and the second pawl P3B of the third clutch mechanism C3 each comprise two bearing surfaces, here two roller bearings P3As, P3Bs. The bearing surfaces P3As, P3Bs are supported on the cam shaft 34 and are lifted by the cams N3 and N4. A circumferential groove is provided here in the cam shaft 34 between the cams N3 and N4 as a gap for the first pawl P3A and the second pawl P3B. In this example, the first pawl P4A and the second pawl P4B of the fourth clutch mechanism C4 each comprise two bearing surfaces, here two roller bearings P4As, P4Bs. The bearing surfaces P4As, P4Bs are supported on the cam shaft 34 and are lifted by the cams N5 and N6. A circumferential groove is provided here in the cam shaft 34 between the cams N5 and N6 as a gap for the first pawl P4A and the second pawl P4B.

[0156] It can be understood that it is also possible for the cams of the cam shaft 34 to be provided with bearings, such as roller bearings or sliding bearings, for contacting the pawls. In examples, the actuator comprises a rotation sensor and / or a position sensor. Thus, the gearwheel in which the actuator is positioned can be monitored. For example, the rotational position of the electromechanical actuator 32 and / or the cam shaft 34 can be monitored.

[0157] Figure 7B An example is shown in which two sun gears 129a, 129b are shown mounted on the axle 30, covering the respective pawls P1, P2A, P2B. For the sake of clarity, Figure 7B The sun gears 129c, 129d are not shown in

[0158] As can be seen in more detail from Figures 4A-4H In this example, the pawls associated with the larger sun gears also have larger rolling bearings for the bearing surfaces than the pawls associated with the smaller sun gears.

[0159] In this example, in each clutch mechanism C1, C2, C3, C4, the first pawls P1, P2A, P3A, P4A and the second pawls P2B, P3B, P4B are configured to pivot about their respective pivot axes. In this example, each pawl includes two protrusions Pip that form the end of the pivot axle P of the corresponding pawl. Figure 3B The image indicates the protrusion P2Bp of the second pawl P2B of the second clutch mechanism C2. It can be understood that, in this example, other pawls have similar protrusions.

[0160] from Figure 3B As can be seen, the pawls of clutch mechanisms C1, C2, C3, and C4 are positioned to rotate about the central axis A. Specifically, pawl P1 of the first clutch mechanism C1 is rotatably positioned about the central axis A relative to the pawls of the second, third, and fourth clutch mechanisms C2, C3, and C4. The first pawl P2A and the second pawl P2B of the second clutch mechanism C2 are positioned to rotate about the central axis A relative to the pawls of the first, third, and fourth clutch mechanisms C1, C3, and C4. The first pawl P3A and the second pawl P3B of the third clutch mechanism C3 are positioned to rotate about the central axis A relative to the pawls of the first, second, and fourth clutch mechanisms C1, C2, and C4. The first pawl P4A and the second pawl P4B of the fourth clutch mechanism C4 are positioned to rotate about the central axis A relative to the pawls of the first, second, and third clutch mechanisms C1, C2, and C3. Therefore, the first position of at least one pawl in at least one of the clutch mechanisms rotates about the central axis relative to the second position of at least one pawl in at least one of the clutch mechanisms. Here, the first position of at least one first pawl and the second pawl in the clutch mechanism rotates about the central axis relative to the second position of at least one other first pawl and the second pawl in the clutch mechanism. As will be combined Figures 4A-4H In one example, the pawls are positioned such that rotation of the camshaft in a single direction sequentially actuates the corresponding pawls, thereby selecting the transmission ratio in ascending or descending order. In this example, the pawls are spaced 40 degrees apart. Therefore, the camshaft can rotate 40 degrees eight times to obtain nine different transmission ratios.

[0161] Figure 3B Two bearings 36, which are rolling bearings (but sliding bearings are also possible), are shown around the camshaft 34 for supporting the camshaft 34 inside the axle 30.

[0162] Figure 3C Showing Figure 3A and 3B The actuator is located inside the axle 30. For example... Figure 3CAs shown, in this example, the axle 30 has a plurality of axle sections of different outer diameters. In this example, a first axle section 30A has a first outer diameter. In this example, the first sun gear 129a and the second sun gear 129b can be mounted on the first axle section 30A. A second axle section 30B has a smaller outer diameter than the first axle section 30A. In this example, the third sun gear 129c can be mounted on the second axle section 30B. A third axle section 30C has a smaller outer diameter than the second axle section 30B. In this example, the fourth sun gear 129d can be mounted on the third axle section 30C. Thus, the axle 30 has different outer radii at the locations of the different sun gears 129i among the plurality of sun gears. The different outer diameters of the axle sections 30A, 30B, 30C can facilitate assembly of the clutch mechanisms C1, C2, C3, C4. The different outer diameters of the axle sections 30A, 30B, 30C can provide larger diameter axle sections to support sun gears that transmit higher torques to the axle 30. Preferably, the torque is supported from the axle 30 onto the bicycle frame on the side of the axle 30 having the largest axle section diameter, i.e. the non-drive side in this example.

[0163] As can also be seen from Figure 3C It can also be seen that, for different ones of the plurality of clutch mechanisms C1, C2, C3, C4, the radial distance between the pivot axis p of the pawl and the central axis A of the axle 30 is different. For all of the pawls Pi, the pivot axis p of the respective pawl Pi is positioned such that the pivot axle P is positioned directly below the surface of the respective axle section. In this example, the first radial distance between the pivot axis p of the first pawl P1 of the first clutch mechanism C1 and the central axis A of the axle 30 is equal to the second radial distance between the pivot axes p of the first and second pawls P2A, P2B of the second clutch mechanism C2 and the central axis A of the axle 30. In this example, the first radial distance between the pivot axes p of the first and second pawls P2A, P2B of the second clutch mechanism C2 and the central axis A of the axle 30 is greater than the third radial distance between the pivot axes p of the first and second pawls P3A, P3B of the third clutch mechanism C3 and the central axis A of the axle 30. In this example, the third radial distance between the pivot axes p of the first and second pawls P3A, P3B of the third clutch mechanism C3 and the central axis A of the axle 30 is greater than the fourth radial distance between the pivot axes p of the first and second pawls P4A, P4B of the fourth clutch mechanism C4 and the central axis A of the axle 30. It can be appreciated that, in this example, the radial distance between the top of the cams N5, N6 of the fourth clutch mechanism C4 and the central axis A is also less than the radial distance between the top of the cams N1, N2, N3, N4 of the first, second, and third clutch mechanisms C1, C2, C3 and the central axis.

[0164] The pivot axis p of the pawl is held at a radial distance from the central axis A by a recess formed in the carrier 30. In particular, a protrusion Pip of the end of the pivot carrier P forming the respective pawl is nested in a recess formed in the carrier 30. Figures 4A-4H The sequence of gear shifting using the transmission of Figures 1-3C is shown. In this example, when the transmission input I is driven in the first rotational direction R1 about the stationary carrier 30 and the switching mechanism is in the first state, the ring gear 128 is also driven in the first rotational direction and, by way of the stepped planetary gear 127, a rotational force in the second, opposite rotational direction is induced on the sun gear 129i. By braking a selective one of the sun gears 129i in the second rotational direction using a corresponding one of the clutch mechanisms Ci, torque can be transmitted from the ring gear 128 to the planet carrier 126 according to a reduction drive ratio.

[0165] Figure 4A A situation is shown in which the transmission input I is driven in the first rotational direction R1 about the stationary carrier 30 and the switching mechanism is in the first state. In Figure 4A the first actuatable bidirectional clutch mechanism C1 is shown in the second configuration. In this example, the first actuatable bidirectional clutch mechanism C1 is a biased actuatable bidirectional clutch mechanism with only a single pawl P1. The pawl P1 is not actuated by the cams N1, N2 in the first position. The biased actuatable bidirectional clutch mechanism C1 comprises a freewheel clutch 15 which allows rotation in the first rotational direction R1 and prevents rotation in the second rotational direction R2. Figure 5A An example of the freewheel clutch 15 of the biased actuatable bidirectional clutch mechanism C1 is shown. Here, the freewheel clutch 15 comprises a plurality of rollers 15r, such as balls or rollers, between an inner race 15i and an outer race 15o. In this example, the outer race 15o is provided with a sawtooth profile. Thus, the largest sun gear 129a is braked and torque is transmitted from the input I via the ring gear 128 to the planetary gear 127 and further via the planet carrier 126 to the output O. The drive ratio is determined by the first sun gear 129a and the first planetary gear portion 127a and constitutes the smallest drive ratio (first gear, reduction drive).

[0166] Figure 4B A situation is shown in which the transmission input I is driven in the first rotational direction R1 about the stationary carrier 30 and the switching mechanism is in the first state. In Figure 4BIn the middle, the second actuatable bidirectional clutch mechanism C2 is shown in the second configuration. The cam shaft has been rotated to the second position. The second pawl P2B is actuated in the second position by the cams N2, N3. The engagement surface of the second pawl P2B engages the corresponding engagement surface associated with the second sun gear 129b and prevents rotation in the second rotational direction R2. Thus, the second sun gear 129b is braked, torque is transmitted from the input I via the ring gear 128 to the planetary gear 127, and via the carrier 126 to the output O. The transmission ratio is determined by the second sun gear 129b and the second planetary gear part 127b and constitutes the next higher transmission ratio (second gear, underdrive).

[0167] Figure 4C A situation is shown in which the transmission input I is driven in the first rotational direction R1 about the fixed axle 30 and the switching mechanism is in the first state. Figure 4C In the middle, the third actuatable bidirectional clutch mechanism C3 is shown in the second configuration. The cam shaft has been rotated to the third position. The second pawl P3B is actuated in the third position by the cams N3, N4. The engagement surface of the second pawl P2B engages the corresponding engagement surface associated with the third sun gear 129c and prevents rotation in the second rotational direction R2. Thus, the fourth sun gear 129d is braked, torque is transmitted from the input I via the ring gear 128 to the planetary gear 127, and via the carrier 126 to the output O. The transmission ratio is determined by the third sun gear 129c and the third planetary gear part 127c and constitutes the next higher transmission ratio (third gear, underdrive).

[0168] Figure 4D A situation is shown in which the transmission input I is driven in the first rotational direction R1 about the fixed axle 30 and the switching mechanism is in the first state. Figure 4D In the middle, the fourth actuatable bidirectional clutch mechanism C4 is shown in the second configuration. The cam shaft has been rotated to the fourth position. The second pawl P4B is actuated in the fourth position by the cams N5, N6. The engagement surface of the second pawl P4B engages the corresponding engagement surface associated with the fourth sun gear 129d and prevents rotation in the second rotational direction R2. Thus, the fourth sun gear 129d is braked, torque is transmitted from the input I via the ring gear 128 to the planetary gear 127, and via the carrier 126 to the output O. The transmission ratio is determined by the fourth sun gear 129d and the fourth planetary gear part 127d and constitutes the next higher transmission ratio (fourth gear, underdrive).

[0169] Figure 4EA situation is shown in which the cam shaft 34 is rotated to a fifth position. In this fifth position, the fourth actuatable bi-directional clutch mechanism C4 is in a third configuration. As such, neither the first pawl P4A nor the second pawl P4B is lifted by the cams N5, N6. In this situation, the switching mechanism is switched to a third state. As such, the ring gear 128 and the planet carrier 126 are coupled to rotate together. Torque is transmitted from the input I via the ring gear and / or the planet carrier 126 to the output O. It will be appreciated that in this example, the cams N5, N6 of the fourth clutch mechanism C4 are wider than the cams N1-N4 of the other clutch mechanisms C1, C2, C3. Thus, a smooth handover from the fourth gear to the fifth gear (and from the fifth gear to the sixth gear) can be achieved. This situation constitutes the next higher gear ratio, which corresponds to a unit gear ratio (fifth gear, unit gear ratio).

[0170] Next, the switching mechanism is switched to a second state. When the transmission input I is driven in a first rotational direction about the stationary axle 30 and the switching mechanism is in the second state, the planet carrier 126 is also driven in the first rotational direction and, by way of the stepped planet gear 127, causes a rotational force in the first rotational direction on the sun gear 129i. By braking a selective one of the sun gears 129i in the first rotational direction with a corresponding one of the clutch mechanisms Ci, torque can be transmitted from the planet carrier 126 to the ring gear 128 according to an overdrive gear ratio.

[0171] Figure 4F A situation is shown in which the transmission input I is driven in a first rotational direction R1 about the stationary axle 30 and the switching mechanism is in the second state. Figure 4F The fourth actuatable bi-directional clutch mechanism C4 is shown in a first configuration in the middle. The cam shaft has been rotated to a sixth position. The first pawl P4A is actuated in the sixth position by the cams N5, N6. The engagement surface of the first pawl P4A engages a corresponding engagement surface associated with the fourth sun gear 129d and prevents rotation in the first rotational direction R1. Thus, the fourth sun gear 129d is braked, torque is transmitted from the input I via the planet carrier 126 to the planet gear 127 and via the ring gear 128 to the output O.

[0172] The gear ratio is determined by the fourth sun gear 129d and the fourth planet gear portion 127d and constitutes the next higher gear ratio (sixth gear, speed-up transmission).

[0173] Figure 4G A situation is shown in which the transmission input I is driven in a first rotational direction R1 about the stationary axle 30 and the switching mechanism is in the second state. Figure 4FThe third actuatable bidirectional clutch mechanism C3 is shown in the first configuration in Fig. 6. The cam shaft has been rotated to the seventh position. The first pawl P3A is actuated by the cams N3, N4 in the seventh position. The engagement surface of the first pawl P3A engages the corresponding engagement surface associated with the third sun gear 129c and prevents rotation in the first rotational direction Rl. Thus, the third sun gear 129c is braked, torque is transmitted from the input I via the planet carrier 126 to the planet gears 127 and via the ring gear 128 to the output O. The transmission ratio is determined by the third sun gear 129c and the third planetary gear part 127c and constitutes the next higher transmission ratio (seventh gear, speed increasing transmission).

[0174] Figure 4H A situation is shown in which the transmission input I is driven in the first rotational direction Rl about the fixed axle 30 and the switching mechanism is in the second state. Figure 4G The second actuatable bidirectional clutch mechanism C2 is shown in the first configuration in Fig. 5. The cam shaft has been rotated to the eighth position. The first pawl P2A is actuated by the cams N2, N3 in the eighth position. The engagement surface of the first pawl P2A engages the corresponding engagement surface associated with the second sun gear 129b and prevents rotation in the first rotational direction Rl. Thus, the second sun gear 129b is braked, torque is transmitted from the input I via the planet carrier 126 to the planet gears 127 and via the ring gear 128 to the output O. The transmission ratio is determined by the second sun gear 129b and the second planetary gear part 127b and constitutes the next higher transmission ratio (eighth gear, speed increasing transmission).

[0175] Figure 4I A situation is shown in which the transmission input I is driven in the first rotational direction Rl about the fixed axle 30 and the switching mechanism is in the second state. Figure 4H The first actuatable bidirectional clutch mechanism Cl is shown in the first configuration in Fig. 4. The cam shaft has been rotated to the ninth position. The engagement surface 38 of the pawl Pl engages the corresponding engagement surface 40 associated with the first sun gear 129a and prevents rotation in the first rotational direction Rl. Thus, the first sun gear 129a is braked, torque is transmitted from the input I via the planet carrier 126 to the planet gears 127 and via the ring gear 128 to the output O. The transmission ratio is determined by the first sun gear 129a and the first planetary gear part 127a and constitutes the next higher transmission ratio (ninth gear, speed increasing transmission).

[0176] It is to be understood that in the course of the successive gears from the lowest (here: first) to the highest (here: ninth) gear, the sun gears 129i are first used in the order from largest to smallest and subsequently in the order from smallest to largest.

[0177] Figure 5B An example of a sun gear 129i with an actuatable bi-directional clutch mechanism Ci is shown. The pawls PiA, PiB are generally L-shaped in this example. The pawls PiA, PiB have a first body portion 44 extending from the pivot axle P to an engagement surface 38. The first body portion extends substantially tangentially to the outer surface of the axle 30 with the pivot axle P being articulatedly supported in a pocket 48 of the axle 30. The pawls PiA, PiB have a second body portion 46 extending substantially radially inwardly. The second body portion 46 carries a support surface Pis. Here, the second body portion has two axially oriented bosses on which roller bearings forming the support surface Pis are mounted. In this example, the engagement surface 38 of the pawl Pi and the corresponding engagement surface 40 of the sun gear 129i are angled with respect to the radial direction. The angle is chosen such that moving the engagement surfaces 38, 40 relative and towards each other tends to move the pawl Pi radially inwardly. In this way, the pawl Pi is biased to disengage. A spring can be added for spring-biasing the pawl Pi to disengage. Figure 7A An example of a pawl Pi biased by a spring 121 is shown. In this way, the actuatable bi-directional clutch mechanism Ci is biased to disengage. In the first configuration and the second configuration, the presence of the cam Ni below the support surface Pis prevents the engagement surfaces 38, 40 from disengaging when pressed against each other. In the first configuration, rotating the sun gear 129i in the first rotational direction Ri will force the engagement surfaces against each other, the first pawl PiA is pushed in the pocket 48 towards the radial end wall 49 of the pocket 48 and the rotation of the sun gear 129i in the first rotational direction is blocked (see corresponding Figure 5B In the first configuration, rotating the sun gear 129i in the first rotational direction Ri will force the engagement surfaces against each other, the first pawl PiA is pushed in the pocket 48 towards the radial end wall 49 of the pocket 48 and the rotation of the sun gear 129i in the first rotational direction is blocked (see corresponding Figure 4G ). Figure 5BA specific scenario is illustrated where the clutch mechanism Ci is in a first configuration and the sun gear 129i is driven in a second rotational direction R2. The actuable bidirectional clutch mechanism Ci is configured such that, in the first configuration, the sun gear 129i is prevented from rotating in the first rotational direction R1 but is able to rotate (free-spin) in the second rotational direction R2. In this case, a protrusion 50 on the inner periphery of the sun gear 129i pushes the first pawl PiA in the first rotational direction, tangentially moving the pawl PiA within the recess 48 away from the radial end wall 49 of the recess, causing the support surface Pis to fall onto the cam Ni. This causes the first pawl PiA to pivot radially inward, such that the radius of the engagement surface 38 of the pawl PiA is smaller than the radius of the engagement surface 40 of the sun gear 129i. As a result, the sun gear 129i can free-spin in the first rotational direction R1 while the clutch mechanism Ci is in the first configuration. In this example, the first pawl PiA has a protrusion 52, such as a ridge, on its radially outward surface. The protrusion 52 can be captured by the protrusion 50 of the sun gear 129i to facilitate tangential movement of the pawl PiA, thereby dropping the cam Ni. In this example, a spring or other elastic element is provided to bias the pawl PiA back into the recess 48. The spring or other elastic element can pull the pawl so that the pivot axle P tangentially abuts against the radial end wall of the recess 48. It can be understood that, similarly, the actuable bidirectional clutch mechanism Ci is configured such that, in the second configuration, the sun gear 129i is prevented from rotating in the second rotational direction R2, but is able to rotate (free-spin) in the first rotational direction R1.

[0178] Figure 8A An example is shown in which the spring 121 has a combined function of biasing pawls PiA and PiB into a recess 48 and of radially inwardly biasing pawls PiA and PiB to achieve bias disengagement of the engagement surfaces 38 and 40. In this example, the spring 121 includes a helical winding segment 121a. Two arms 121b and 121c extend from the ends of the helical winding segment. In this example, the distal ends of arms 121b and 121c overlap. Thus, the spring 121 is wound around the axle 30 more than 360 degrees. The distal ends of arms 121b and 121c are each provided with hooks 121d and 121e. In this example, the spring includes a single helical winding segment 121a. It is understood that the spring may also include more than one, for example, two helical winding segments. Figure 7B As shown, hooks 121d and 121e engage the corresponding pawls PiA and PiB. Therefore, the tension of spring 121 biases pawls PiA and PiB, causing the pivot axle P to tangentially abut against the radial end wall of recess 48. Furthermore, the arms 121b and 121c of the spring are positioned in the circumferential grooves Pig of pawls PiA and PiB (see example...). Figure 7A and Figure 7Bgrooves P1g, P2g, P3g, P4g in the hub 40, such that the tension of the spring 121 biases the pawls PiA and PiB radially inwards. Here, the arms wrap around the pawls PiA, PiB. In this example, the first arm 121b pushes the second pawl PiB radially inwards and the second arm 121c pushes the first pawl PiA radially inwards. Here, the arms are also positioned in the circumferential groove 30g of the outer surface of the axle 30. In this example, the spring 121 extends between the pawls PiA, PiB, i.e. a first end 121d of the spring is attached to the first pawl PiA and a second end 121e of the spring is attached to the second pawl PiB. In this way, the spring 121 pulls the pawls PiA, PiB towards each other. It is appreciated that each pawl can also have one or more separate springs associated therewith.

[0179] Returning to Figure 1 , Figure 2 and Figure 3A , the camshaft 34 is further configured for actuating the switching mechanism. In this example, the camshaft comprises one or more grooves 54, here two grooves, for actuating the switching mechanism. The camshaft 34 is configured for axially moving the selector 56 from the first position to the second position or from the second position to the first position. Here, the selector 56 comprises a pen-like piece 58 extending into the groove 54. It is appreciated that the groove 54 is shaped such that a rotation of the camshaft 34 will axially move the pen-like piece 58, thereby moving the selector 56. The first actuatable clutch S1 and / or the second actuatable clutch S2 are configured to switch from the coupled state to the uncoupled state or from the uncoupled state to the coupled state upon axial movement of the selector 56. In this example, the groove 54 is shaped such that the first actuatable clutch S1 and the second actuatable clutch S2 are substantially simultaneously switched from the coupled state to the uncoupled state or from the uncoupled state to the coupled state.

[0180] The actuatable clutches S1, S2 of the switching mechanism can be similar or identical to the clutches described in WO2018 / 199757A2, WO2020 / 085911A2, WO2021 / 080431A1 or WO2021 / 249945A1, the entire contents of which are incorporated herein by reference. Reference is made to Figure 6A and Figure 6BThe actuatable clutch S1, S2 can have a first rotatable unit 80 comprising at least one first abutment surface 82 and a second rotatable unit 84 comprising at least one second abutment surface 86 arranged for selectively engaging the first abutment surface. The first abutment surface 82 and the second abutment surface 86 are adapted to each other allowing disengagement under load, preferably in both directions. The actuatable clutch S1, S2 can have a third rotatable unit 88 comprising at least one retaining member 90. The third rotatable unit 88 is arranged relative to the second rotatable unit 84 to be selectively in a first mode ( Figure 6A ) or in a second mode ( Figure 6B ). In the first mode, the at least one retaining member 90 locks the at least one second abutment surface 86 for rotationally coupling the second rotatable unit 84 to the first rotatable unit 80, e.g. in both rotational directions. In the second mode, the at least one retaining member 90 releases the at least one second abutment surface 86 to uncouple the second rotatable unit 84 from the first rotatable unit 80. The actuatable clutch can comprise an actuator for moving the third rotatable unit relative to the second rotatable unit from a first position ( Figure 6A ) to a second position ( Figure 6B ) or from the second position to the first position. Here, the second rotatable unit 84 carries a gripping member 92. The gripping member has the second abutment surface 86. The gripping member 92 is pivotally connected to the second rotatable unit 84. In the first position, here the retaining member 90 is positioned to push the second abutment surface 86 of the gripping member 92 radially outward into engagement with the first engagement surface 82. In this example, the second engagement surface 86 and the corresponding first engagement surface 82 are angled relative to the radial direction. The angle is chosen such that moving the engagement surfaces 82, 86 relative and towards each other tends to move the gripping member 92 radially inward. In this way, the gripping member 92 is biased to disengage. A spring can be added for spring biasing the gripping member 92 to disengage. Thus, the actuatable clutch S1, S2 is biased to disengage. In the first position, the presence of the retaining member below the gripping member 92 prevents the engagement surfaces 82, 86 from disengaging when pressed against each other. In the second position, the retaining member 90 is positioned to allow the gripping member 92 to pivot radially inward to allow the second abutment surface 86 to disengage from the first engagement surface 82.

[0181] The third rotatable unit 88 includes at least one actuating member 94 arranged to move the third rotatable unit 88 relative to the second rotatable unit 84 from a first position to a second position or from a second position to a first position. In this example, the actuable clutches S1, S2 also include a fourth unit 96, which includes a selector 98. The fourth unit 96 may be non-rotating, for example, relative to the axle 30. The selector is arranged to selectively be in a gripping mode or a non-gripping mode. In the gripping mode, the selector 98 is arranged to grip at least one actuating member 94 to rotate the third rotatable unit 88 relative to the second rotatable unit 84 from a first position to a second position or from a second position to a first position. In the non-gripping mode, the selector 98 is arranged not to engage the at least one actuating member 94.

[0182] Figure 9A and Figure 9B An example of a selector 98 is shown. In this example, the selector includes one or more grooves 120 fixed relative to the axle 30. The selector further includes a selector bushing 122 axially movable relative to the axle 30. The bushing 122 includes a first segment 122A having a first outer diameter and a second segment 122B having a second outer diameter smaller than the first outer diameter. In this example, the bushing 122 is axially movable by a pin 124 residing in a groove 54 of the camshaft 34. The bushing 122 can be moved to a first position ( Figure 9A ) and second position ( Figure 9B ).like Figure 9A and Figure 9B As shown, in this example, the two actuating members 94A and 94B are slightly different. In particular, the cutouts 126A and 126B of the corresponding actuating members 94A and 94B are positioned differently.

[0183] like Figure 9A As shown, with the bushing in the first position, the first actuating member 94A rests with its radially inward end on the first segment 122A of the bushing's larger outer diameter. This prevents the first actuating member 94A from entering the groove 120. Figure 8A As shown, with the bushing in the first position, the second actuating member 94B aligns its cut 126B with the first segment 122A of the bushing's larger outer diameter. This allows the second actuating member 94A to enter the groove 120. Figure 9B As shown, with the bushing in the second position, the second actuating member 94B rests with its radially inward end on the first section 122A of the bushing's larger outer diameter. This prevents the second actuating member 94B from entering the groove 120. Figure 9BAs shown, in the case where the bushing is in the second position, the first actuation member 94A has its cut-out 126A aligned with the first section 122A of larger outer diameter of the bushing. In this way, the first actuation member 94A can be brought into the groove 120. Once the first actuation member 94A or the second actuation member 94B is brought into the groove 120, the third rotatable unit 88 is temporarily stopped, causing the third rotatable unit to rotate relative to the second rotatable unit 84. The third rotatable unit 88 will rotate relative to the second rotatable unit 84 from a first position ( Figure 6A ) to a second position ( Figure 6B ) or from the second position to the first position. In this way, the actuatable clutch S1, S2 will be engaged or disengaged. After the third rotatable unit 88 is moved from the first position to the second position or from the second position to the first position, the respective actuation member 94A, 94B is knocked out of the respective groove 120 by a return member 128, for example co-rotating with the second rotatable unit 84.

[0184] Optionally, a resilient member is placed in the connection between the camshaft 34 and the selection bushing 122. The resilient member allows the camshaft 34 to have performed a movement for axially moving the bushing 122, while at the same time the bushing 122 is (temporarily) prevented from actually performing the axial movement, for example due to being prevented from performing the axial movement by one or more of the actuation members 94A, 94B. For example, when the first actuation member 94A is in the groove 120, the bushing 122 can be prevented from moving from the first position to the second position. In this case, if the camshaft is rotated to axially move the bushing 122 from the first position to the second position, the resilient member can be deformed. Once the first actuation member 94A is raised out of the groove, the bushing 122 can perform (or complete) the axial movement that has been imposed by the camshaft 34. For example, when the second actuation member 94B is in the groove 120, the bushing 122 can be prevented from moving from the second position to the first position. In this case, if the camshaft is rotated to axially move the bushing 122 from the second position to the first position, the resilient member can be deformed. Once the second actuation member 94B is raised out of the groove, the bushing 122 can perform (or complete) the axial movement that has been imposed by the camshaft 34.

[0185] The resilient member can be a compliant mechanism. The resilient member can for example be pre-tensioned in two directions, such as two axial directions. The resilient member can for example be placed in the bushing 122, between the bushing 122 and the pin 124, between the pin 124 and the groove 54, and / or between the groove 54 and the camshaft 34.

[0186] Figures 10A-10CAn example of a selector 98 is shown. In this example, the selector includes one or more grooves 120 that are fixed relative to the axle 30. In this example, the selection sleeve 122 includes a first section 122A having a first outer diameter. In this example, a second section 122B having a second outer diameter that is smaller than the first outer diameter is omitted. Also in this example, the sleeve 122 can be moved axially by a pin 124 that resides in the groove 54 of the camshaft 34. The sleeve 122 can be moved to a first position (Fig. 9A) and a second position (Fig. 9B). As shown in Fig. 9A, with the sleeve 122 in the first position, the first actuation member 94A resides with its radially inward end on the first section 122A of the outer diameter of the sleeve. In this way, the first actuation member 94A is prevented from entering the groove 120. As shown in Fig. 9B, with the sleeve in the first position, the second actuation member 94B has its cutout 126B aligned with the first section 122A of the outer diameter of the sleeve. In this way, the second actuation member 94A can enter the groove 120. As shown in Fig. 9C, with the sleeve in the second position, the second actuation member 94B resides with its radially inward end on the first section 122A of the outer diameter of the sleeve. In this way, the second actuation member 94B is prevented from entering the groove 120. With the sleeve in the second position, the first actuation member 94A can enter the groove 120, as shown in Fig. 9D. In this example, the first actuation member 94A does not have a cutout 126A. Instead, the width of the first actuation member 94A is chosen such that, with the sleeve in the second position, the first actuation member 94A can enter the groove 120. Once either the first actuation member 94A or the second actuation member 94B enters the groove 120, the third rotatable unit 88 is temporarily stopped, causing the third rotatable unit to rotate relative to the second rotatable unit 84. The third rotatable unit 88 will rotate relative to the second rotatable unit 84 from a first position (Fig. 9E) to a second position (Fig. 9F) or from the second position to the first position. As a result, the actuatable clutch S1, S2 will be engaged or disengaged. After the third rotatable unit 88 moves from the first position to the second position or from the second position to the first position, the respective actuation member 94A, 94B is kicked out of the respective groove 120 by a reset member 128, for example, that co-rotates with the second rotatable unit 84. Figure 10A Figure 10B Figure 10A Figure 10A Figure 10B Figure 6A Figure 6B

[0187] Figure 10C ​​​​​​​A side view of a bushing 122 example is shown. In this example, a pin 124 is connected to the bushing 122 via a tangential arm 124A. The proximal end of the arm 124A is connected to the bushing 122, while the distal end of the arm 124A is connected to the pin 124. In this example, the arm is made of a resilient material, such as a plastic material. The arm 124A can form the resilient member referred to above. This arm allows the pin to have moved in the axial direction of the axle 30, while still preventing the bushing 122 from moving axially by virtue of the first or second actuation member being positioned in the groove 120.

[0188] Figures 11A-11C An example of a selector 98 is shown. In this example, the selector comprises one or more grooves 120 that are fixed relative to the axle 30. In this example, the selection bushing 122 comprises a first section 122A having a first outer diameter. In this example, a second section 122B having a second outer diameter that is smaller than the first outer diameter is omitted. Also in this example, the bushing 122 can be moved axially by a pin 124 that resides in the groove 54 of the camshaft 34. The pin can be connected to the bushing 122, for example, by an arm 124A as shown. The pin extends through a cut-out 123 in the axle 30. In an example, the bushing 122 has a plurality of pins 124 connected to it, such as 2 or 3 pins, for example, evenly distributed around the circumference of the bushing 122. The bushing 122 can be moved to a first position (P1) and a second position (P2). As can be seen, the groove 54 has two legs that extend transverse to the longitudinal axis of the camshaft 34. When the pin 124 is in one of the two legs, the bushing is in a stable state in the first or second position, respectively. The arm 124A can be tensioned in the first and / or second position, such that the bushing 122 is pressed against the axial faces 30A, 30B. Thus, a stable positioning of the bushing 122 can be obtained. Figure 10C Figure 11A Figure 11C Figures 11A-11C Figure 11B An intermediate position is shown, in which the camshaft 34 is rotated such that the pin 124 is in the inclined portion of the groove 54 that connects the two legs. The two actuation members 94A and 94B can be similar to those shown in Figure 9A and Figure 9B or Figure 10A and Figure 10B

[0189] The first actuation member 94A and the second actuation member 94B can be, for example, Figure 9A , Figure 9B , Figure 10A or Figure 10B Figure 11A ​​​​​​As shown, in the case where the bushing 122 is in the first position, the first actuation member 94A lodges with its radially inward end on the first section 122A of the outer diameter of the bushing. In this way, the first actuation member 94A is prevented from entering the groove 120. As shown in Figure 11A As shown, in the case where the bushing is in the first position, the second actuation member 94B can align its cutout 126B with the first section 122A of the larger outer diameter of the bushing. In this way, the second actuation member 94A can be enabled to enter the groove 120. As shown in Figure 11A As shown, the first actuation member 94A can run with its radially inward end on the first section 122A of the outer diameter of the bushing. In this way, the second actuation member 94B is prevented from entering the groove 120. As shown in Figure 11A As shown, the second actuation member 94B can align its cutout 126B with the first section 122A of the larger outer diameter of the bushing. Alternatively, the first actuation member can be free of a cutout, as described with reference to Figure 10A 、 10B Thus, the first actuation member 94A can be enabled to enter the groove 120. Once the first actuation member 94A or the second actuation member 94B enters the groove 120, the third rotatable unit 88 is temporarily stopped, causing the third rotatable unit to rotate relative to the second rotatable unit 84. The third rotatable unit 88 will rotate relative to the second rotatable unit 84 from a first position ( Figure 6A ) to a second position ( Figure 6B ) or from the second position to the first position. Thus, the actuatable clutches S1, S2 will be engaged or disengaged. After the third rotatable unit 88 moves from the first position to the second position or from the second position to the first position, the respective actuation member 94A, 94B is kicked out of the respective groove 120 by a reset member 128, for example co-rotating with the second rotatable unit 84.

[0190] In one example, the bicycle derailleur comprises an electric drive for propelling or assisting in propelling the bicycle. The electric drive can be mounted concentrically around the axle 30. Alternatively, the electric drive can be at least partially mounted inside the axle 30. The electric drive can comprise an electric motor. The electric motor can comprise a stator and a rotor. The electric drive can comprise a planetary gear set. The electric drive can comprise a rotation sensor and / or a position sensor.

[0191] Returning to Figure 1The bicycle derailleur 1000 includes a hub housing 51 for connection to a bicycle wheel, for example via spoke flanges 140. The bicycle derailleur 1000 further includes a drive section 142 for connection to one or more sprockets 3. In this example, the drive section 142 is mounted to the axle 30 via first bearings 144 (here, two first bearings). The hub housing 51 is mounted to the axle 30 via a second bearing 146 and to the drive section 142 via a third bearing 148. The bicycle derailleur 1000 further includes a derailleur system 100. In this example, the derailleur system includes a planetary gear set 100. In this example, the derailleur system 100 is positioned between the second bearing 146 and the third bearing 148. In this example, switching mechanisms S1, S2 and clutch mechanisms C1, C2, C3, C4 are positioned between the second bearing 146 and the third bearing 148.

[0192] The bicycle derailleur 1000 further includes control electronics 150 for controlling actuators, such as electromechanical actuator 32. In this example, viewed from the derailleur system 100, the control electronics 150 is positioned outside the second bearing 146. Figure 1 As can be seen, the hub housing 51 encloses a first cavity between the second bearing 146 and the third bearing 148. The transmission system 100 is located within the first cavity. The control electronics 150 is located outside the first cavity. In this example, the control electronics 150 is mounted away from the non-drive side hub bearing 146. However, the control electronics 150 may also be mounted away from the drive side hub bearing 148.

[0193] exist Figure 1 In this example, viewed from the transmission system 100, the hub housing 51 extends beyond the second bearing 146 and encloses the control electronics 150. The control electronics 150 is mounted, for example, fixedly mounted on the axle 30, or concentrically mounted on the axle. The control electronics includes at least one of a controller, generator, battery, PCB, wireless receiver / transmitter, antenna, LED, charging plug, connector, or microchip. In this example, the control electronics is mounted behind the housing 152. The housing 152 is preferably transmissive to wireless signals. The housing may be made, for example, of a plastic material.

[0194] The receiver of the control electronics 150 can be configured to receive a shift control signal, such as a shift control signal from the shifter 1024. The shift control signal can represent a desired transmission gear (e.g., first gear, second gear, third gear, etc.). The shift control signal can represent a shift up or a shift down. The controller can be configured to shift the control actuator, such as an electromechanical actuator, based on the shift control signal. Alternatively or additionally, the controller can be configured to autonomously change the transmission gear, e.g., based on the current transmission gear, wheel speed, cadence, torque, and / or heart rate. In particular, when the transmission system comprises a generator and is configured to autonomously change the transmission ratio, a self-contained autonomous transmission can be provided. Optionally, the characteristics of the transmission system, such as parameters for when to shift, can be adjusted by a user, e.g., using an interface in (wireless) communication with the control electronics, such as on a mobile communication device, such as a smartphone.

[0195] In Figure 1 In the example of Fig. 1, the hub shell 51 comprises an inner hub shell 51i housing the axle 30 and an outer hub shell 51o configured for connection to the wheel. Here, the control electronics 150 are positioned to be replaceable upon removal of the inner hub shell 51i from the outer hub shell 510.

[0196] Figure 12 An example of a bicycle 1 is shown. The bicycle comprises a frame 1002 and a front fork 1005. The bicycle comprises handlebars 1003. A front wheel 1011 is mounted to the front fork 1005. The frame 1002 comprises a rear fork 1007 having a rear wheel 1013 mounted thereto. A crank bridge 1004 is mounted to the frame 1002. Pedals 1017 are connected to the crank bridge 1004. A front sprocket 1009 is also connected to the crank bridge 1004. The rear wheel is provided with a hub 1022. A rear sprocket 1021 is connected to the hub. In this example, the rear sprocket 1021 is connected to the hub 1022 by a transmission system 100, e.g., as described above. Alternatively or additionally, the crank bridge 1004 can be connected to the front sprocket 1009 by a transmission system 100, e.g., as described above. The front sprocket 1009 drives the rear sprocket 1021 via an endless member, such as a chain or a belt. In this example, the bicycle 1 comprises a shifter 1024 configured to send a shift control signal to a receiver of control electronics 150 of the transmission system 100.

[0197] Embodiments

[0198] The present disclosure will now be further described with respect to the following numbered embodiments. It is to be understood that some or all of the embodiments summarized in the following numbered embodiments summarize aspects of the present disclosure provided in the detailed description and the drawings. Accordingly, the embodiments are also to be read in conjunction with the foregoing paragraphs and the drawings and are not limiting of the present disclosure. The features and preferences as described hereinabove also apply to the following embodiments.

[0199] Embodiment 1 : A bicycle derailleur comprising:

[0200] a wheel bridge, such as a wheel bridge or a countershaft in a crank derailleur, having a central axis;

[0201] at least one sun gear rotatably mounted about the wheel bridge;

[0202] at least one clutch mechanism configured to selectively prevent rotation of the at least one sun gear about the wheel bridge in a first rotational direction in a first mode, and to selectively prevent rotation of the at least one sun gear about the wheel bridge in an opposite second rotational direction in a second mode;

[0203] a camshaft mounted inside the wheel bridge for actuating the at least one clutch mechanism;

[0204] wherein each clutch mechanism comprises a first pawl and a second pawl, the pawls being configured to be actuated by the camshaft such that the first pawl selectively engages with the respective sun gear in the first mode, and the second pawl selectively engages with the respective sun gear in the second mode.

[0205] Embodiment 2: The bicycle derailleur according to embodiment 1, wherein the at least one clutch mechanism comprises a plurality of clutch mechanisms.

[0206] Embodiment 3: The bicycle derailleur according to embodiment 2, wherein in each clutch mechanism the first pawl and the second pawl are configured to each pivot about a respective pivot axis, wherein the radial distance between the pivot axis and the central axis is different for different ones of the plurality of clutch mechanisms.

[0207] Embodiment 4: The bicycle derailleur according to embodiment 1, 2 or 3, wherein the first pawl is tangentially movable to allow tangential movement of the first pawl relative to the camshaft to allow free spinning of the sun gear in the first mode, and wherein the second pawl is tangentially movable to allow tangential movement of the second pawl relative to the camshaft to allow free spinning of the sun gear in the second mode.

[0208] Embodiment 5: The bicycle derailleur according to any one of embodiments 1 to 4, wherein the first pawl and the second pawl are pivotably arranged to selectively engage or disengage with the respective sun gear.

[0209] Example 6: The bicycle derailleur according to Example 5, wherein the first and second pawls are each hingedly supported in the respective first and second pockets of the chainstay, such that the camshaft can selectively pivot the first pawl radially to engage with the sun gear to prevent the sun gear from rotating relative to the chainstay in a first rotational direction, or pivot the second pawl radially to engage with the sun gear to prevent the sun gear from rotating relative to the chainstay in a second rotational direction, opposite the first rotational direction.

[0210] Example 7: The bicycle derailleur according to Example 6, wherein the first pawl is tangentially movable in the first pocket to allow the first pawl to move tangentially and radially inward relative to the camshaft to allow the sun gear to freewheel in the second rotational direction, and wherein the second pawl is tangentially movable in the second pocket to allow the second pawl to move tangentially and radially inward relative to the camshaft to allow the sun gear to freewheel in the first rotational direction.

[0211] Example 8: The bicycle derailleur according to any one of Examples 1-7, wherein the at least one sun gear comprises a plurality of sun gears.

[0212] Example 9: The bicycle derailleur according to Example 8, wherein the chainstay has different outer radii at locations of different ones of the plurality of sun gears.

[0213] Example 10: The bicycle derailleur according to any one of Examples 1-9, wherein the first position of the first and second pawls of at least one of the clutch mechanisms is rotated about the central axis relative to the second position of the first and second pawls of at least one other of the clutch mechanisms.

[0214] Example 11 : A bicycle derailleur, comprising:

[0215] a chainstay, such as a wheel bridge or countershaft in a derailleur, the chainstay having a central axis;

[0216] a plurality of sun gears rotatably mounted about the chainstay;

[0217] a plurality of clutch mechanisms for selectively preventing one or more of the plurality of sun gears from rotating about the chainstay in at least one rotational direction;

[0218] a camshaft mounted inside the chainstay for actuating the plurality of clutch mechanisms;

[0219] wherein each clutch mechanism includes at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with a respective sun gear, the at least one pawl being configured to pivot about a pivot axis;

[0220] wherein the radial distance between the pivot axis and the central axis is different for different ones of the plurality of clutch mechanisms.

[0221] Embodiment 12: The bicycle derailleur according to embodiment 11, wherein the outer radius of the carriage is different at the location of different ones of the plurality of sun gears.

[0222] Embodiment 13: The bicycle derailleur according to embodiment 11 or 12, wherein the first position of the at least one pawl of at least one of the clutch mechanisms is rotated relative to the second position of the at least one pawl of at least another one of the clutch mechanisms about the central axis.

[0223] Embodiment 14: A bicycle derailleur, comprising:

[0224] a carriage, such as a wheel bridge or a countershaft in a derailleur, having a central axis;

[0225] a plurality of sun gears rotatably mounted about the carriage;

[0226] a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears about the carriage in at least one rotational direction;

[0227] a camshaft mounted inside the carriage for actuating the plurality of clutch mechanisms;

[0228] wherein the outer radius of the carriage is different at the location of different ones of the plurality of sun gears.

[0229] Embodiment 15: The bicycle derailleur according to embodiment 14, wherein each clutch mechanism comprises at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with the respective sun gear.

[0230] Embodiment 16: The bicycle derailleur according to embodiment 15, wherein the first position of the at least one pawl of at least one of the clutch mechanisms is rotated relative to the second position of the at least one pawl of at least another one of the clutch mechanisms about the central axis.

[0231] Embodiment 17: A bicycle derailleur, comprising:

[0232] a carriage, such as a wheel bridge or a countershaft in a derailleur, having a central axis;

[0233] a plurality of sun gears rotatably mounted about the carriage;

[0234] a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears about the carriage in at least one rotational direction;

[0235] a camshaft mounted inside the axle for actuating the plurality of clutch mechanisms;

[0236] wherein each clutch mechanism comprises at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with the respective sun gear;

[0237] wherein the first position of the at least one pawl of at least one of the clutch mechanisms is rotated about the central axis relative to the second position of the at least one pawl of at least another of the clutch mechanisms.

[0238] Embodiment 18: The bicycle derailleur according to any one of embodiments 11-17, wherein each clutch mechanism is configured to selectively prevent rotation of the respective sun gear about the axle in a first rotational direction in the first mode, and to selectively prevent rotation of the respective sun gear about the axle in an opposite second rotational direction in the second mode.

[0239] Embodiment 19: The bicycle derailleur according to embodiment 18, wherein for each clutch mechanism, the at least one pawl comprises a first pawl and a second pawl, the pawls configured to be actuated by the camshaft such that the first pawl selectively engages with the respective sun gear in the first mode, and the second pawl selectively engages with the respective sun gear in the second mode.

[0240] Embodiment 20: The bicycle derailleur according to embodiment 19, wherein in each clutch mechanism, the first pawl and the second pawl are configured to each pivot about a respective pivot axis, wherein the radial distance between the pivot axis and the central axis is different for different ones of the plurality of clutch mechanisms.

[0241] Embodiment 21 : The bicycle derailleur according to embodiment 19 or 20, wherein in each clutch mechanism, the first pawl is tangentially movable to allow tangential movement of the first pawl relative to the camshaft to thereby allow free spinning of the sun gear in the first mode, and wherein the second pawl is tangentially movable to allow tangential movement of the second pawl relative to the camshaft to thereby allow free spinning of the sun gear in the second mode.

[0242] Embodiment 22: The bicycle derailleur according to any one of embodiments 19-21, wherein in each clutch mechanism, the first pawl and the second pawl are pivotally arranged to selectively engage or disengage with the respective sun gear.

[0243] Example 23: The bicycle derailleur according to Example 22, wherein in each clutch mechanism, the first and second pawls are each hingedly supported in the respective first and second pockets of the chainstay, such that the camshaft can selectively pivot the first pawl radially to engage with the sun gear to prevent the sun gear from rotating relative to the chainstay in a first rotational direction, or pivot the second pawl radially to engage with the sun gear to prevent the sun gear from rotating relative to the chainstay in a second, opposite rotational direction.

[0244] Example 24: The bicycle derailleur according to Example 23, wherein in each clutch mechanism, the first pawl is tangentially movable in the first pocket to allow the first pawl to move tangentially and radially inward relative to the camshaft to thereby allow the sun gear to freewheel in the second rotational direction, and wherein the second pawl is tangentially movable in the second pocket to allow the second pawl to move tangentially and radially inward relative to the camshaft to thereby allow the sun gear to freewheel in the first rotational direction.

[0245] Example 25: A bicycle derailleur, comprising:

[0246] a chainstay, such as a wheel bridge or countershaft in a derailleur, having a central axis;

[0247] a sun gear rotatably mounted about the chainstay;

[0248] a clutch mechanism for selectively preventing the sun gear from rotating about the chainstay in at least one rotational direction;

[0249] a camshaft having a cam for actuating the clutch mechanism;

[0250] wherein the clutch mechanism includes at least one pawl hingedly supported in a pocket of the chainstay, such that the cam can selectively pivot the at least one pawl radially to engage with the sun gear to prevent the sun gear from rotating relative to the chainstay in a first rotational direction; and

[0251] wherein the at least one pawl is tangentially movable in the pocket to allow the pawl to move tangentially and radially inward relative to the cam to thereby allow the sun gear to freewheel in a second, opposite rotational direction.

[0252] Example 26: The bicycle derailleur according to Example 25, wherein the clutch mechanism further includes a spring having an arm extending around a radially outer surface of the at least one pawl for biasing the at least one pawl radially inward.

[0253] Example 27: A bicycle derailleur, comprising:

[0254] a chainstay, such as a wheel bridge or countershaft in a derailleur, having a central axis;

[0255] a sun gear rotatably mounted about the axle;

[0256] a clutch mechanism for selectively preventing rotation of the sun gear about the axle in at least one rotational direction;

[0257] a cam shaft having a cam for actuating the clutch mechanism;

[0258] wherein the clutch mechanism includes a first pawl and a second pawl, each pawl being hingedly supported in a respective first and second pocket of the axle, such that the cam can selectively pivot the first pawl radially to engage with the sun gear to prevent rotation of the sun gear relative to the axle in a first rotational direction, or pivot the second pawl radially to engage with the sun gear to prevent rotation of the sun gear relative to the axle in a second, opposite rotational direction; and

[0259] wherein the first pawl is tangentially movable in the first pocket to allow tangential and radial inward movement of the first pawl relative to the cam to allow free spinning of the sun gear in the second rotational direction, and wherein the second pawl is tangentially movable in the second pocket to allow tangential and radial inward movement of the second pawl relative to the cam to allow free spinning of the sun gear in the first rotational direction.

[0260] Example 28: The bicycle derailleur according to Example 27, including one or more springs for biasing the first and second pawls radially inward.

[0261] Example 29: The bicycle derailleur according to any one of Examples 1 to 26, wherein the first and second pawls are each hingedly supported in a respective first and second pocket.

[0262] Example 30: The bicycle derailleur according to Example 27, 28 or 29, including one or more springs for biasing the first pawl tangentially into the first pocket and for biasing the second pawl tangentially into the second pocket.

[0263] Example 31 : The bicycle derailleur according to any one of Examples 27-30, including a single spring for biasing the first and second pawls radially inward, biasing the first pawl tangentially into the first pocket and biasing the second pawl tangentially into the second pocket.

[0264] Example 32: The bicycle derailleur according to any one of Examples 27-31, including a spring having a helically wound section, a first arm extending from a first end of the helically wound section and a second arm extending from a second end of the helically wound section, wherein a distal end of the first arm is connected to the first pawl and a distal end of the second arm is connected to the second pawl.

[0265] Example 33: The bicycle derailleur according to Example 32, wherein the first arm and the second arm together wrap more than 360 degrees around the axle such that the first arm pushes the second pawl radially inward and the second arm pushes the first pawl radially inward.

[0266] Example 34: The bicycle derailleur according to any one of Examples 1-33, wherein the first and / or second pawl is L-shaped.

[0267] Example 35: The bicycle derailleur according to any one of Examples 1-34, wherein the first and / or second pawl has a first body portion extending substantially tangentially to an outer surface of the axle; and a second body portion extending substantially radially inward from the first body portion.

[0268] Example 36: The bicycle derailleur according to Example 35, wherein the first body portion has a proximal end proximate the pawl pivot axis and a distal end having an engagement surface for engagement with an engagement surface of the sun gear.

[0269] Example 37: The bicycle derailleur according to Example 35 or 36, wherein the second body portion is connected to a distal end of the pawl.

[0270] Example 38: The bicycle derailleur according to Example 37, wherein the second body portion carries one or more bearing surfaces.

[0271] Example 39: The bicycle derailleur according to any one of Examples 25-38, comprising a plurality of sun gears.

[0272] Example 40: The bicycle derailleur according to any one of Examples 1-10, 19-24, or 27-39, wherein the first pawl and the second pawl are formed together as a single body.

[0273] Example 41: The bicycle derailleur according to any one of Examples 1-40, comprising one or more rolling or sliding bearings forming a contact point between the camshaft and the corresponding pawl.

[0274] Example 42: The bicycle derailleur according to any one of Examples 1-41, comprising one or more bearings, such as rolling and / or sliding bearings, mounted for bearing the camshaft inside the axle.

[0275] Example 43: A bicycle derailleur, comprising:

[0276] an axle, such as a wheel axle or a countershaft in a derailleur;

[0277] at least one sun gear rotatably mounted about the axle;

[0278] at least one clutch mechanism for selectively preventing rotation of the at least one sun gear around the axle in at least one rotational direction;

[0279] a cam shaft mounted inside the axle for actuating the at least one clutch mechanism; and

[0280] one or more bearings mounted for supporting the cam shaft inside the axle.

[0281] Embodiment 44: Bicycle derailleur according to embodiment 43, wherein the bearings are rolling bearings or sliding bearings.

[0282] Embodiment 45: Bicycle derailleur according to any one of embodiments 1 to 44, wherein the axle is configured to be non-rotatably fixed to the bicycle frame.

[0283] Embodiment 46: Bicycle derailleur according to any one of embodiments 1 to 45, wherein the cam shaft comprises a plurality of cams in a longitudinal direction of the cam shaft, each cam for engaging a pawl associated with a consecutive one of the plurality of sun gears, wherein the cams are aligned with each other along a single line parallel to the central axis.

[0284] Embodiment 47: Bicycle derailleur, e.g. according to any one of embodiments 1 to 46, comprising:

[0285] an axle, e.g. a wheel axle or a countershaft in a derailleur, configured to be non-rotatably fixed to the bicycle frame;

[0286] at least one sun gear rotatably mounted around the axle;

[0287] at least one clutch mechanism for selectively preventing rotation of the at least one sun gear around the axle in at least one rotational direction; and

[0288] a cam shaft mounted inside the axle for actuating the at least one clutch mechanism.

[0289] Embodiment 48: Bicycle derailleur according to embodiment 47, further comprising an electromechanical actuator, e.g. an electric motor, on or in the axle and configured for moving, e.g. rotating, the cam shaft.

[0290] Embodiment 49: Bicycle derailleur, e.g. according to any one of embodiments 1 to 48, comprising:

[0291] an axle;

[0292] a clutch mechanism around and / or inside the axle; and

[0293] an electromechanical actuator, e.g. an electric motor, in the axle and configured for actuating the clutch mechanism.

[0294] Example 50: The bicycle derailleur according to example 49, further comprising a camshaft mounted inside the bridge, configured for movement by an electromechanical actuator, the camshaft being configured for actuating the clutch mechanisms.

[0295] Example 51 : The bicycle derailleur according to example 49 or 50, wherein the bridge is configured to be non-rotatably fixed to the bicycle frame, the derailleur further comprising:

[0296] at least one sun gear rotatably mounted around the bridge, wherein the clutch mechanisms are configured for selectively preventing rotation of the at least one sun gear around the bridge in at least one rotational direction.

[0297] Example 52: A bicycle derailleur, e.g. according to any one of examples 1 to 51, comprising:

[0298] a bridge, e.g. a wheel bridge or a countershaft in a derailleur, configured to be non-rotatably fixed to a vehicle frame;

[0299] a plurality of sun gears rotatably mounted around the bridge;

[0300] a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears around the bridge in at least one rotational direction; and

[0301] a camshaft comprising a single notched profile for actuating the plurality of clutch mechanisms.

[0302] Example 53: The bicycle derailleur according to example 52, wherein the camshaft is mounted inside the bridge.

[0303] Example 54: The bicycle derailleur according to example 52 or 53, further comprising an electromechanical actuator, e.g. an electric motor, on or in the bridge, and configured for moving, e.g. rotating, the camshaft.

[0304] Example 55: A bicycle derailleur, comprising:

[0305] a bridge, e.g. a wheel bridge or a countershaft in a derailleur, configured to be non-rotatably fixed to a vehicle frame;

[0306] at least one sun gear rotatably mounted around the bridge;

[0307] at least one clutch mechanism configured for selectively preventing rotation of the at least one sun gear around the bridge in a first rotational direction in a first mode, and for selectively preventing rotation of the at least one sun gear around the bridge in an opposite second rotational direction in a second mode.

[0308] Example 56: The bicycle derailleur according to Example 55, wherein the at least one clutch mechanism is configured to allow the sun gear to freely rotate about the axle in at least one or both rotational directions in the third mode.

[0309] Example 57: The bicycle derailleur according to Example 55 or 56, wherein the at least one clutch mechanism is configured to be actively electronically actuated to select the respective mode of the clutch mechanism.

[0310] Example 58: The bicycle derailleur according to Example 55, 56, or 57, wherein the at least one sun gear comprises at least two or at least three sun gears rotatably mounted about the axle, and the at least one clutch mechanism comprises a respective clutch mechanism associated with each sun gear for selecting at least the first mode and the second mode.

[0311] Example 59: The bicycle derailleur according to Example 58, wherein the at least two or at least three sun gears have different diameters and are connected by at least one stepped planetary gear rotatably mounted within the housing.

[0312] Example 60: The bicycle derailleur according to Example 59, comprising a ring gear meshing with one of the planetary gears of the stepped planetary gear.

[0313] Example 61 : The bicycle derailleur according to any one of Examples 55 to 60, wherein the input of the derailleur is connectable to the ring gear or the carrier of the planetary gear set.

[0314] Example 62: The bicycle derailleur according to Example 61, wherein the input of the derailleur is connected to the ring gear via a one-way clutch or one-way bearing.

[0315] Example 63: The bicycle derailleur according to Example 61 or 62, wherein the input of the derailleur is connected to the carrier via a first actuable clutch mechanism.

[0316] Example 64: The bicycle derailleur according to any one of Examples 55 to 63, wherein the output of the derailleur is connectable to the ring gear or the carrier of the planetary gear set.

[0317] Example 65: The bicycle derailleur according to Example 64, wherein the carrier is connected to the output of the derailleur via a one-way clutch or one-way bearing.

[0318] Example 66: The bicycle derailleur according to Example 64 or 65, wherein the ring gear is connected to the output of the derailleur via a second actuable clutch mechanism.

[0319] Example 67: Bicycle derailleur according to any one of the examples 55-66, wherein or each clutch mechanism comprises a first pawl and a second pawl, the pawls being configured to be actuated by the cam shaft such that the first pawl selectively engages with the respective sun gear in the first mode and the second pawl selectively engages with the respective sun gear in the second mode.

[0320] Example 68: Bicycle derailleur according to any one of the examples 55-67, wherein at least one of the clutch mechanisms comprises a freewheel or a one-way bearing to create the first mode or the second mode.

[0321] Example 69: Bicycle derailleur according to example 67 or example 68 dependent on example 67, wherein the cam shaft is mounted inside the bridge for actuating at least one clutch mechanism.

[0322] Example 70: Bicycle derailleur according to example 69 dependent on example 58, wherein the cam shaft mounted inside the bridge is configured for actuating a respective clutch mechanism of the at least one clutch mechanism.

[0323] Example 71 : Bicycle derailleur according to example 70 dependent on examples 63 and 66, wherein the cam shaft mounted inside the bridge is configured for actuating the first and the second actuable clutch mechanism.

[0324] Example 72: Bicycle derailleur according to any one of the examples 55-71, wherein the at least one clutch mechanism is designed such that it can disengage from the torque bearing sun gear in at least one direction.

[0325] Example 73: Bicycle derailleur according to example 72 dependent on example 67, wherein the pawls are designed such that they disengage under torque load on the sun gear and the cam shaft is configured to allow prevention of disengagement.

[0326] Example 74: Bicycle derailleur according to any one of the examples 55-73, wherein there is a rolling bearing between the cam shaft and the pawls.

[0327] Example 75: Bicycle derailleur according to any one of the examples 55-74, wherein there is at least one rolling bearing between the cam shaft and the bridge.

[0328] Example 76: Bicycle derailleur according to any one of the examples 1 -75, wherein the cam shaft comprises a single notched profile for actuating a plurality of clutch mechanisms.

[0329] Example 77: Bicycle derailleur according to any one of examples 1-76, wherein each clutch mechanism comprises at least one pawl configured to be actuated by the camshaft such that the at least one pawl is selectively engaged or disengaged with the respective sun gear.

[0330] Example 78: Bicycle derailleur according to any one of examples 1-77, wherein the at least one pawl is configured to move in a radial direction relative to the bridge.

[0331] Example 79: Bicycle derailleur according to any one of examples 1-78, wherein each clutch mechanism has a selection bushing associated therewith, and wherein the camshaft comprises one or more grooves for axially moving the selection bushing.

[0332] Example 80: Bicycle derailleur according to any one of examples 1-79, comprising a resilient member, e.g. a compliant mechanism, connecting the camshaft and the electromechanical actuator.

[0333] Example 81 : Bicycle derailleur according to example 80, wherein the resilient member is pre-tensioned in two opposite directions.

[0334] Example 82: Bicycle derailleur according to any one of examples 1-81, comprising an electric drive for propelling or assisting in propelling the bicycle, wherein the electric drive is mounted concentrically inside and / or outside the bridge or on another bridge, e.g. parallel to the bridge.

[0335] Example 83: Bicycle derailleur according to example 82, wherein the electric drive comprises an electric motor, and optionally a planetary gear set.

[0336] Example 84: Bicycle derailleur according to any one of examples 1-83, wherein the camshaft or the electric drive comprises a rotation sensor and / or a position sensor.

[0337] Example 85: Bicycle derailleur according to any one of examples 1-84, further comprising control electronics for controlling the electromechanical actuator, wherein the control electronics are optionally mounted away from the drive side or non-drive side hub bearing.

[0338] Example 86: Bicycle derailleur, e.g. according to any one of examples 1-85, comprising:

[0339] a hub shell for connection to a bicycle wheel;

[0340] a wheel bridge;

[0341] a driver part for connection to one or more sprockets, wherein the driver part is mounted to the wheel bridge via a first bearing, and wherein the hub shell is mounted to the wheel bridge via a second bearing and to the driver part via a third bearing;

[0342] a transmission system providing a plurality of selectable different gear ratios between the driver and the hub shell, the transmission system being positioned between the second bearing and the third bearing;

[0343] an electromechanical actuator for actuating a shift from one gear ratio to another gear ratio;

[0344] control electronics for controlling the electromechanical actuator;

[0345] wherein the control electronics are positioned outside the second bearing as seen from the transmission system.

[0346] Embodiment 87: A bicycle transmission, e.g. according to any one of embodiments 1-85, comprising:

[0347] a hub shell for connection to a bicycle wheel;

[0348] a wheel bridge;

[0349] a driver part for connection to one or more sprockets, wherein the driver part is mounted to the wheel bridge via a first bearing, and wherein the hub shell is mounted to the wheel bridge via a second bearing and to the driver part via a third bearing, wherein the hub shell encloses a first cavity between the second bearing and the third bearing;

[0350] a transmission system providing a plurality of selectable different gear ratios between the driver and the hub shell, the transmission system being positioned in the first cavity;

[0351] an electromechanical actuator for actuating a shift from one gear ratio to another gear ratio;

[0352] control electronics for controlling the electromechanical actuator;

[0353] wherein the control electronics are positioned outside the first cavity.

[0354] Embodiment 88: The bicycle transmission according to embodiment 86 or 87, wherein the hub shell extends outside the second bearing and encloses the control electronics as seen from the transmission system.

[0355] Embodiment 89: The bicycle transmission according to any one of embodiments 85-88, wherein the control electronics are mounted, e.g. fixedly mounted, on the wheel bridge, e.g. concentrically on the wheel bridge.

[0356] Example 90: Bicycle derailleur according to any one of the examples 85 to 89, wherein the control electronics comprise at least one of a generator, a battery, a PCB, a wireless receiver / transmitter, an antenna, an LED, a charging plug, a connector or a microchip.

[0357] Example 91 : Bicycle derailleur according to any one of the examples 85 to 90, wherein the control electronics are mounted inside, behind and / or connected to the plastic housing.

[0358] Example 92: Bicycle derailleur according to any one of the examples 85 to 91, wherein the hub shell comprises an inner hub shell housing the axle and an outer hub shell configured for connection to the wheel, wherein the control electronics are positioned such that the inner hub shell is replaceable after removal from the outer hub shell.

[0359] Example 93: Bicycle derailleur according to any one of the examples 1 to 92, wherein each of the plurality of sun gears is in mesh with a planet gear portion of a stepped planet gear carried by a planet carrier, each planet gear portion having a different radius, wherein optionally at least one planet gear portion is in mesh with the ring gear.

[0360] Example 94: Bicycle derailleur according to example 93, comprising a switching mechanism arranged adjustable between a first state for establishing torque transfer from the derailleur input to the ring gear and from the planet carrier to the derailleur output and a second state for establishing torque transfer from the derailleur input to the planet carrier and from the ring gear to the derailleur output.

[0361] Example 95: Bicycle derailleur according to example 94, wherein the switching mechanism comprises a first actuatable clutch in a transmission path between the derailleur input and the planet carrier, a first freewheel in a transmission path between the derailleur input and the ring gear; and a second actuatable clutch in a transmission path between the ring gear and the derailleur output, a second freewheel in a transmission path between the planet carrier and the derailleur output.

[0362] Example 96: Bicycle derailleur according to example 94 or 95, wherein the camshaft is further configured for actuating the switching mechanism.

[0363] Example 97: Bicycle derailleur according to example 96, wherein the camshaft comprises one or more grooves for actuating the switching mechanism.

[0364] Embodiment 98: The bicycle derailleur according to embodiment 96 or 97, wherein the camshaft is configured for axially moving the selector from the first position to the second position or from the second position to the first position, wherein the first actuatable clutch and / or the second actuatable clutch is configured to switch from the coupled state to the decoupled state or from the decoupled state to the coupled state upon movement of the selector.

[0365] Embodiment 99: A bicycle derailleur hub comprising the bicycle derailleur of any one of embodiments 1 to 98.

[0366] Embodiment 100: A bicycle crank derailleur comprising the bicycle derailleur of any one of embodiments 1 to 98.

[0367] Embodiment 101 : A bicycle comprising the bicycle derailleur hub of embodiment 99 and / or the bicycle crank derailleur of embodiment 100.

[0368] Embodiment 102: A human-powered vehicle comprising the bicycle derailleur of any one of embodiments 1 to 98.

[0369] Embodiment 103: A light electric vehicle comprising the bicycle derailleur of any one of embodiments 1 to 98.

[0370] Embodiment 104: The light electric vehicle according to embodiment 103, having an electric motor with a power of 10 kW or less, preferably 5 kW or less, more preferably 2 kW or less, such as 1 kW or less, or 500 W or less, such as 250 W or less.

[0371] Herein, the application has been described with reference to specific examples of embodiments of the application. It will, however, be evident that various modifications and changes can be made thereunto without departing from the essence of the application. For the purposes of clarity and brevity, each feature is described in relation to only one or a few embodiments, however, it is to be understood that combinations of all or some of the features of the different embodiments can be resorted to as is appropriate.

[0372] In these examples, the use of four different sun gears provides an eight- or nine-speed transmission system. It will be appreciated that fewer or more different gear ratios can also be provided for the transmission system, for example two or three (one sun gear), four or five (two sun gears), six or seven (three sun gears), ten or eleven (five sun gears), twelve or thirteen (six sun gears), fourteen or fifteen (seven sun gears), sixteen or seventeen (eight sun gears), eighteen or nineteen (nine sun gears), or twenty or twenty-one (ten sun gears) different gear ratios. The number of differently radiused planet gear portions of the stepped planet gears can correspond to the number of different sun gears.

[0373] In this example, each sun gear is associated with an actuatable bi-directional clutch mechanism configured to selectively prevent rotation of the at least one sun gear about the axle in a first rotational direction (and optionally to allow rotation of the at least one sun gear about the axle in an opposite second rotational direction) in a first mode, and to selectively prevent rotation of the at least one sun gear about the axle in the opposite second rotational direction (and optionally to allow rotation of the at least one sun gear about the axle in the first rotational direction) in a second mode, to provide two different gear ratios with one sun gear. It will be appreciated that the transmission system can further comprise one or more sun gears having an associated freewheel mechanism configured to selectively prevent rotation of the at least one sun gear about the axle in a first rotational direction (and optionally to allow rotation of the at least one sun gear about the axle in an opposite second rotational direction) in a first mode, and to allow rotation of the at least one sun gear in the first rotational direction (and optionally to allow rotation of the at least one sun gear about the axle in the opposite second rotational direction) in a second mode.

[0374] However, other modifications, variations and alternatives are possible. Accordingly, the specification, drawings, and examples should be regarded as illustrative rather than restrictive.

[0375] In the claims, any reference signs placed between parentheses shall not be construed as limiting the claim. The word 'comprising' does not exclude the presence of elements or steps other than those listed in a claim. Further, the word 'a' or 'an' preceding an element does not exclude the presence of a plurality of such elements. The mere fact that different features are recited in mutually different dependent claims does not indicate that a combination of these features cannot be used to advantage.

Claims

1. A bicycle derailleur comprising: a bridge, such as a wheel bridge or a countershaft in a crank derailleur, having a central axis; at least one sun gear rotatably mounted about the bridge; at least one clutch mechanism configured for selectively preventing rotation of the at least one sun gear about the bridge in a first rotational direction in a first mode, and for selectively preventing rotation of the at least one sun gear about the bridge in an opposite second rotational direction in a second mode; a camshaft mounted inside the bridge for actuating the at least one clutch mechanism; wherein each clutch mechanism comprises a first pawl and a second pawl configured to be actuated by the camshaft such that the first pawl selectively engages with the respective sun gear in the first mode, and the second pawl selectively engages with the respective sun gear in the second mode.

2. Bicycle derailleur according to claim 1, characterized in that The at least one clutch mechanism comprises a plurality of clutch mechanisms.

3. Bicycle derailleur according to claim 2, characterized in that, In each clutch mechanism, the first pawl and the second pawl are configured for pivoting about respective pivot axes, wherein the radial distance between the pivot axes and the central axis is different for different ones of the plurality of clutch mechanisms.

4. Bicycle derailleur according to claim 1, 2 or 3, characterized in that, The at least one sun gear comprises a plurality of sun gears.

5. A bicycle derailleur according to claim 4, characterised in that, The bridge has different outer radii at locations of different ones of the plurality of sun gears.

6. Bicycle derailleur according to any of claims 1-5, characterized in that, A first position of the first pawl and the second pawl of at least one of the clutch mechanisms is rotated about the central axis relative to a second position of the first pawl and the second pawl of at least another one of the clutch mechanisms.

7. A bicycle derailleur comprising: a bridge, such as a wheel bridge or a countershaft in a crank derailleur, having a central axis; a plurality of sun gears rotatably mounted about the bridge; a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears about the bridge in at least one rotational direction; a camshaft mounted inside the bridge for actuating the plurality of clutch mechanisms; wherein each clutch mechanism comprises at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with the respective sun gear, the at least one pawl being configured for pivoting about a pivot axis; wherein the radial distance between the pivot axes and the central axis is different for different ones of the plurality of clutch mechanisms.

8. Bicycle derailleur according to claim 7, characterized in that The bridge has different outer radii at locations of different ones of the plurality of sun gears.

9. Bicycle derailleur according to claim 7 or 8, characterized in that, A first position of the at least one pawl of at least one of the clutch mechanisms is rotated about the central axis relative to a second position of the at least one pawl of at least another one of the clutch mechanisms.

10. A bicycle derailleur comprising: An axle, such as a wheel bridge or countershaft in a derailleur, having a central axis; A plurality of sun gears rotatably mounted about the axle; A plurality of clutch mechanisms for selectively preventing one or more of the plurality of sun gears from rotating in at least one rotational direction about the axle; A camshaft mounted inside the axle for actuating the plurality of clutch mechanisms; Wherein the axle has different outer radii at locations of different ones of the plurality of sun gears.

11. Bicycle derailleur according to claim 10, characterized in that, Each clutch mechanism includes at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with a respective sun gear.

12. Bicycle derailleur according to claim 11, characterized in that, A first position of the at least one pawl of at least one of the clutch mechanisms is rotated about the central axis relative to a second position of the at least one pawl of at least another one of the clutch mechanisms.

13. A bicycle derailleur comprising: An axle, such as a wheel bridge or countershaft in a derailleur, having a central axis; A plurality of sun gears rotatably mounted about the axle; A plurality of clutch mechanisms for selectively preventing one or more of the plurality of sun gears from rotating in at least one rotational direction about the axle; A camshaft mounted inside the axle for actuating the plurality of clutch mechanisms; Wherein each clutch mechanism includes at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages or disengages with a respective sun gear; Wherein a first position of the at least one pawl of at least one of the clutch mechanisms is rotated about the central axis relative to a second position of the at least one pawl of at least another one of the clutch mechanisms.

14. Bicycle derailleur according to any of claims 7 to 13, characterized in that, Each clutch mechanism is configured for selectively preventing a respective sun gear from rotating in a first rotational direction about the axle in a first mode, and for selectively preventing the respective sun gear from rotating in an opposite second rotational direction about the axle in a second mode.

15. Bicycle derailleur according to claim 14, characterized in that, For each clutch mechanism, the at least one pawl includes a first pawl and a second pawl configured to be actuated by the camshaft such that the first pawl selectively engages with the respective sun gear in the first mode, and the second pawl selectively engages with the respective sun gear in the second mode.

16. A bicycle derailleur comprising: An axle, such as a wheel bridge or countershaft in a derailleur, having a central axis; A sun gear rotatably mounted about the axle; A clutch mechanism for selectively preventing the sun gear from rotating in at least one rotational direction about the axle; A camshaft having a cam for actuating the clutch mechanism; wherein the clutch mechanism includes at least one pawl hingedly supported in a pocket of the axle such that the cam can selectively pivot the at least one pawl radially to engage the sun gear to prevent rotation of the sun gear relative to the axle in a first rotational direction; and wherein the at least one pawl is tangentially movable in the pocket to allow the pawl to move tangentially and radially inward relative to the cam to allow the sun gear to freewheel in a second, opposite rotational direction.

17. The bicycle derailleur of claim 16, wherein, The clutch mechanism further includes a spring having an arm extending around a radially outer surface of the at least one pawl for biasing the at least one pawl radially inward.

18. A bicycle derailleur comprising: an axle, such as a wheel axle or a countershaft in a crankset, having a central axis; a sun gear rotatably mounted about the axle; a clutch mechanism for selectively preventing rotation of the sun gear about the axle in at least one rotational direction; a cam shaft having a cam for actuating the clutch mechanism; wherein the clutch mechanism includes first and second pawls each hingedly supported in respective first and second pockets of the axle such that the cam can selectively pivot the first pawl radially to engage the sun gear to prevent rotation of the sun gear relative to the axle in a first rotational direction or pivot the second pawl radially to engage the sun gear to prevent rotation of the sun gear relative to the axle in a second, opposite rotational direction; and wherein the first pawl is tangentially movable in the first pocket to allow the first pawl to move tangentially and radially inward relative to the cam to allow the sun gear to freewheel in the second rotational direction, and wherein the second pawl is tangentially movable in the second pocket to allow the second pawl to move tangentially and radially inward relative to the cam to allow the sun gear to freewheel in the first rotational direction.

19. The bicycle derailleur of claim 18, wherein, one or more springs for biasing the first and second pawls radially inward.

20. Bicycle derailleur according to claim 18 or 19, characterized in that, one or more springs for biasing the first pawl tangentially into the first pocket and for biasing the second pawl tangentially into the second pocket.

21. Bicycle derailleur according to any of claims 18 to 20, characterized in that, a single spring for biasing the first and second pawls radially inward, biasing the first pawl tangentially into the first pocket, and biasing the second pawl tangentially into the second pocket.

22. Bicycle derailleur according to any of claims 18 to 21, characterized in that, a spring having a helically wound section, a first arm extending from a first end of the helically wound section, and a second arm extending from a second end of the helically wound section, wherein a distal end of the first arm is connected to the first pawl and a distal end of the second arm is connected to the second pawl.

23. The bicycle derailleur of claim 22, wherein, The first arm and the second arm together wrap more than 360 degrees around the axle such that the first arm pushes the second pawl radially inwards and the second arm pushes the first pawl radially inwards.

24. Bicycle derailleur according to any of claims 16 to 23, characterized in that, The plurality of sun gears comprises one or more sun gears.

25. Bicycle derailleur according to any of claims 1 to 6, 15 or 18 to 24, characterized in that, The first pawl and the second pawl together are formed by a single body.

26. Bicycle derailleur according to any of claims 1 to 25, characterized in that The one or more bearings comprise one or more rolling bearings or sliding bearings forming a contact point between the camshaft and a respective pawl.

27. Bicycle derailleur according to any of claims 1 to 26, characterized in that The one or more bearings comprise one or more rolling bearings and / or sliding bearings mounted for supporting the camshaft inside the axle.

28. A bicycle derailleur comprising: an axle, for example a crankset axle or a countershaft in a derailleur; at least one sun gear rotatably mounted around the axle; at least one clutch mechanism for selectively preventing rotation of the at least one sun gear in at least one rotational direction around the axle; a camshaft mounted inside the axle for actuating the at least one clutch mechanism; and one or more bearings mounted for supporting the camshaft inside the axle. The bearings are rolling bearings or sliding bearings.

29. The bicycle derailleur of claim 28, wherein, The axle is configured to be non-rotatably fixed to a frame of a bicycle.

30. Bicycle derailleur according to any of claims 1 to 29, characterized in that The camshaft comprises a plurality of cams along a longitudinal direction of the camshaft, each cam for engaging a pawl associated with a consecutive sun gear of the plurality of sun gears, wherein the cams are mutually aligned along a single line parallel to the central axis.

31. Bicycle derailleur according to any of claims 4 to 30, characterized in that, Each sun gear of the plurality of sun gears is in mesh with a planet gear portion of a stepped planet gear carried by a planet carrier, each planet gear portion having a different radius, wherein optionally at least one planet gear portion is in mesh with a ring gear.

32. Bicycle derailleur according to any of claims 4 to 31, characterized in that, The derailleur comprises a switching mechanism arranged adjustable between a first state for establishing torque transfer from a derailleur input to the ring gear and from the planet carrier to a derailleur output and a second state for establishing torque transfer from the derailleur input to the planet carrier and from the ring gear to the derailleur output.

33. The bicycle derailleur of claim 32, wherein, The switching mechanism comprises a first actuatable clutch in a drive path between the derailleur input and the planet carrier, a first freewheel in a drive path between the derailleur input and the ring gear, and a second actuatable clutch in a drive path between the ring gear and the derailleur output, and a second freewheel in a drive path between the planet carrier and the derailleur output.

34. The bicycle derailleur of claim 33, wherein, The camshaft is further configured for actuating the switching mechanism.

35. Bicycle derailleur according to claim 33 or 34, characterized in that The camshaft comprises one or more grooves for actuating the switching mechanism.

36. The bicycle derailleur of claim 35, wherein, ​ 37. Bicycle derailleur according to claim 35 or 36, characterized in that The camshaft is configured for moving the selector shaft axially from a first position to a second position or from the second position to the first position, wherein the first and / or the second actuatable clutch is configured to switch from a coupled state to a decoupled state or from a decoupled state to a coupled state when the selector is moved.

38. Bicycle derailleur according to any one of claims 1 to 37, characterized in that comprises an electric drive for propelling or assisting in propelling the bicycle, wherein the electric drive is mounted concentrically inside and / or outside the axle and / or on another axle, for example parallel to the other axle.

39. Bicycle derailleur hub comprising a bicycle derailleur according to any one of claims 1 to 38.

40. Bicycle crank derailleur comprising a bicycle derailleur according to any one of claims 1 to 38.

41. Bicycle, human-powered vehicle or light electric vehicle comprising a bicycle derailleur hub according to claim 39 and / or a bicycle crank derailleur according to claim 40.

Images