bicycle gearbox

Abstract

The disclosure relates to a bicycle transmission comprising an axle, such as a wheel axle or a countershaft in a crank transmission, configured to be non-rotatably fixed to a frame of the bicycle; at least one sun gear rotatably mounted about the axle; at least one clutch mechanism for selectively preventing rotation of the at least one sun gear in at least one direction of rotation about the axle; and a camshaft mounted inside the axle to actuate the at least one clutch mechanism.

Description

AREA

[0001] The invention relates to a bicycle transmission system, such as for a bicycle. GENERAL STATE OF THE ART

[0002] Bicycle gear systems are well-known in themselves. Many bicycle gear systems are configured to provide a wide variety of different gear ratios.

[0003] A well-known class of bicycle drivetrain systems is based on a chain connecting a front chainring and a rear sprocket, the rear sprocket being one of a variety of rear sprockets, e.g., combined in a cassette, and a derailleur being provided to offer selectable gear ratios. Alternatively or additionally, the front chainring is one of a variety of front chainrings, and a derailleur being provided to offer selectable gear ratios.

[0004] Another well-known class of bicycle drivetrain systems uses enclosed gears. Such enclosed gears can be, for example, internally geared bicycle hub gears. Such enclosed gears can also be internally geared cranksets. These enclosed gears can be used in combination with a derailleur system.

[0005] Current enclosed gearbox systems can have the disadvantage of offering fewer different gear ratios. Current enclosed gearbox systems with more gear ratios often have the disadvantage of being heavy. SUMMARY

[0006] The task is to propose an improved bicycle transmission for a human-powered vehicle or a light electric vehicle. It is understood that the bicycle transmission can be used in various vehicles, such as bicycles, other human-powered vehicles, or light electric vehicles.

[0007] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank-gear unit. The axle is configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a frame of the vehicle, such as the bicycle. The transmission includes at least one sun gear that is rotatably mounted around the axle. The transmission includes at least one clutch mechanism configured to selectively prevent rotation of the at least one sun gear in a first direction around the axle in a first mode, and to selectively prevent rotation of the at least one sun gear in an opposite second direction around the axle in a second mode.The first mode is also referred to in this document as the first disposition. The second mode is also referred to in this document as the second disposition. It is understood that in the first mode, at least one sun wheel can rotate freely around its axis in the second direction of rotation. It is understood that in the second mode, at least one sun wheel can rotate freely around its axis in the first direction of rotation.

[0008] Optionally, at least one coupling mechanism is configured in a third mode to allow the sun gear to rotate freely around the axis in at least one, or preferably both, directions of rotation. This third mode is also referred to in this document as the third disposition.

[0009] Optionally, at least one clutch mechanism is configured to be actively electronically actuated in order to select the respective mode of the clutch mechanism.

[0010] Optionally, the at least one sun gear comprises at least two or at least three sun gears rotatably mounted around the axis. The at least one coupling mechanism can include a separate coupling mechanism assigned to each of the sun gears for selecting at least the first and second modes. Therefore, each sun gear can have an assigned coupling mechanism. Each sun gear can be assigned to one of the coupling mechanisms, and each coupling mechanism can be assigned to one of the sun gears.

[0011] Optionally, the at least two or at least three sun gears have different diameters and are connected by at least one stepped planetary gear, which is rotatably mounted within a carrier. The bicycle transmission may include a ring gear that meshes with one of the planets of the stepped planetary gears.

[0012] Optionally, the gearbox input can be connected to either the ring gear or the carrier of the planetary gear set. The gearbox input can be connected to the ring gear via a freewheel clutch or a freewheel bearing. The gearbox input can be connected to the carrier via a first actuated clutch mechanism. Optionally, the gearbox output can be connected to either the ring gear or the carrier of the planetary gear set. The carrier can be connected to the gearbox output via a freewheel clutch or a freewheel bearing. The ring gear can be connected to the gearbox output via a second actuated clutch mechanism. The first actuated clutch and the second actuated clutch can be part of a shifting mechanism. This allows for selective connection of the input to the carrier and the ring gear to the output, or for connecting the input to the ring gear and the carrier to the output.Therefore, the number of usable gear ratios can be increased. It is also possible to connect the input and output to both the carrier and the ring gear to provide a uniform gear ratio.

[0013] Optionally, the clutch mechanism or mechanisms include a first pawl and a second pawl configured to be actuated by a camshaft, such that the first pawl engages selectively with the respective sun gear in the first mode and the second pawl engages selectively with the respective sun gear in the second mode.

[0014] Optionally, at least one of the coupling mechanisms includes a passive freewheel clutch or a passive freewheel bearing to create a first or second mode.

[0015] Optionally, the camshaft is mounted inside the axis to actuate the at least one clutch mechanism. Optionally, the inside-the-axis camshaft is configured to actuate the respective clutch mechanisms of the at least one clutch mechanism. Optionally, the camshaft can actuate a plurality of clutch mechanisms. Optionally, the inside-the-axis camshaft is configured to actuate the first and second actuated clutch mechanisms. Therefore, the camshaft can actuate the connection of the transmission's input and output to the ring gear and carrier, as described above.

[0016] Optionally, at least one coupling mechanism is designed in such a way that it can separate from a sun gear subjected to torque in at least one direction.

[0017] Optionally, the pawls are designed to separate under torque load at the sun gear, and the camshaft is configured to prevent separation.

[0018] Optionally, a roller bearing is provided between the camshaft and the pawls.

[0019] Optionally, at least one roller bearing is provided between the camshaft and the axle.

[0020] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank drive unit. The axle is configured to be fixed against rotation. The axle can, for example, be non-rotatably fixed to a bicycle frame. The transmission includes at least one sun gear that is rotatably mounted around the axle. The transmission includes at least one clutch mechanism for selectively preventing rotation of the at least one sun gear in at least one direction around the axle. The transmission includes a camshaft mounted inside the axle to actuate the at least one clutch mechanism.Mounting the camshaft inside the axis can provide efficient actuation of at least one clutch mechanism.

[0021] Optionally, the transmission includes an electromechanical actuator, such as an electric motor, configured to move the camshaft, for example, to rotate it. The electromechanical actuator, such as the electric motor, can be positioned on or within the shaft. Placing the electromechanical actuator within the shaft can provide greater design flexibility for the transmission.

[0022] Optionally, the at least one sun gear comprises a plurality of sun gears rotatably mounted about the axis. Optionally, the at least one clutch mechanism comprises a plurality of clutch mechanisms. The plurality of clutch mechanisms can be configured to selectively prevent rotation of one or more of the plurality of sun gears about the axis in at least one direction. Optionally, each clutch mechanism of the plurality of clutch mechanisms is configured to selectively prevent rotation of an associated member of the plurality of sun gears about the axis in at least one direction. Optionally, the camshaft comprises a single-groove profile for actuating the plurality of clutch mechanisms.

[0023] According to one aspect, a bicycle transmission system is provided that includes an axle. The transmission includes a clutch mechanism that surrounds and / or is located within the axle. The transmission includes an electromechanical actuator, such as an electric motor, within the axle and is configured to actuate the clutch mechanism. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crankshaft assembly. The transmission can be a crankshaft assembly.

[0024] Optionally, the transmission includes a camshaft configured to be moved by the electromechanical actuator, with the camshaft being configured to actuate the clutch mechanism. The camshaft may be mounted inside the axle.

[0025] Optionally, the axle is configured to be fixed against rotation. For example, the axle can be fixed non-rotatably to a bicycle frame. Furthermore, the transmission can include at least one sun gear rotatably mounted around the axle, with the coupling mechanism configured to selectively prevent rotation of the at least one sun gear around the axle in at least one direction.

[0026] Optionally, the at least one sun gear comprises a plurality of sun gears rotatably mounted around the axis. Optionally, the transmission comprises a plurality of clutch mechanisms. The plurality of clutch mechanisms can be configured to selectively prevent rotation of one or more of the plurality of sun gears around the axis in at least one direction. Optionally, each clutch mechanism of the plurality of clutch mechanisms is configured to selectively prevent rotation of an associated member of the plurality of sun gears around the axis in at least one direction. Optionally, the camshaft comprises a single-groove profile for actuating the plurality of clutch mechanisms.

[0027] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank gear unit. The axle is configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a plurality of sun gears that are rotatably mounted around the axle. The transmission includes a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears in at least one direction of rotation around the axle. The transmission includes a camshaft that has a single-notch profile for actuating the plurality of clutch mechanisms.The single-notch profile can comprise a cam or a plurality of cam sections extending along an axial direction of the camshaft. The single-notch profile, e.g., the cam or the plurality of cam sections, can extend along a line parallel to a central axis of the camshaft.

[0028] Optionally, the camshaft is mounted inside the axle.

[0029] Optionally, the transmission includes an electromechanical actuator, such as an electric motor, configured to move the camshaft, for example, to rotate it. The electromechanical actuator, such as the electric motor, can be positioned on or inside the shaft.

[0030] The following may apply to the transmission according to any of the above aspects.

[0031] Optionally, each clutch mechanism includes at least one pawl configured to be actuated by the camshaft, such that the at least one pawl is selectively engaged with or disengaged from the respective sun gear. The pawl engaged with the respective sun gear can selectively prevent rotation of the respective sun gear around its axis in at least one direction.

[0032] Optionally, at least one pawl is configured to move radially relative to the axis. The pawl can engage with the respective sun gear when it is in a radially outward position. The pawl can disengage from the respective sun gear when it is in a radially inward position.

[0033] Optionally, each clutch mechanism has an associated selector bushing. The camshaft may include one or more grooves for axially moving the selector bushing(s).

[0034] Optionally, the transmission includes an elastic element, such as a conformal mechanism, that connects the camshaft to the electromechanical actuator. The elastic element can be pre-tensioned in two opposite directions.

[0035] Optionally, the transmission includes an electric drive for powering or assisting the bicycle's propulsion. The electric drive can be mounted concentrically inside and / or outside the axle. For example, the electric drive can be mounted concentrically on the central axle of a hub gear comprising the bicycle's transmission. Alternatively, the electric drive can be mounted on another axle, such as parallel to the main axle. For example, the electric drive can be mounted concentrically on a crank axle of a crank gear comprising the bicycle's transmission. Optionally, the electric drive includes an electric motor. Optionally, the electric drive includes a planetary gear set.

[0036] Optionally, the camshaft or electric drive includes a rotation sensor and / or a position sensor.

[0037] Optionally, the gearbox includes control electronics for controlling the electromechanical actuator. The control electronics can be mounted distal to a drive-side or non-drive-side hub bearing.

[0038] According to one aspect, a bicycle gearbox is provided, for example, according to any of the preceding aspects, which includes a hub shell for connection to a bicycle wheel. The gearbox includes a wheel axle. The gearbox includes a rider part configured for connection to one or more sprockets. The rider part is mounted to the wheel axle via a first bearing. The hub shell is mounted to the wheel axle via a second bearing and to the rider part via a third bearing. The gearbox includes a transmission system that provides a variety of selectable gear ratios between the rider and the hub shell. The transmission system is positioned between the second and third bearings. The gearbox includes an electromechanical actuator for initiating a gear change from one gear ratio to another. The gearbox includes control electronics for controlling the electromechanical actuator.The control electronics are positioned behind the second bearing when viewed from the perspective of the transmission system.

[0039] According to one aspect, a bicycle gearbox is provided, for example, according to any of the foregoing aspects, comprising a hub shell for connection to a wheel of a bicycle. The gearbox includes a wheel axle. The gearbox includes a rider part for connection to one or more sprockets, the rider part being mounted to the wheel axle via a first bearing, and the hub shell being mounted to the wheel axle via a second bearing and to the rider part via a third bearing, the hub shell enclosing a first cavity between the second bearing and the third bearing. The gearbox includes a transmission system providing a variety of selectable different gear ratios between the rider and the hub shell, the transmission system being positioned in the first cavity.The transmission includes an electromechanical actuator for initiating gear changes from one gear ratio to another. The transmission also includes control electronics for controlling the electromechanical actuator. The control electronics are located outside the first cavity.

[0040] Optionally, the hub housing extends beyond the second bearing when viewed from the perspective of the transmission system and encloses the control electronics.

[0041] Optionally, the control electronics can be mounted immobilely on the axle, for example concentrically on the axle.

[0042] Optionally, the control electronics include at least one of a generator, a battery, a circuit board, a wireless receiver / transmitter, an antenna, an LED, a charging plug, a connecting element or a microchip.

[0043] Optionally, the control electronics can be mounted inside, behind, or connected to a plastic housing.

[0044] Optionally, the hub shell comprises an inner housing that encloses the axle and an outer housing configured for connection to, for example, a wheel rim, e.g., via spokes. Optionally, the control electronics are positioned so that they are replaceable after the inner housing has been removed from the outer housing.

[0045] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank drive unit. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes at least one sun gear that is rotatably mounted around the axle.The transmission comprises at least one clutch mechanism configured to selectively prevent rotation of the at least one sun gear in a first direction around the axis in a first mode, and to selectively prevent rotation of the at least one sun gear in an opposite second direction around the axis in a second mode. The transmission comprises a camshaft mounted inside the axis to actuate 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 offers the advantage that the sun gear can be selectively blocked against rotation in two different directions. Therefore, the transmission of torque to the sun gear can be selectively controlled in two different directions.

[0046] Optionally, the transmission includes an additional sun gear and an additional clutch mechanism. The additional clutch mechanism can include a third pawl configured to be actuated by the camshaft, allowing the third pawl to selectively engage with the additional sun gear in a third mode.

[0047] Optionally, the first and second locking pawls are configured to pivot about their respective pivot axis.

[0048] Optionally, the at least one coupling mechanism comprises a multitude of coupling mechanisms. Optionally, in each coupling mechanism, the first and second pawls are configured to pivot about their respective pivot axis. Optionally, the radial distance between the pivot axis and the central axis differs among the various coupling mechanisms. This offers the advantage of allowing a larger radial distance for coupling mechanisms intended to transmit higher torque.

[0049] Optionally, the system can use at least one sun gear or multiple sun gears. Optionally, the axle can have different outer radii at the positions of different sun gears within this multiple system. Optionally, the sun gears can have an inner radius corresponding to the outer radius of the axle. This offers the advantage of allowing larger diameters for axle sections and sun gears intended to transmit higher torque.

[0050] Optionally, a first position of the first and second pawls of at least one of the clutch mechanisms is rotated about the central axis relative to a second position of the first and second pawls of at least one other clutch mechanism. Therefore, the clutch mechanism can be actuated by a camshaft that includes a single-notch profile for actuating the plurality of clutch mechanisms. The single-notch profile can include a single cam or a plurality of cams extending along an axial direction of the camshaft. The single-notch profile, e.g., the cam or the plurality of cams, can extend along a line parallel to a central axis of the camshaft.

[0051] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank-gear unit. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The axle can be used to transmit torque from the sun gears to the frame. The transmission includes a plurality of sun gears rotatably mounted around the axle. The transmission includes a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears in at least one direction around the axle.The transmission includes a camshaft mounted within the axis to actuate the plurality of clutch mechanisms. Each clutch mechanism includes at least one pawl configured to be actuated by the camshaft such that the at least one pawl selectively engages with or disengages from the respective sun gear, and is configured to pivot a pivot axis. The radial distance between the pivot axis and the central axis varies among the different clutch mechanisms of the plurality of clutch mechanisms.

[0052] Optionally, the axis has a different outer radius at the positions of different sun gears of the multitude of sun gears.

[0053] Optionally, a first position of at least one pawl of at least one of the coupling mechanisms is rotated around the central axis relative to a second position of at least one pawl of at least one other of the coupling mechanisms.

[0054] 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. Each clutch mechanism can be configured to selectively prevent rotation of the at least one sun gear in the first direction of rotation about the axis in the first mode, and to selectively prevent rotation of the at least one sun gear in the opposite second direction of rotation about the axis in the second mode.

[0055] Optionally, the transmission includes an additional sun gear and an additional clutch mechanism. The additional clutch mechanism can include a third pawl configured to be actuated by the camshaft, allowing the third pawl to selectively engage with the additional sun gear in a third mode.

[0056] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crankshaft assembly. The transmission can be a crankshaft assembly. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a plurality of sun gears rotatably mounted around the axle. The transmission includes a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears in at least one direction around the axle. The transmission includes a camshaft mounted inside the axle to actuate the plurality of clutch mechanisms.The axis has a different outer radius at the positions of different sun wheels among the multitude of sun wheels.

[0057] Optionally, each clutch mechanism includes at least one pawl configured to be actuated by the camshaft, such that the at least one pawl is selectively engaged with or disengaged from the respective sun gear.

[0058] Optionally, a first position of at least one pawl of at least one of the coupling mechanisms is rotated around the central axis relative to a second position of at least one pawl of at least one other of the coupling mechanisms.

[0059] Optionally, the transmission includes an additional sun gear and an additional clutch mechanism. The additional clutch mechanism can include a third pawl configured to be actuated by the camshaft, allowing the third pawl to selectively engage with the additional sun gear in a third mode.

[0060] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crankshaft assembly. The transmission can be a crankshaft assembly. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a plurality of sun gears rotatably mounted around the axle. The transmission includes a plurality of clutch mechanisms for selectively preventing rotation of one or more of the plurality of sun gears in at least one direction around the axle. The transmission includes a camshaft mounted inside the axle to actuate 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 with or disengages from the 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 one other of the clutch mechanisms. Therefore, the clutch mechanism can be actuated by the camshaft, which may include a single-notch profile for actuating the plurality of clutch mechanisms. The single-notch profile may comprise a cam or a plurality of cams extending along an axial direction of the camshaft. The single-notch profile, e.g., the cam or the plurality of cams, may extend along a line parallel to a central axis of the camshaft.

[0061] Optionally, each coupling mechanism is configured to selectively prevent rotation of the respective sun gear in a first direction around the axis in a first mode, and to selectively prevent rotation of the respective sun gear in an opposite second direction around the axis in a second mode.

[0062] Optionally, 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.

[0063] Optionally, the transmission includes an additional sun gear and an additional clutch mechanism. The additional clutch mechanism can include a third pawl configured to be actuated by the camshaft, allowing the third pawl to selectively engage with the additional sun gear in a third mode.

[0064] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank gear unit. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a sun gear that is rotatably mounted around the axle. The transmission includes a clutch mechanism for selectively preventing rotation of the sun gears around the axle in at least one direction. The transmission includes a camshaft that has a cam for actuating the clutch mechanism.The coupling mechanism comprises at least one pawl, which is pivotally supported in a pocket of the shaft, such that the cam can selectively pivot the at least one pawl radially into engagement with the sun gear to block rotation of the sun gear relative to the shaft in a first direction of rotation. The at least one pawl is tangentially movable in the pocket to allow it to move tangentially and radially inward relative to the cam, thus enabling free rotation of the sun gear in a second, opposite direction. For example, the at least one pawl can be pivoted radially outward so that it engages with the sun gear to block rotation of the sun gear relative to the shaft in the first direction of rotation.The at least one pawl can be pivoted radially inwards so that it is disengaged from the sun gear, allowing the sun gear to rotate relative to the axis in the first direction. If the at least one pawl is pivoted, for example, radially outwards, into engagement with the sun gear to block rotation relative to the axis in the first direction, a rotation of the sun gear in the second direction can move the at least one pawl tangentially in the second direction. This allows the pawl to pivot, for example, radially inwards out of engagement with the sun gear, enabling the sun gear to rotate freely in the second direction.

[0065] Optionally, the transmission, e.g. the clutch mechanism, includes a spring for pre-tensioning at least one pawl radially inwards.

[0066] Optionally, the transmission, e.g. the clutch mechanism, includes a spring for pre-tensioning the at least one pawl tangentially into the pocket, e.g. in the direction of a radial end wall of the pocket, such as against it.

[0067] Optionally, the transmission, e.g. the clutch mechanism, includes a spring having an arm extending around a radial outer surface of the at least one pawl to preload the at least one pawl radially inwards.

[0068] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank gear unit. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a sun gear that is rotatably mounted around the axle. The transmission includes a clutch mechanism for selectively preventing rotation of the sun gears around the axle in at least one direction. The transmission includes a camshaft that has a cam for actuating the clutch mechanism.The coupling mechanism comprises a first pawl and a second pawl, each pivotally supported in a respective first and second pocket of the shaft, so that the cam can selectively pivot the first pawl radially into engagement with the sun gear to block rotation of the sun gear relative to the shaft in a first direction of rotation, or pivot the second pawl radially into engagement with the sun gear to block rotation of the sun gear relative to the shaft in a second, opposite direction of rotation.The first pawl is movable tangentially in the first pocket to allow the first pawl to move tangentially and radially inward relative to the cam to allow free rotation of the sun gear in the second direction of rotation, and wherein the second pawl is movable tangentially in the second pocket to allow the second pawl to move tangentially and radially inward relative to the cam to allow free rotation of the sun gear in the first direction of rotation.

[0069] Thus, in a first mode, the first pawl can be pivoted radially outwards, for example, so that it engages with the sun gear to block rotation of the sun gear relative to the axis in the first direction. The first pawl can also be pivoted radially inwards, for example, so that it is disengaged from the sun gear to allow rotation of the sun gear relative to the axis in the first direction. In a second mode, the second pawl can be pivoted radially outwards, for example, so that it engages with the sun gear to block rotation of the sun gear relative to the axis in the second direction. Alternatively, the second pawl can be pivoted radially inwards, for example, so that it is disengaged from the sun gear to allow rotation of the sun gear relative to the axis in the second direction.In the first mode, when the first pawl is pivoted, e.g., radially outward, into engagement with the sun gear to block rotation of the sun gear relative to the axis in the first direction of rotation, a rotation of the sun gear in the second direction of rotation can move the first pawl tangentially in the second direction of rotation. This allows the first pawl to pivot, e.g., radially inward, out of engagement with the sun gear to allow free rotation of the sun gear in the second direction of rotation. In the second mode, when the second pawl is pivoted, e.g., radially outward, into engagement with the sun gear to block rotation of the sun gear relative to the axis in the second direction of rotation, a rotation of the sun gear in the first direction of rotation can move the second pawl tangentially in the first direction of rotation. This allows the second pawl to pivot, e.g.,to pivot radially inwards out of engagement with the sun gear to allow the sun gear to rotate freely in the first direction. Thus, in the first mode, the gearbox allows the sun gear to be locked in the first direction while allowing it to rotate freely in the second direction, and in the second mode, it locks the sun gear in the second direction while allowing it to rotate freely in the first direction.

[0070] Optionally, the first and / or second pawl are L-shaped. The first and / or second pawl may have a first body section extending substantially tangentially to an outer surface of the shaft, and a second body section extending substantially radially inward from the first body section. The first body section may have a proximal end after a pivot axis of the pawl and a distal end having a mating surface for engaging a mating surface of the sun gear. The second body section may be connected to the distal end of the pawl. The second body section may carry one or more support surfaces, as described above. The camshaft can pivot the pawl radially outward by positioning the camshaft lobe under the support surface(s).A tangential movement of the pawl can cause the support surface(s) to move away from the cam, thus enabling the pawl to pivot radially inwards.

[0071] Optionally, the gearbox includes one or more springs for pre-tensioning the first and second pawls radially inwards.

[0072] Optionally, the gearbox includes one or more springs for pre-tensioning the first pawl tangentially into the first pocket and for pre-tensioning the second pawl tangentially into the second pocket.

[0073] Optionally, the gearbox includes a single spring for pre-tensioning the first and second pawls radially inwards, for pre-tensioning the first pawl tangentially into the first pocket, and for pre-tensioning the second pawl tangentially into the second pocket.

[0074] Optionally, the mechanism includes 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, with a distal end of the first arm being connected to the first pawl and a distal end of the second arm being connected to the second pawl.

[0075] Optionally, the first and second arms can wrap around the axis together by more than 360 degrees, so that the first arm pushes the second pawl radially inwards and the second arm pushes the first pawl radially inwards.

[0076] The gearbox optionally includes a variety of sun gears. The following may apply to each of the above aspects.

[0077] Optionally, the first and second pawls can be separate bodies. The first and second pawls can be connected, for example, so that they move synchronously. Optionally, the first and second pawls can be formed together by a single body. Therefore, the first and second pawls together can form a monolithic part.

[0078] Optionally, the mechanism includes one or more bearings, such as roller or plain bearings, that form a contact point between the camshaft and the respective pawls. Optionally, the pawl includes one or more bearings for engaging a cam lobe on the camshaft. Optionally, each pawl includes two bearings, with each bearing engaging a different cam lobe area. The bearings reduce friction between the camshaft and the respective pawls. This can improve the ease of pawl actuation. It can, for example, reduce the torque required to rotate the camshaft.

[0079] Optionally, the gearbox includes one or more bearings, such as roller bearings and / or plain bearings, which are mounted inside the axle to support the camshaft.

[0080] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank gear unit. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a sun gear that is rotatably mounted around the axle. The transmission includes a clutch mechanism for selectively preventing rotation of the sun gear around the axle in at least one direction. The transmission includes a camshaft that has a cam for actuating the clutch mechanism.The coupling mechanism comprises at least one pawl, which is pivotally supported in a pocket of the shaft, such that the cam can selectively pivot the at least one pawl radially into engagement with the sun gear to block rotation of the sun gear relative to the shaft in a first direction of rotation. The at least one pawl is tangentially movable within the pocket to allow it to move tangentially and radially inward relative to the cam, thus enabling free rotation of the sun gear in a second, opposite direction. Therefore, when the pawl is pivoted out of engagement with the sun gear, the sun gear can rotate freely in at least the first direction of rotation. When the pawl is pivoted into engagement with the sun gear, rotation of the sun gear in the first direction of rotation is prevented, but free rotation of the sun gear in the second direction of rotation is possible.

[0081] Optionally, the gearbox includes a spring having an arm extending around a radial outer surface of the at least one pawl to preload the at least one pawl radially inwards.

[0082] Optionally, the gearbox includes a spring for pre-tensioning at least one pawl tangentially against a tangential end wall of the pocket.

[0083] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crank mechanism. The transmission can be a crank gear unit. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes a sun gear that is rotatably mounted around the axle. The transmission includes a clutch mechanism for selectively preventing rotation of the sun gear around the axle in at least one direction. The transmission includes a camshaft that has a cam for actuating the clutch mechanism.The coupling mechanism comprises a first pawl and a second pawl, each pivotally supported in a respective first and second pocket of the shaft, so that the cam can selectively pivot the first pawl radially into engagement with the sun gear to block rotation of the sun gear relative to the shaft in a first direction of rotation, or pivot the second pawl radially into engagement with the sun gear to block rotation of the sun gear relative to the shaft in a second, opposite direction of rotation.The first pawl is movable tangentially in the first pocket to allow the first pawl to move tangentially and radially inward relative to the cam to allow free rotation of the sun gear in the second direction of rotation, and wherein the second pawl is movable tangentially in the second pocket to allow the second pawl to move tangentially and radially inward relative to the cam to allow free rotation of the sun gear in the first direction of rotation.Thus, in a first mode, the transmission allows selective prevention of rotation of the at least one sun gear in the first direction of rotation around the axis, while allowing freewheeling in the second direction of rotation; in a second mode, selective prevention of rotation of the at least one sun gear in the opposite second direction of rotation around the axis, while allowing freewheeling in the first direction of rotation.

[0084] Optionally, a tangential movement of the first or second pawl causes the pawl to move beyond the cam, thus allowing a radial pivoting of the pawl inwards beyond the cam.

[0085] Optionally, the gearbox includes one or more springs for pre-tensioning the first and second pawls radially inwards.

[0086] Optionally, the gearbox includes one or more springs for pre-tensioning the first pawl tangentially into the first pocket and for pre-tensioning the second pawl tangentially into the second pocket.

[0087] Optionally, the gearbox includes a single spring for pre-tensioning the first and second pawls radially inwards, for pre-tensioning the first pawl tangentially into the first pocket, and for pre-tensioning the second pawl tangentially into the second pocket.

[0088] Optionally, the mechanism includes 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, with a distal end of the first arm being connected to the first pawl and a distal end of the second arm being connected to the second pawl.

[0089] Optionally, the first and second arms can wrap around the axis together by more than 360 degrees, so that the first arm pushes the second pawl radially inwards and the second arm pushes the first pawl radially inwards.

[0090] Optionally, the gearbox includes a variety of sun gears, each with an assigned function.

[0091] According to one aspect, a bicycle transmission system is provided that includes an axle. The axle can be, for example, a wheel axle. The transmission can be an internally geared hub. The axle can be, for example, a shaft, such as a countershaft, in a crankshaft assembly. The transmission can be a crankshaft assembly. The axle has a central axis extending longitudinally from the axle. The axle can be configured to be fixed against rotation. The axle can be, for example, non-rotatably fixed to a bicycle frame. The transmission includes at least one sun gear rotatably mounted around the axle. The transmission includes at least one clutch mechanism for selectively preventing rotation of the at least one sun gear around the axle in at least one direction. The transmission includes a camshaft mounted inside the axle to actuate the at least one clutch mechanism.The gearbox includes one or more bearings that are mounted inside the axle to support the camshaft.

[0092] The bearings can be either rolling bearings or plain bearings.

[0093] The following may apply to any one of the above aspects.

[0094] Optionally, the camshaft comprises a plurality of cams along a longitudinal direction of the camshaft, each for engaging the pawl(s) assigned to a subsequent sun gear of the plurality of sun gears, the cams being aligned together along a single line extending parallel to the central axis.

[0095] Optionally, the multitude of sun gears is toothed with a stepped planetary gear supported by a planet carrier. Optionally, each sun gear of the multitude of sun gears is toothed with a planet gear segment of a stepped planetary gear supported by a planet carrier. Optionally, each planet gear has a different radius. Optionally, at least one planet gear segment is toothed with a ring gear.

[0096] Optionally, the transmission includes a shifting mechanism designed to be adjustable between a first state for producing torque transmission from a transmission input to the ring gear and from the planet carrier to a transmission output, and a second state for producing torque transmission from the transmission input to the planet carrier and from the ring gear to the transmission output.

[0097] Optionally, the shifting mechanism includes a first actuated clutch in a transmission path between the transmission input and the planet carrier and a first freewheel in a transmission path between the transmission input and the ring gear; and a second actuated clutch in a transmission path between the ring gear and the transmission output and a second freewheel in a transmission path between the planet carrier and the transmission output.

[0098] Optionally, the camshaft is further configured to actuate the shifting mechanism. Optionally, the camshaft includes one or more grooves for actuating the shifting mechanism. Optionally, the camshaft is configured to axially move a selection unit from a first position to a second position or from the second position to the first position, wherein the first actuated clutch and / or the second actuated clutch are configured to shift from a engaged state to a disengaged state or from a disengaged state to a engaged state when the selection unit is moved.

[0099] Optionally, the gearbox includes a drive mechanism for selectively moving one or more of the selection units from its first position to its second position or from its second position to its first position.

[0100] Optionally, the drive mechanism is configured to drive intermediate bodies, each of which is individually elastically connected to the selection units.

[0101] Optionally, the camshaft grooves are configured to drive a plurality of journals in the longitudinal direction of the camshaft, with each journal being assigned to one of the selection units or one of the intermediate bodies.

[0102] Optionally, the selection unit is designed to be selectively in a gripping or non-gripping mode, wherein the selection unit has a first section of a first outer diameter and a second section of a second outer diameter, the first outer diameter being larger than the second outer diameter, and wherein the selection unit is axially movable between the first position and the second position; wherein, when the selection unit is in the first position, the selection unit is in the gripping mode designed to enable gripping of at least one actuating element of the clutch or brake system; and wherein, when the selection unit is in the second position, the selection unit is in the non-gripping mode designed not to engage the at least one actuating element.

[0103] According to one aspect, a bicycle gearbox is provided which includes a bicycle gearbox according to any of the above aspects.

[0104] According to one aspect, a bicycle crank gear is provided, which includes a bicycle gear according to any of the above aspects.

[0105] According to one aspect, a bicycle is provided that includes a bicycle gear hub and / or a bicycle crank gear.

[0106] It is understood that any of the aspects, features and options described in this document can be combined. BRIEF DESCRIPTION OF THE DRAWINGS

[0107] Embodiments of the present invention will now be described in detail with reference to the accompanying drawings, in which the following applies: Fig. Figure 1 shows an example of a gearbox; Fig. 2 a schematic example of a gearbox; the Fig. 3A-3C show an example of an actuator; the Fig. 4A-4I shows an example of a gear-shifting sequence; Fig. 5A shows an example of a freewheel clutch; Fig. Figure 5B shows an example of an actuated bidirectional coupling mechanism; the Fig. 6A and Fig. Figure 6B shows examples of an actuated clutch of a shifting mechanism; the Fig. 7A and Fig. Figure 7B shows an example of an actuator; Fig. 8A shows an example of a spring; Fig. 8B shows an example of a coupling; the Fig. 9A and Fig. 9B shows an example of a selection unit; the Fig. 10A and Fig. 10B shows an example of a selection unit; Fig. 10C shows an example of a socket; the Fig. 11A, Fig. 11B and Fig.11C shows an example of a selection unit; Fig. 12 shows an example of a bicycle; and Fig. 13 a schematic example of a gearbox. DETAILED DESCRIPTION

[0108] Fig. 1, Fig. 2 and Fig. Figure 13 shows schematic examples of a bicycle gearbox 1000 for a human-powered vehicle or light electric vehicle, such as a bicycle. The examples from Fig. 1 and Fig. 2. The gearbox 1000 is embodied as a hub gearbox, although it is understood that the gearbox can also be embodied as a crank gearbox, as in Fig. Figure 13 shows the gearbox 1000, which includes a gearbox input I and a gearbox output O.

[0109] With reference to the Fig. 1 and Fig.2 Here, the gearbox input I is connected to a rear sprocket 3 for engaging with a chain or belt of a chain or belt drive 300. The sprocket 3 can be part of a cassette of sprockets, such as one containing two or three sprockets. In a specific example, the cassette of sprockets contains at most two or at most three sprockets. In the embodiment of a crank gearbox, the gearbox input I can be connected to a crank of the bicycle. Here, the gearbox output O is connected to a hub housing 51, which in turn can be connected to a driven wheel of the bicycle. In the embodiment of a crank gearbox, the gearbox output O can be connected to a front chainring of the chain or belt drive 300.

[0110] The transmission 1000 comprises a transmission system 100, specifically a planetary gear set 100, designed to provide speed reduction and / or speed increase between input I and output O. The planetary gear set 100 includes a ring gear 128 and a planet carrier 126, which carries one or more planet gears 127. In this example, the planet carrier 126 carries one or more stepped planet gears 127, each having several planet gear sections 127i with different planet radii. In this example, the stepped planet gear has four planet gear sections 127a, 127b, 127c, and 127d. The ring gear 128 is meshed with one of the different planet radii 127i. Here, the ring gear 128 is meshed with the third planet gear section 127c. The planetary gear set 100 also includes a plurality of different sun gears 129i. The multitude of sun gears is each interlocked with the multitude of different planet radii 127i.Here, the array of sun gears comprises four sun gears 129a, 129b, 129c, and 129d. It should be noted that in this example, the sun gears 129i are positioned with continuously increasing diameters from one end of the shaft 30 to the other. This can be advantageous in combination with a continuously increasing diameter of the shaft 30 corresponding to the increasing diameter of the sun gear, as described below. This also applies to the planet gear components 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 design. Likewise, positioning the planet gear components 127d with the largest diameter between two planet gear components with a smaller diameter can provide a compact design.

[0111] The 129i sun wheels are rotatably arranged around a stationary axle 30. The stationary axle 30 can be mounted on a bicycle frame to support torque. Thus, the axle can be rotatably fixed to the frame.

[0112] The transmission 1000 comprises a shifting mechanism. The shifting mechanism includes a first actuated clutch mechanism S1 and a second actuated clutch mechanism S2. The first actuated clutch mechanism S1 is arranged in a transmission path between the transmission input I and the planet carrier 126. The second actuated clutch mechanism S2 is arranged in a transmission path between the ring gear 128 and the transmission output O. The transmission 1000 also includes a first freewheel 11 in a transmission path between the transmission input I and the ring gear 128. The first freewheel 11 is therefore parallel to the first actuated clutch mechanism S1. The transmission 1000 also includes a second freewheel 12 in a transmission path between the planet carrier 126 and the transmission output O. The second freewheel 12 is therefore parallel to the second actuated clutch mechanism S2.

[0113] The first shifting mechanism is configured to selectively operate in either a first or a second state. In the first state, both the first and second actuated clutch mechanisms S1 and S2 are disengaged. Accordingly, 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. 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 dimensions of the interacting rotating elements of the planetary gear set 100.

[0114] In the second state of the shifting mechanism, both the first and second actuated clutch mechanisms S1 and S2 are engaged. Accordingly, torque can be transmitted in the second state from the transmission input I via the first actuated clutch mechanism S1 to the planet carrier 128 and from the ring gear 126 via the second actuated clutch mechanism S2 to the transmission output O. The first freewheel 11 and the second freewheel 12 are disengaged in the second state. In the second state, the planetary gear set 100 provides a speed increase from the planet carrier 128 to the ring gear 126 according to the relative dimensions of the interacting rotating elements of the planetary gear set 100.

[0115] Here, the gearbox 1000 also includes a third freewheel 13, which is arranged in series with the first actuated clutch S1, and a fourth freewheel 14, which is arranged in series with the second actuated clutch S2. The third and fourth freewheels 13 and 14 prevent the gearbox 1000 from locking when the bicycle is to be rolled backwards.

[0116] The shifting mechanism allows a reversal of the transmission path through the planetary gear set 100, e.g., from the ring gear 128 to the carrier 126 or vice versa, in order to effectively increase the range of gear ratios of the transmission 1000 as a whole. In the first state of the shifting mechanism, the transmission 1000 operates according to a creep gear ratio, whereby the rotational speed is reduced from input I to output O. In the second state of the shifting mechanism, the transmission 1000 operates according to a high-speed gear ratio, whereby the rotational speed is increased from input I to output O.

[0117] The shifting mechanism can also be designed to selectively operate in a third state. In this third state, the first actuated clutch mechanism S1 can be in its engaged state while the second actuated clutch mechanism S2 is in its disengaged state, or vice versa. In this third state, the transmission input I and the transmission output O are coupled to the same rotating element of the planetary gear set 100, e.g., both to the planet carrier 126 or both to the ring gear 128. In this third state, the transmission can be operated according to a uniform gear ratio, e.g., a gear ratio of 1:1.

[0118] The transmission 1000 further comprises a clutch mechanism. The clutch mechanism is designed for selectively engaging one of the plurality of sun gears 129i with the stationary shaft 30. For this purpose, the clutch mechanism comprises a plurality of actuated bidirectional clutch mechanisms Ci. In this example, the plurality of actuated bidirectional clutch mechanisms Ci comprises four actuated bidirectional clutch mechanisms C1, C2, C3, and C4. Each actuated bidirectional clutch mechanism Ci is assigned to a respective sun gear 129i in order to engage the assigned sun gear 129i with the stationary shaft 30 in one of two opposing directions of rotation. Each actuated bidirectional clutch mechanism Ci is designed to be selective in either a first arrangement or a second arrangement.In the first arrangement, the actuated bidirectional clutch mechanism Ci prevents the respective sun gear 129i from rotating in the first direction around the stationary axis 30. In this document, preventing the rotation of the respective sun gear 129i in the first direction around the stationary axis 30 is also referred to as braking the respective sun gear 129i in the first direction of rotation. In the second arrangement, the actuated bidirectional clutch mechanism C2.i prevents the rotation of the respective sun gear 129i in the second direction around the stationary axis 30. In this document, preventing the rotation of the respective sun gear 129i in the second direction around the stationary axis 30 is also referred to as braking the respective sun gear 129i in the second direction of rotation. The direction in which the sun gear 129i is to be braked depends on the state of the shifting mechanism.For example, when the switching mechanism is in a first state, a selective actuating bidirectional clutch mechanism can prevent a rotation of a respective sun gear 129a in the second direction of rotation, whereas when the switching mechanism is in the second state, a selective actuating bidirectional clutch mechanism Ci can prevent a rotation of a respective sun gear 129a in the first direction of rotation.

[0119] When the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30 while the shifting mechanism is in the first state, the ring gear 128 is also driven in the first direction of rotation, and a torque is induced on the sun gears 129i in the second, reverse direction of rotation via the stepped planetary gear 127. By selectively braking one of the sun gears 129i in the second direction of rotation with a corresponding clutch mechanism Ci, torque can be transmitted from the ring gear 128 to the planet carrier 126 according to a creep transmission ratio. If the transmission input I is driven in the first direction of rotation about the stationary axis 30 while the shifting mechanism is in the second state, the planet carrier 126 is also driven in the first direction of rotation, and a torque is induced on the sun gears 129i in the first direction of rotation via the stepped planetary gear 127.By selectively braking one of the sun gears 129i in the first direction of rotation with a corresponding coupling mechanism Ci, torque can be transferred from the planet carrier 128 to the ring gear 126 according to a high-speed gear ratio.

[0120] In both the first and second arrangements, the actuated bidirectional clutch mechanisms Ci can be configured to prevent rotation of the sun gear 129 in one direction while allowing rotation of the sun gear in the opposite direction, e.g., by means of a freewheel. Thus, in the first arrangement, the actuated bidirectional clutch mechanism Ci can be configured to allow freewheeling of the sun gear 129i in the second direction of rotation while preventing rotation of this sun gear 129i in the first direction. Furthermore, in the second arrangement, the actuated bidirectional clutch mechanism Ci can be configured to allow freewheeling of the sun gear 129i in the first direction of rotation while preventing rotation of this sun gear 129i in the second direction.

[0121] One or more of the actuated bidirectional coupling mechanisms Ci can also be selectively configured in a third arrangement. In the third arrangement, the actuated bidirectional coupling mechanism Ci can allow free rotation of the respective sun gear 129i in both directions around the stationary axis 30. For example, while one of the actuated bidirectional coupling mechanisms Ci is in the first or second arrangement, others of the actuated bidirectional coupling mechanisms can be in the third arrangement.

[0122] One or more, e.g., all, of the actuable bidirectional clutch mechanisms Ci can be configured to be adjustable to the third arrangement when the shifting mechanism is in the third state, to allow the ring gear 128 and the planet carrier 126 to rotate together about the stationary axis 30. In this way, the transmission 1000 can provide a uniform gear ratio between the input I and the output O. When the shifting mechanism is in the third state, one or more of the actuable bidirectional clutch mechanisms Ci can also be set to be in the second arrangement, to allow the ring gear 128 and the planet carrier 126 to rotate together in the first direction about the stationary axis 30.

[0123] It is possible that one (or more) of the actuated bidirectional clutch mechanisms Ci is an actuated bidirectional clutch mechanism configured to be in the second arrangement by default and configured to be actively actuated into the first arrangement. The pre-tensioned actuated bidirectional clutch mechanism may be configured not to have a third arrangement. The pre-tensioned actuated bidirectional clutch mechanism can be used to prevent all actuated bidirectional clutch mechanisms from being in the third arrangement while the shift mechanism is in the first or second state, which could result in a state where no torque is transmitted through the transmission.Furthermore, the pre-tensioned actuated bidirectional clutch mechanism Ci can be configured to allow freewheeling of the sun gear 129i in the first direction of rotation, while preventing rotation of this sun gear 129i in the second direction of rotation. It is also possible that one (or more) of the actuated bidirectional clutch mechanisms Ci is an actuated bidirectional clutch mechanism configured to be in the first arrangement by default and configured to be actively actuated into the second arrangement.

[0124] In the Fig. 1 and Fig.2. The planetary gear set 100 comprises four sun gears 129a, 129b, 129c, 129d, which are meshed with four respective planetary radii 127a, 127b, 127c, 127d of the stepped planetary gear 127. Furthermore, the multiple actuated bidirectional coupling mechanisms Ci comprise four actuated bidirectional coupling mechanisms C1, C2, C3, C4, which are designed for selectively coupling the respective sun gears 129a, 129b, 129c, 129d to the stationary shaft 30. An eight-speed or nine-speed transmission 1000 can thus be obtained. Exemplary transmission states of the shifting mechanism (first actuated clutch mechanism S1 and a second actuated clutch mechanism S2) and of the clutch mechanism (actuated bidirectional clutch mechanisms C1, C2, C3, C4) for the nine-speed transmission 1000 are summarized in Table 1. Table 1 aisle S1 S2 C1 (arrangement) C2 (arrangement) C3 (arrangement) C4 (arrangement) 1 (0,47) uncoupled uncoupled 2. or freewheel 3. 3. 3. 2 (0,56) uncoupled uncoupled 3. 2. 3. 3. 3 (0,68) uncoupled uncoupled 3. 3. 2. 3. 4 (0,83) uncoupled uncoupled 3. 3. 3. 2. 5 (1,00) uncoupled coupled 3. 3. 3. 3. 6 (1,21) coupled coupled 3. 3. 3. 1. 7 (1,46) coupled coupled 3. 3. 1. 3. 8 (1,77) coupled coupled 3. 1. 3. 3. 9 (2,14) coupled coupled 1. 3. 3. 3.

[0125] Exemplary transmission states of the shifting mechanism (first actuated clutch mechanism S1 and a second actuated clutch mechanism S2) and of the clutch mechanism (actuated bidirectional clutch mechanisms C1, C2, C3, C4) for the nine-speed transmission 1000 are summarized in Table 2 for a situation in which the first actuated bidirectional clutch mechanism C1 is a pre-tensioned actuated bidirectional clutch mechanism. Table 2 aisle S1 S2 C1 (arrangement) C2 (arrangement) C3 (arrangement) C4 (arrangement) 1 (0,47) uncoupled uncoupled 2. or freewheel 3. 3. 3. 2 (0,56) uncoupled uncoupled 2. 2. 3. 3. 3 (0,68) uncoupled uncoupled 2. 3. 2. 3. 4 (0,83) uncoupled uncoupled 2. 3. 3. 2. 5 (1,00) uncoupled coupled 2. 3. 3. 3. 6 (1,21) coupled coupled 2. 3. 3. 1. 7 (1,46) coupled coupled 2. 3. 1. 3. 8 (1,77) coupled coupled 2. 1. 3. 3. 9 (2,14) coupled coupled 1. 3. 3. 3.

[0126] In Tables 1 and 2, the 1000 transmission can be operated according to a single gear ratio, but this gear can be optionally omitted. The shift mechanism, for example, can omit the third position, but can only be set between the second and third positions. Without the single gear, the first actuated clutch S1 and the second actuated clutch S2 can be actuated synchronously, with both clutches S1 and S2 switching simultaneously between their engaged and disengaged states. This can simplify the actuation mechanism. One advantage of the single gear is an increase in the gear ratio range. Furthermore, with the single gear, each upshift or downshift to the next higher or lower gear only involves the actuation of one of the first and second actuated clutch mechanisms S1 and S2.

[0127] In Tables 1 and 2, the actuated bidirectional clutch mechanisms also include the optional third arrangement. However, the actuated bidirectional clutch mechanisms Ci can only be set between the first and second arrangements. The transmission from Fig. 1 and Fig. 2 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 arrangement, i.e., provide the second and third arrangements. For a five-speed boost transmission, the clutch mechanisms C1, C2, C3, and C4 can omit the second arrangement, i.e., provide the first and third arrangements. Also in the five-speed transmission, one of the clutches C1, C2, C3, or C4 (e.g., C1) can be a freewheel.

[0128] Without clutches S1 and S2, we can only use gears 1 to 4 or only 5 to 9, with gear 5 being in freewheel mode.

[0129] Without clutches C1 to C4, it is a 3-speed gearbox.

[0130] In the example from Fig. 1 and Fig. In Figure 2, axis 30 has a central axis A. Axis 30 can be, for example, a wheel axle or a countershaft in a crankshaft transmission. An actuator for actuating the clutch mechanisms C1, C2, C3, and C4 is mounted within axis 30. In this example, the actuator is an electromechanical actuator. The electromechanical actuator in this example comprises an electric motor 32. The actuator in this example also includes a camshaft 34, which is mounted within axis 30 for actuating the clutch mechanisms C1, C2, C3, and C4. The electromechanical actuator 32 is configured to rotate the camshaft 34 within axis 30.

[0131] Fig.Figure 13 shows schematic examples of a bicycle transmission 1000 for a human-powered vehicle or light electric vehicle, such as a bicycle, designed as a crank transmission. The axle 30 is non-rotatably connected to a housing 308 of the clutch transmission. The axle 30 is offset and parallel to a crank axle 1004. In this example, the crank axle 1004 includes a first roller 302, and a second roller 304 is mounted at the input I of the transmission for driving the input. Here, the input is driven via a belt 306. It is understood that it is also possible to drive the transmission input I via a chain, a cardan shaft, offset wheels, or the like. The transmission output is connected to a front sprocket 1009 for engaging with a chain or belt of a chain or belt drive 300. Here, the front sprocket 1009 is offset relative to the crank axle 1004.It is clear that it is also possible that the front gear ring 1009 is coaxial with the crank axle 1004. The gearbox 1000 in this example is similar to the gearbox which, with regard to the . Fig. 1 and Fig. 2 is described. In this example, an electric motor 310 is provided in the housing 308. Here, the electric motor 310 drives the gearbox input I, specifically via the belt 306. A gear ratio from the crankshaft 1004 to the gearbox input I is chosen as a speed-increasing gear ratio in order to reduce torque on the gearbox 100. The speed-increasing gear ratio from the crankshaft to the gearbox input can be, for example, about 2.5 or less.

[0132] Fig. Figure 3A shows an example of the actuator. Fig.Figure 3A shows the electromechanical actuator 32 and the camshaft 34. Here, the camshaft comprises a plurality of cams Ni, specifically six cams N1, N2, N3, N4, N5, and N6. The camshaft 34 also includes a single-slot profile for actuating the plurality of clutch mechanisms. This single-slot profile is formed by the plurality of cams Ni extending along an axial direction of the camshaft 34. In this example, the single-slot profile, e.g., the plurality of cams, extends along a line parallel to a central axis A of the camshaft 34.

[0133] Fig. 3B shows the actuator. Fig.3A with pawls Pi, in particular pawls P1, P2A, P2B, P3A, P3B, P4A, P4B. 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 C2, third C3, and fourth C4 clutch mechanism each comprise a first pawl PiA and a second pawl PiB configured to be actuated by the camshaft 34 such that the first pawl PiA selectively engages with the respective sun gear 129i in the first mode, and the second pawl PiB selectively engages with the respective sun gear 129i in the second mode.

[0134] In this example, each pawl Pi comprises two support surfaces Pis, which are supported on the camshaft 34 and can be lifted by the cams Ni. Here, the support surfaces Pis are designed as bearings, such as rolling bearings or plain bearings. In this example, the first pawl P1 of the first clutch mechanism C1 comprises two support surfaces, here two rolling bearings, P1s. The support surfaces P1s are supported on the camshaft 34 and are lifted by the cams N1 and N2. A circumferential groove is provided in the camshaft 34 between the cams N1 and N2 as a spacer for the first pawl P1. In this example, the first and second pawls P2A, P2B of the second clutch mechanism C2 each comprise two support surfaces, here two rolling bearings, P2As, P2Bs. The support surfaces P2As, P2Bs are supported on the camshaft 34 and are lifted by the cams N2 and N3.A circumferential groove is provided in camshaft 34 between cams N2 and N3 to accommodate the first and second pawls P2A and P2B. In this example, the first and second pawls P3A and P3B of the third clutch mechanism C3 each comprise two support surfaces, in this case two rolling bearings, P3As and P3Bs. The support surfaces P3As and P3Bs are supported on camshaft 34 and are raised by cams N3 and N4. A circumferential groove is also provided in camshaft 34 between cams N3 and N4 to accommodate the first and second pawls P3A and P3B. In this example, the first and second pawls P4A and P4B of the fourth clutch mechanism C4 each comprise two support surfaces, in this case two rolling bearings, P4As and P4Bs. The support surfaces P4As, P4Bs are supported on the camshaft 34 and are lifted by the cams N5 and N6.A circumferential groove is provided here in the camshaft 34 between the cams N5 and N6 as a distance for the first and second locking pawls P4A, P4B.

[0135] It is understood that the cams of the camshaft 34 are also possible to be equipped with bearings, such as roller bearings or plain bearings, for contacting the pawls. In one example, the actuator includes a rotation sensor and / or a position sensor. Thus, a gear in which the actuator is positioned can be monitored. For example, it is possible to monitor the rotational position of the electromechanical actuator 32 and / or the camshaft 34.

[0136] Fig. Figure 7B shows an example in which two sun gears 129a, 129b are shown mounted on the axle 30 over the respective pawls P1, P2A, P2B. For clarification, the sun gears 129c, 129d are shown in Fig. 7B not shown.

[0137] As in the Fig.As can be seen in more detail in 4A-4H, the pawls assigned to larger sun gears in this example also have larger rolling bearings for support surfaces than pawls assigned to smaller sun gears.

[0138] In this example, in each coupling mechanism C1, C2, C3, C4, the first pawl P1, P2A, P3A, P4A and the second pawl P2B, P3B, P4B are configured to pivot about their respective pivot axis. In this example, each pawl includes two projections Pip that form one end of a pivot axis P of the respective pawl. The projections P2Bp of the second pawl P2B of the second coupling mechanism C2 are in Fig. 3B is specified. It is understood that the other pawls in this example have similar protrusions.

[0139] As in Fig.As can be seen in Figure 3B, the pawls of the coupling mechanisms C1, C2, C3, and C4 are positioned rotated about the central axis A. That is, the pawl P1 of the first coupling mechanism C1 is positioned rotated about the central axis A relative to the pawls of the second, third, and fourth coupling mechanisms C2, C3, and C4. The first and second pawls P2A and P2B of the second coupling mechanism C2 are positioned rotated about the central axis A relative to the pawls of the first, third, and fourth coupling mechanisms C1, C3, and C4. The first and second pawls P3A and P3B of the third coupling mechanism C3 are positioned rotated about the central axis A relative to the pawls of the first, second, and fourth coupling mechanisms C1, C2, and C4. The first and second pawls P4A, P4B of the fourth clutch mechanism C4 are positioned rotated around the central axis A relative to the pawls of the first, second and third clutch mechanisms C1, C2, C3.Thus, a first position of at least one pawl of at least one of the coupling mechanisms is rotated about the central axis relative to a second position of at least one pawl of at least one other of the coupling mechanisms. Here, a first position of the first and second pawls of at least one of the coupling mechanisms is rotated about the central axis relative to a second position of the first and second pawls of at least one other of the coupling mechanisms. As with regard to the . Fig.As discussed in sections 4A-4H, in one example the pawls are positioned such that a rotation of the camshaft in a single direction sequentially actuates the respective pawls, selecting the transmission ratios in ascending or descending order. In this example, the pawl positions are spaced 40 degrees apart. Thus, the camshaft can be rotated more than eight times by 40 degrees to access nine different transmission ratios.

[0140] Fig. Figure 3B further shows two bearings 36, here roller bearings (but plain bearings are also possible), to support the camshaft 34 within the axis 30.

[0141] Fig. 3C shows the actuator from Fig. 3A and Fig. 3B within axis 30. As in Fig.As shown in Figure 3C, in this example, the axis 30 has a multitude of axis sections with different outer diameters. In this example, the first axis section 30A has a smaller outer diameter. The first 129a and the second 129b sun gear can be mounted on the first axis section 30A. A second axis section 30B has a smaller outer diameter than the first axis section 30A. The third sun gear 129c can be mounted on the second axis section 30B. A third axis section 30C has a smaller outer diameter than the second axis section 30B. The fourth sun gear 129d can be mounted on the third axis section 30C. Thus, the axis 30 has different outer radii at the positions of different sun gears 129i within the multitude of sun gears.The different outer diameters of the axle sections 30A, 30B, 30C facilitate the assembly of the coupling mechanisms C1, C2, C3, C4. These different outer diameters also allow for the provision of a larger diameter axle section to support sun gears that transmit a higher torque to axle 30. Preferably, the torque is transmitted from axle 30 to the bicycle frame on the side of axle 30 with the largest axle section diameter, i.e., the non-drive side.

[0142] It is in Fig.Figure 3C also shows that the radial distance between a pivot axis p of the pawls and the central axis A of axis 30 differs for the various coupling mechanisms C1, C2, C3, C4 of the multitude of coupling mechanisms. For all pawls Pi, the pivot axis p of the respective pawls Pi is positioned such that the pivot axis P is located exactly below the surface of the respective axis area. In this example, a first radial distance between the pivot axis p of the first pawl P1 of the first coupling mechanism C1 and the central axis A of axis 30 is equal to a second radial distance between the pivot axis p of the first and second pawls P2A, P2B of the second coupling mechanism C2 and the central axis A of axis 30.In this example, the first radial distance between the pivot axis p of the first and second pawls P2A, P2B of the second coupling mechanism C2 and the central axis A of axis 30 is greater than a third radial distance between the pivot axis p of the first and second pawls P3A, P3B of the third coupling mechanism C3 and the central axis A of axis 30. In this example, the third radial distance between the pivot axis p of the first and second pawls P3A, P3B of the third coupling mechanism C3 and the central axis A of axis 30 is greater than a fourth radial distance between the pivot axis p of the first and second pawls P4A, P4B of the fourth coupling mechanism C4 and the central axis A of axis 30.It is understood that in this example a radial distance between the tops of the cams N5, N6 of the fourth clutch mechanism C4 and the central axis A is also smaller than a radial distance between the tops of the cams N1, N2, N3, N4 of the first, second and third clutch mechanisms C1, C2, C3 and the central axis.

[0143] The pivot axis p of the pawls is held at a radial distance from the central axis A in a pocket formed in axis 30. In particular, the projections Pip, which form the ends of the pivot axis P of the respective pawl, are embedded in pockets formed in axis 30.

[0144] The Fig. 4A-4H show a sequence of gear changes using the gearbox from the Fig.1-3C. In this example, when the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30 while the shifting mechanism is in the first state, the ring gear 128 is also driven in the first direction of rotation, and a rotational force is induced on the sun gears 129i in the second, reversed direction of rotation via the stepped planetary gear 127. By selectively braking one of the sun gears 129i in the second direction of rotation with a corresponding clutch mechanism Ci, torque can be transmitted from the ring gear 128 to the planet carrier 126 according to a creep transmission ratio.

[0145] Fig. Figure 4A shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the first state. The first actuated bidirectional clutch mechanism C1 is in the second arrangement in Fig.Figure 4A shows the first actuated bidirectional clutch mechanism C1. In this example, it is a pre-tensioned actuated bidirectional clutch mechanism with only a single pawl P1. The pawl P1 is not actuated by the cam N1, N2 in the first position. The pre-tensioned actuated bidirectional clutch mechanism C1 includes a freewheel clutch 15 that allows rotation in the first direction R1 and blocks rotation in the second direction R2. Fig.Figure 5A shows an example of the freewheel clutch 15 of the preloaded actuated bidirectional clutch mechanism C1. Here, the freewheel clutch 15 comprises a plurality of rolling elements 15r, such as balls or cylinders, between an inner race 15i and an outer race 150. In this example, the outer race 150 has 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 planet gear 127 and to the output O via the planet carrier 126. The gear ratio is determined by the first sun gear 129a and the first planet gear section 127a and represents the lowest gear ratio (first gear, creeper gear).

[0146] Fig.Figure 4B shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the first state. The second actuated bidirectional clutch mechanism C2 is shown in the second arrangement. Fig.Figure 4B shows the camshaft being rotated into a second position. The second pawl P2B is actuated by the cam N2, N3 in the second position. A mating surface of the second pawl P2B engages with a corresponding mating surface associated with the second sun gear 129b, blocking rotation in the second direction R2. Thus, the second sun gear 129b is braked, and torque is transmitted from input I via the ring gear 128 to the planet gear 127 and then to output O via the planet carrier 126. The gear ratio is determined by the second sun gear 129b and the second planet gear section 127b and represents the next higher gear ratio (second gear, creeper gear).

[0147] Fig.Figure 4C shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the first state. The third actuated bidirectional clutch mechanism C3 is shown in the second arrangement in Fig.Figure 4C shows the camshaft being rotated to a third position. The second pawl P3B is actuated by the cam N3, N4 in the third position. A mating surface of the second pawl P2B engages with a corresponding mating surface associated with the third sun gear 129c, blocking rotation in the second direction R2. Thus, the third sun gear 129c is braked, and torque is transmitted from input I via the ring gear 128 to the planet gear 127 and then to output O via the planet carrier 126. The gear ratio is determined by the third sun gear 129c and the third planet gear section 127c and represents the next higher gear ratio (third gear, creeper gear).

[0148] Fig.Figure 4D shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the first state. The fourth actuated bidirectional clutch mechanism C4 is shown in the second arrangement in Fig.Figure 4D shows the camshaft being rotated to a fourth position. The second pawl P4B is actuated by the cam N5, N6 in the fourth position. A mating surface of the second pawl P4B engages a corresponding mating surface associated with the fourth sun gear 129d, blocking rotation in the second direction R2. Thus, the fourth sun gear 129d is braked, and torque is transmitted from input I via the ring gear 128 to the planet gear 127 and then to output O via the planet carrier 126. The gear ratio is determined by the fourth sun gear 129d and the fourth planet gear section 127d and represents the next higher gear ratio (fourth gear, creeper gear).

[0149] Fig.Figure 4E shows a situation in which the camshaft 34 is rotated to its fifth position. In this fifth position, the fourth actuated bidirectional clutch mechanism C4 is in its third position. Thus, neither the first pawl P4A nor the second pawl P4B is raised by the cams N5 and N6. In this situation, the shift mechanism is switched to its third position. The ring gear 128 and the planet carrier 126 are then coupled to rotate together. Torque is transmitted from the input I to the output O via the ring gear and / or the planet carrier 126. It is understood that in this example, the cams N5 and N6 of the fourth clutch mechanism C4 are wider than those N1-N4 of the other clutch mechanisms C1, C2, and C3. This allows for a smooth transition from fourth to fifth gear (and from fifth to sixth gear).This situation represents a next higher translation ratio, which corresponds to a uniform translation ratio (fifth gear, uniform translation ratio).

[0150] The shifting mechanism is then switched to the second state. If the transmission input I is driven in the first direction of rotation about the stationary axis 30 while the shifting mechanism is in the second state, the planet carrier 126 is also driven in the first direction of rotation, and a rotational force is induced on the sun gears 129i in the first direction of rotation via the stepped planetary gear 127. By selectively braking one of the sun gears 129i in the first direction of rotation with a corresponding clutch mechanism Ci, torque can be transmitted from the planet carrier 128 to the ring gear 126 according to a high-speed gear ratio.

[0151] Fig.Figure 4F shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the second state. The fourth actuated bidirectional clutch mechanism C4 is in the first arrangement in Fig.Figure 4F shows the camshaft being rotated to its sixth position. The first pawl, P4A, is actuated by the cams N5 and N6 in the sixth position. A contact surface of the first pawl, P4A, engages a corresponding contact surface associated with the fourth sun gear, 129d, and blocks rotation in the first direction, R1. Thus, the fourth sun gear, 129d, is braked, and torque is transmitted from input I, via the planet carrier, 126, to the planet gear, 127, and via the ring gear, 128, to the output O. The gear ratio is determined by the fourth sun gear, 129d, and the fourth planet gear, 127d, and represents the next higher gear ratio (sixth gear, overdrive).

[0152] Fig.Figure 4G shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the second state. The third actuated bidirectional clutch mechanism C3 is in the first arrangement in Fig.Figure 4F shows the camshaft being rotated to its seventh position. The first pawl, P3A, is actuated by the cams N3 and N4 in the seventh position. A mating surface of the first pawl, P3A, engages with a corresponding mating surface associated with the third sun gear, 129c, and blocks rotation in the first direction, R1. Thus, the third sun gear, 129c, is braked, and torque is transmitted from input I, via the planet carrier, 128, to the planet gear, 127, and via the ring gear, 126, to the output O. The gear ratio is determined by the third sun gear, 129c, and the third planet gear, 127c, and represents the next higher gear ratio (seventh gear, overdrive).

[0153] Fig.Figure 4H shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the second state. The second actuated bidirectional clutch mechanism C2 is in the first arrangement in Fig.Figure 4G shows the camshaft being rotated to its eighth position. The first pawl P2A is actuated by the cams N2 and N3 in the eighth position. A mating surface of the first pawl P2A engages a corresponding mating surface associated with the second sun gear 129b, blocking rotation in the first direction R1. This brakes the second sun gear 129b, and torque is transmitted from input I via the planet carrier 128 to the planet gear 127 and via the ring gear 126 to the output O. The gear ratio is determined by the second sun gear 129b and the second planet gear section 127b and represents the next higher gear ratio (eighth gear, overdrive).

[0154] Fig.Figure 4I shows a situation in which the transmission input I is driven in the first direction of rotation R1 about the stationary axis 30, while the shifting mechanism is in the second state. The first actuated bidirectional clutch mechanism C1 is in the first arrangement in Fig.Figure 4H shows the camshaft being rotated to its ninth position. The pawl P1 is actuated by the cam N1, N2 in the ninth position. A mating surface 38 of the pawl P1 engages a corresponding mating surface 40, which is associated with the first sun gear 129a, and blocks rotation in the first direction R1. Thus, the first sun gear 129a is braked, and torque is transmitted from the input I via the planet carrier 128 to the planet gear 127 and via the ring gear 126 to the output O. The gear ratio is determined by the first sun gear 129a and the first planet gear section 127a and represents the next higher gear ratio (ninth gear, overdrive).

[0155] It is understood that, while shifting through the successive gears from the lowest (here first) to the highest (here ninth) gear, the sun gears 129i are first used in a sequence from the largest to the smallest sun gear and then in a sequence from the smallest to the largest sun gear.

[0156] Fig.Figure 5B shows an example of a sun gear 129i with an actuated bidirectional clutch mechanism Ci. The pawls PiA, PiB are generally L-shaped in this example. The pawls PiA, PiB have a first body section 44 extending from the pivot axis P to the engagement surface 38. The first body section extends substantially tangentially to the outer surface of the axis 30. The pivot axis P is pivotally supported in a pocket 48 of the axis 30. The pawls PiA, PiB have a second body section 46 extending substantially radially inward. The second body section 46 carries the support surfaces Pis. Here, the second body section has two axially oriented protrusions on which rolling bearings are mounted, forming the support surfaces Pis.In this example, the engagement surface 38 of the pawls Pi and the corresponding engagement surface 40 of the sun gear 129i are angled relative to the radial direction. The angle is chosen such that moving the engagement surfaces 38 and 40 relative to each other and towards each other tends to move the pawl Pi radially inwards. Thus, the pawls Pi are biased to disengage. A spring can be added for spring-loaded disengagement of the pawls Pi. Fig. Figure 7A shows an example of the pawls Pi, which are pre-tensioned by a spring 121. Thus, the actuated bidirectional clutch mechanism Ci is pre-tensioned to disengage. In the first and second arrangements, the presence of the cam Ni under the support surfaces Pis prevents the engagement surfaces 38, 40 from separating when pressed against each other. Fig.In 5B, the camshaft 34 is positioned such that the clutch mechanism Ci is in the first arrangement. In this first arrangement, a rotation of the sun gear 129i in the first direction of rotation R1 presses the engagement surfaces against each other, whereby the first pawl PiA is pressed into the pocket 48 against a radial end wall 49 of the pocket 48 and a rotation of the sun gear 129i in the first direction of rotation is prevented (see corresponding Fig. 4G). Fig.Figure 5B shows the specific situation in which the clutch mechanism Ci is in the first arrangement and the sun gear 129i is driven in the second direction of rotation R2. The actuated bidirectional clutch mechanism Ci is configured such that, in the first arrangement, the sun gear 129i is prevented from rotating in the first direction of rotation R1, but is allowed to rotate in the second direction of rotation R2 (freewheel). In this case, the projections 50 of the inner circumference of the sun gear 129i push the first pawl PiA in the first direction of rotation, whereby the pawl PiA is moved tangentially within the pocket 48, away from the radial end wall 49 of the pocket, so that the support surfaces Pis release the cam Ni. This causes the first pawl PiA to pivot radially inwards, so that the engagement surface 38 of the pawl PiA is at a radius that is smaller than the engagement surface 40 of the sun gear 129i.As a result, the sun gear 129i can run freely in the first direction of rotation R1, while the clutch mechanism Ci is in the first arrangement.

[0157] In this example, the first pawl PiA has a projection 52, such as a raised section, on a radial outer surface of the pawl PiA. The projection 52 can be engaged by the projection 50 of the sun gear 129i to facilitate tangential movement of the pawl PiA, thus releasing the cam Ni. In this example, a spring or other elastic element is provided to bias the pawl PiA back into the pocket 48. The spring or other elastic element can pull the pawl so that the pivot axis P rests tangentially against the radial end wall of the pocket 48. It is understood that, similarly, the actuated bidirectional clutch mechanism Ci is configured such that, in the second arrangement, the sun gear 129i is prevented from rotating in the second direction R2, but is allowed to rotate in the first direction R1 (freewheeling).

[0158] Fig.Figure 8A shows an example in which the spring 121 has the combined function of pre-tensioning the pawls PiA, PiB into the pocket 48 and pre-tensioning the pawls PiA, PiB radially inward to pre-tension a separation of the engagement surfaces 38, 40. In this example, the spring 121 comprises a helically wound section 121a. Two arms 121b, 121c extend from the ends of the helically wound section. The distal ends of the arms 121b, 121c overlap in this example. As a result, the spring 121 winds around the axis 30 by more than 360 degrees. The distal ends of the arms 121b, 121c each have a hook 121d, 121e. In this example, the spring comprises a single helically wound section 121a. It is understood that the spring can also comprise more than one, e.g., two, helically wound sections. As in Fig.As shown in Figure 8B, the hooks 121d and 121e engage the respective pawls PiA and PiB. The tensile force of the spring 121 thus pre-tensions the pawls PiA and PiB, so that the pivot axis P rests tangentially against a radial end wall of the pocket 48. Furthermore, the arms 121b and 121c of the spring are positioned in circumferential grooves Pig of the pawls PiA and PiB (see, for example, grooves P1g, P2g, P3g, and P4g in the figures). Fig. 7A and Fig.7B), so that a tensile force of the spring 121 biases the pawls PiA, 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 a circumferential groove 30g in 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 a first pawl PiA, and a second end 121e of the spring is attached to a second pawl PiB. Thus, here the spring 121 pulls the pawls PiA, PiB towards each other. It is understood that it is also possible for each pawl to have one or more individual springs assigned to it.

[0159] Back to the Fig. 1, Fig. 2 and Fig.In 3A, the camshaft 34 is further configured to actuate the shifting mechanism. In this example, the camshaft includes one or more grooves 54, here two grooves, for actuating the shifting mechanism. The camshaft 34 is configured to move a selection unit 56 axially from a first position to a second position or from the second position to the first position. Here, the selection unit 56 includes a pin 58 that extends into the groove 54. It is understood that the groove 54 is shaped such that a rotation of the camshaft 34 moves the pin 58 and thereby the selection unit 56 axially. The first actuated clutch S1 and / or the second actuated clutch S2 are configured to shift from a engaged state to a disengaged state or from a disengaged state to a engaged state upon axial movement of the selection unit 56.In this example, the grooves 54 are shaped such that the first actuable clutch S1 and the second actuable clutch S2 transition essentially simultaneously from the coupled state to the decoupled state or from the decoupled state to the coupled state.

[0160] The actuated clutches S1, S2 of the shifting mechanism may be similar to or identical with a clutch as described in WO2018 / 199757A2, WO2020 / 085911A2, WO2021 / 080431A1 or WO2021 / 249945A1, which are incorporated in their entirety by reference in this document. With reference to the Fig. 6A and Fig.6B The actuated couplings S1, S2 can have a first rotatable unit 80, which includes at least one first support surface 82, and a second rotatable unit 84, which includes at least one second support surface 86, designed to selectively engage the first support surface. The first and second support surfaces 82, 86 are adapted to each other to allow separation under load, preferably in two directions. The actuated couplings S1, S2 can have a third rotatable unit 88, which includes at least one retaining element 90. The third rotatable unit 88 is designed to selectively engage the first support surface in a first mode ( Fig. 6A) or a second mode ( Fig.6B) relative to the second rotatable unit 84. In the first mode, the at least one retaining element 90 locks the at least one second support surface 86 for rotating coupling of the second rotatable unit 84 with the first rotatable unit 80, e.g., in two directions of rotation. In the second mode, the at least one retaining element 90 releases the at least one second support surface 86 for decoupling the second rotatable unit 84 from the first rotatable unit 80. The actuated coupling can accommodate an actuator for moving the third rotatable unit from a first position ( Fig. 6A) into a second position ( Fig.6B) or from a second position to a first position relative to the second rotatable unit. Here, the second rotatable unit 84 carries gripping elements 92. The gripping elements have a second bearing surface 86. The gripping elements 92 are pivotally connected to the second rotatable unit 84. In the first position, the retaining element 90 is positioned such that it presses the second bearing surfaces 86 of the gripping element 92 radially outward into engagement with the first bearing surfaces 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 to each other and toward each other tends to move the gripping element 92 radially inward. Thus, the gripping elements 92 are pre-tensioned to separate. A spring can be added for spring-loaded separation of the gripping elements 92.Thus, the actuated couplings S1 and S2 are pre-tensioned to separate. In the first position, the presence of the retaining element beneath the gripping element 92 prevents the engagement surfaces 82 and 86 from separating when pressed against each other. In the second position, the retaining element 90 is positioned such that it allows the gripping element 92 to pivot radially inwards, thus enabling the separation of the second support surface 86 from the first support surface 82.

[0161] The third rotatable unit 88 includes at least one actuating element 94, which is designed to move the third rotatable unit 88 from a first position to a second position or from a second position to a first position relative to the second rotatable unit 84. In this example, the actuated couplings S1, S2 further include a fourth unit 96, which includes a selection unit 98. The fourth unit 96 may be non-rotatable, e.g., relative to the axis 30. The selection unit is designed to be selectively in a gripping or non-gripping mode. The selection unit 98 in gripping mode is designed to grip the at least one actuating element 94 to rotate the third rotatable unit 88 from the first position to the second position or from the second position to the first position relative to the second rotatable unit 84.The selection unit 98 in the non-gripping mode is designed to disconnect the at least one actuating element 94.

[0162] The Fig. 9A and Fig. Figure 9B shows an example of the selection unit 98. In this example, the selection unit includes one or more grooves 120 that are fixed relative to the axis 30. The selection unit further includes a selection bushing 122 that is axially movable relative to the axis 30. The bushing 122 comprises a first region 122A of a first outer diameter and a second region 122B having a second outer diameter that is smaller than the first outer diameter. In this example, the bushing 122 can be moved axially by a pin 124 that sits in the groove 54 of the camshaft 34. The bushing 122 can be moved into a first position ( Fig. 9A) and a second position ( Fig. 9B). As in the Fig. 9A and Fig.As can be seen in Figure 9B, the two actuating elements 94A and 94B are slightly different in this example. In particular, the cutouts 126A and 126B of the respective actuating elements 94A and 94B are positioned differently.

[0163] With the socket in the first position, as in Fig. As shown in Figure 9A, the first actuating element 94A sits with its radially inwardly directed end against the first area 122A with the larger outer diameter of the bushing. This prevents the first actuating element 94A from entering the groove 120. With the bushing in the first position, as shown in Figure 9A, the first actuating element 94A is positioned in the first position. Fig. As shown in Figure 8A, the cutout 126B of the second actuating element 94B is aligned with the first area 122A, which has the larger outer diameter of the bushing. This prevents the second actuating element 94A from entering the groove 120. With the bushing in the second position, as shown in Fig.As shown in Figure 9B, the second actuating element 94B sits with its radially inwardly directed end against the first area 122A with the larger outer diameter of the bushing. This prevents the second actuating element 94B from entering the groove 120. With the bushing in the second position, as shown in Figure 9B, the second actuating element 94B is positioned in the first area 122A with the larger outer diameter of the bushing. Fig. As shown in Figure 9B, the cutout 126A of the first actuating element 94A is aligned with the first area 122A, which has the larger outer diameter of the bushing. This prevents the first actuating element 94A from entering the groove 120. As soon as the first or second actuating element 94A, 94B enters the groove 120, the third rotatable unit 88 is temporarily stopped, causing it to rotate relative to the second rotatable unit 84. The rotatable unit 88 rotates relative to the second rotatable unit 84 from a first position ( Fig. 6A) into a second position ( Fig.6B) or from a second position to a first position. Thus, the actuated clutch S1, S2 engages or disengages. After the third rotatable unit 88 has moved from a first position to a second position or from a second position to a first position, the respective actuating element 94A, 94B is driven out of the respective groove 120 by a reset element 128, e.g., rotating together with the second rotatable unit 84.

[0164] Optionally, an elastic element is placed in the connection between the camshaft 34 and the selector bushing 122. The elastic element allows the camshaft 34 to begin the axial movement of the bushing 122, while the bushing 122 is (temporarily) prevented from actually performing the axial movement, for example, because it is blocked by one or more of the actuating elements 94A, 94B. For instance, if the first actuating element 94A is in the groove 120, it can prevent the bushing 122 from moving from the first position to the second position. In this situation, if the camshaft is rotated to axially move the bushing 122 from the first position to the second position, the elastic element will be deformed.Once the first actuating element 94A is lifted out of the groove, the bushing 122 can perform (or complete) the axial movement already being forced by the camshaft 34. For example, if the second actuating element 94B is in the groove 120, it can prevent the bushing 122 from moving from the second position to the first position. In this situation, if the camshaft is rotated to axially move the bushing 122 from the second position to the first position, the elastic element will be deformed. Once the second actuating element 94B is lifted out of the groove, the bushing 122 can perform (or complete) the axial movement already being forced by the camshaft 34.

[0165] The elastic element can be a conforming mechanism. The elastic element can be pre-stressed, e.g., in two directions, such as two axial directions. The elastic element can be placed, e.g., in the bushing 122, between the bushing 122 and the pin(s) 124, between the pin(s) 124 and the groove 54, and / or between the groove 54 and the camshaft 34.

[0166] The Fig.Figures 10A-10C show an example of the selection unit 98. In this example, the selection unit includes one or more grooves 120 that are fixed relative to the axis 30. In this example, the selection unit 122 comprises a first area 122A with a first outer diameter. The second area 122B, which has a second outer diameter smaller than the first outer diameter, is omitted in this example. In this example, the bushing 122 can also be moved axially by the pin 124, which sits in the groove 54 of the camshaft 34. The bushing 122 can be moved into a first position ( Fig. 10A) and a second position ( Fig. 10B). With socket 122 in the first position, as shown in Fig. As shown in Figure 10A, the first actuating element 94A sits with its radially inwardly directed end against the first area 122A with the outer diameter of the bushing. This prevents the first actuating element 94A from entering the groove 120. With the bushing in the first position, as shown in Fig. As shown in Figure 10A, the cutout 126B of the second actuating element 94B is aligned with the first area 122A with the outer diameter of the bushing. This prevents the second actuating element 94A from entering the groove 120. With the bushing in the second position, as shown in Fig. As shown in Figure 10B, the second actuating element 94B sits with its radially inwardly directed end against the first area 122A with the outer diameter of the bushing. This prevents the second actuating element 94B from entering the groove 120. With the bushing in the second position, as shown in Fig. As shown in Figure 9C, the first actuating element 94A is enabled to enter the groove 120. In this example, the first actuating element 94A does not have a cutout 126A. Instead, the width of the first actuating element 94A is chosen such that, with the bushing in the second position, it allows the first actuating element 94A to enter the groove 120. As soon as the first or the second actuating element 94A, 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 rotatable unit 88 rotates relative to the second rotatable unit 84 from a first position ( Fig. 6A) into a second position ( Fig. 6B) or from a second position to a first position. Thus, the actuated clutch S1, S2 engages or disengages. After the third rotatable unit 88 has moved from a first position to a second position or from a second position to a first position, the respective actuating element 94A, 94B is driven out of the respective groove 120 by a reset element 128, e.g., rotating together with the second rotatable unit 84.

[0167] Fig. Figure 10C shows a side view of an example of the bushing 122. In this example, the pin 124 is connected to the bushing 122 via a tangential arm 124A. A proximal end of the arm 124A is connected to the bushing 122, while a distal end of the arm 124A is connected to the pin 124. In this example, the arm is made of an elastic material, such as a plastic. The arm 124A forms the elastic element referred to above. The arm accommodates the pin, which already moves in an axial direction along the axis 30, while the fact that the first or second actuating element is positioned in a groove 120 further prevents the bushing 122 from moving axially.

[0168] The Fig. Figures 11A-11C show an example of the selection unit 98. In this example, the selection unit includes one or more grooves 120 that are fixed relative to the axis 30. In this example, the selection unit 122 comprises a first area 122A with a first outer diameter. The second area 122B, which has a second outer diameter smaller than the first outer diameter, is omitted in this example. In this example, the bushing 122 can also be moved axially by the pin 124, which sits in the groove 54 of the camshaft 34. The pin can be moved, for example, by means of an arm 124A that is located in Fig. As shown in Figure 10C, the bushing 122 is connected to the pin. The pin extends through a cutout 123 in the axis 30. In one example, the bushing 122 has a plurality of pins 124 connected to it, such as 2 or 3 pins, e.g., evenly distributed around the circumference of the bushing 122. The bushing 122 can be moved into a first position ( Fig. 11A) and a second position ( Fig. 11C). As in the Fig. As can be seen in Figures 11A-11C, the groove 54 has two legs extending transversely 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 position in the first or second position. The arm 124A can be clamped in the first and / or second position, so that the bushing 122 is pressed against an axial side 30A, 30B. This ensures a stable positioning of the bushing 122. Fig. Figure 11B shows an intermediate position in which the camshaft 34 is rotated such that the pin 124 is in an inclined area of ​​the groove 54 that connects the two legs. The two actuating elements 94A and 94B can be operated similarly to those shown in the Fig. 9A and Fig. 9B or Fig. 10A and Fig. It will be 10B.

[0169] The first and second actuating elements 94A, 94B can, for example, be used as in the Fig. 9A, Fig. 9B, Fig. 10A or Fig. 10B will be shown. With socket 122 in the first position, as shown in Fig. As shown in 11A, the first actuating element 94A can sit with its radially inwardly directed end on the first area 122A with the outer diameter of the bushing.

[0170] This prevents the first actuating element 94A from entering the groove 120. With the bushing in the first position, as in Fig. As shown in Figure 11A, the cutout 126B of the second actuating element 94B can be aligned with the first area 122A, which has the larger outer diameter of the bushing. This prevents the second actuating element 94A from entering the groove 120. With the bushing in the second position, as shown in Figure 11A, the opening 126B of the second actuating element 94B can be aligned with the first area 122A, which has the larger outer diameter of the bushing. This prevents the second actuating element 94A from entering the groove 120. Fig. As shown in Figure 11C, the second actuating element 94B, with its radially inwardly directed end, can sit on the first area 122A with the outer diameter of the bushing. This prevents the second actuating element 94B from entering the groove 120. With the bushing in the second position, as shown in Figure 11C, the second actuating element 94B can be seated with its radially inwardly directed end on the first area 122A with the outer diameter of the bushing. Fig. As shown in Figure 9C, the cutout 126A of the first actuating element 94A can be aligned with the first area 122A with the outer diameter of the bushing. Alternatively, the first actuating element may not have a cutout, as shown in Figure 9C. Fig. 10A, Fig. 10B described. This prevents the first actuating element 94A from entering the groove 120. As soon as the first or the second actuating element 94A, 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 rotatable unit 88 rotates relative to the second rotatable unit 84 from a first position ( Fig. 6A) into a second position ( Fig. 6B) or from a second position to a first position. Thus, the actuated clutch S1, S2 engages or disengages. After the third rotatable unit 88 has moved from a first position to a second position or from a second position to a first position, the respective actuating element 94A, 94B is driven out of the respective groove 120 by a reset element 128, e.g., rotating together with the second rotatable unit 84.

[0171] In one example, the bicycle transmission includes an electric drive for powering or assisting the propulsion of the bicycle. The electric drive can be mounted concentrically around the axis 30. Alternatively, the electric drive can be mounted at least partially inside the axis 30. The electric drive can include an electric motor. The electric motor can include a stator and a rotor. The electric drive can include a planetary gear set. The electric drive can include a rotation sensor and / or a position sensor.

[0172] Back at Fig. The bicycle transmission 1000 comprises the hub housing 51 for connection to a bicycle wheel, e.g., via spoke flanges 140. The bicycle transmission 1000 further comprises a rider part 142 for connection to one or more sprockets 3. In this example, the rider part 142 is mounted on the wheel axle 30 via a first bearing 144, here two first bearings. The hub housing 51 is mounted on the wheel axle 30 via a second bearing 146 and on the rider part 142 via a third bearing 148. The bicycle transmission 1000 further comprises the transmission system 100. In this example, the transmission system comprises the planetary gear set 100. In this example, the transmission system 100 is positioned between the second and third bearings 146, 148. In this example, the shifting mechanism S1, S2 and the clutch mechanisms C1, C2, C3, C4 are positioned between the second and third bearings 146, 148.

[0173] The bicycle gearbox 1000 also includes control electronics 150 for controlling the actuator, e.g., the electromechanical actuator 32. In this example, the control electronics 150 is positioned behind the second bearing 146 when viewed from the gearbox system 100. As in Fig. As can be seen in Figure 1, the hub housing 51 encloses a first cavity between the second bearing 146 and the third bearing 148. The gear system 100 is positioned in the first cavity. The control electronics 150 are positioned outside the first cavity. In this example, the control electronics 150 are mounted distal to the hub bearing 146 on the non-drive side. However, it is possible for the control electronics 150 to be mounted distal to the hub bearing 148 on the drive side.

[0174] In the example from Fig. 1. The hub housing 51 extends beyond the second bearing 146 when viewed from the perspective of the transmission system 100 and encloses the control electronics 150. The control electronics 150 are, for example, immobilely mounted on the axle 30, such as concentrically on the axle. The control electronics comprise at least one of a controller, a generator, a battery, a circuit board, a wireless receiver / transmitter, an antenna, an LED, a charging connector, a connecting element, or a microchip. In this example, the control electronics are mounted behind an enclosure 152. The enclosure 152 is preferably transparent to wireless signals. The enclosure can, for example, be made of a plastic material.

[0175] A receiver of the control electronics 150 can be configured to receive a shift control signal, such as from a shift device 1024. The shift control signal can represent a desired gear (e.g., first gear, second gear, third gear, etc.). The shift control signal can represent an upshift or downshift. Based on the shift control signal, the controller can be configured to control the actuator, such as the electromechanical actuator. Alternatively or additionally, the controller can be configured to autonomously change a gear, e.g., based on a current gear, wheel speed, cadence, torque, and / or heart rate. In particular, if the transmission system includes the generator and is configured to autonomously change the gear ratio, a self-contained, autonomous transmission can be provided.Optionally, features of the transmission system, such as parameters for shifting gears, can be set by a user, e.g. using an interface, such as on a mobile communication device, such as a smartphone, in (wireless) communication with the control electronics.

[0176] In the example from Fig. 1 The hub housing 51 comprises an inner hub housing 51i, which encloses the axle 30, and an outer hub housing 51o, which is configured for connection with the wheel. Here, the control electronics 150 are positioned so that they are replaceable after the inner hub housing 51i has been removed from the outer hub housing 51o.

[0177] Fig.Figure 12 shows an example of a bicycle 1. The bicycle includes a frame 1002 and a front fork 1005. The bicycle includes a handlebar 1003. A front wheel 1011 is mounted on the front fork 1005. The frame 1002 includes a rear triangle 1007, which has a rear wheel 1013 mounted to it. The crank axle 1004 is mounted on the frame 1002. Pedals 1017 are connected to the crank axle 1004. A front sprocket 1009 is also connected to the crank axle 1004. The rear wheel has 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 via the transmission system 100, e.g., as described above. Alternatively or additionally, the crank axle 1004 can be connected to the front gear ring 1009 via a gear system 100, e.g. as described above.The front sprocket 1009 drives the rear sprocket 1021 via an endless element, such as a chain or belt. The bicycle 1 in this example includes a shifting device 1024, which is configured to transmit a shift control signal to a receiver of the control electronics 150 of the transmission system 100.

[0178] In this document, the invention is described with reference to specific examples of embodiments of the invention. However, it is obvious that various modifications and changes can be made to it without departing from the essence of the invention. For the sake of clarity and a concise description, features are described in this document as part of the same or separate embodiments; however, alternative embodiments are also considered that have combinations of all or some of the features described in these separate embodiments.

[0179] The examples provide an eight-speed or nine-speed transmission system using different sun gears. It is understood that it is also possible to provide the transmission system with fewer or more different gear ratios, such as 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). The number of planetary gear sections with different radii of the stepped planetary gears can correspond to the number of different sun gears.

[0180] In the example, each sun gear is associated with an actuated bidirectional clutch mechanism configured to selectively prevent rotation of the at least one sun gear in a first direction around the axis in a first mode (and optionally allow rotation of the at least one sun gear in an opposite second direction around the axis) and to selectively prevent rotation of the at least one sun gear in the opposite second direction around the axis in a second mode (and optionally allow rotation of the at least one sun gear in the first direction around the axis) in order to provide two different gear ratios with one sun gear.It is understood that the transmission system may further include one or more sun gears having an associated unidirectional coupling mechanism configured to selectively prevent, in a first mode, rotation of the at least one sun gear in a first direction of rotation about the axis (and optionally to allow rotation of the at least one sun gear in the opposite second direction of rotation about the axis) and, in a second mode, to allow rotation of the at least one sun gear in the first direction of rotation (and optionally to allow rotation of the at least one sun gear in the opposite second direction of rotation about the axis).

[0181] However, other modifications, variations, and alternatives are also possible. The specifications, drawings, and examples are therefore to be understood in an illustrative, not a limiting, sense.

[0182] In patent claims, reference numerals enclosed in parentheses are not to be interpreted as limiting the patent claim. The word "comprising" does not preclude the presence of features or steps other than those listed in a patent claim. Furthermore, the words "a" and "a" are not to be interpreted as limiting them to "only one," but are instead used to mean "at least one," and do not exclude a plurality. The mere fact that certain measures are mentioned in different patent claims does not indicate that a combination of these measures cannot be used advantageously. QUOTES INCLUDED IN THE DESCRIPTION

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

[0000] WO 2018 / 199757A2

[0160] WO 2020 / 085911A2

[0160] WO 2021 / 080431A1

[0160] WO 2021 / 249945A1

[0160]

Claims

[1] Bicycle gearbox, comprising: an axle, such as a wheel axle or a countershaft in a crank mechanism, which is configured to be fixed in a non-rotatable manner; at least one sun wheel, which is mounted rotatably around the axis; at least one coupling mechanism configured to selectively prevent rotation of the at least one sun gear in a first direction of rotation around the axis in a first mode and to selectively prevent rotation of the at least one sun gear in an opposite second direction of rotation around the axis in a second mode. [2] Bicycle transmission according to claim 1, wherein the at least one clutch mechanism is configured to allow the sun gear to rotate freely about the axis in at least one or both directions of rotation in a third mode. [3] Bicycle transmission according to claim 1 or 2, wherein the at least one clutch mechanism is configured to be actively electronically actuated in order to select the respective mode of the clutch mechanism. [4] Bicycle transmission according to claim 1, 2 or 3, wherein the at least one sun gear comprises at least two or at least three sun gears rotatably mounted about the axis, and the at least one clutch mechanism comprises a respective clutch mechanism assigned to each of the sun gears for selecting at least the first and the second mode. [5] Bicycle transmission according to claim 4, 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 a support. [6] Bicycle transmission according to claim 5, comprising a ring gear which is toothed with one of the planets of the stepped planetary gears. [7] Bicycle transmission according to one of claims 1-6, wherein an input of the transmission can be connected either to the ring gear or to the carrier of the planetary gear set. [8] Bicycle gearbox according to claim 7, wherein the input of the gearbox is connected to the ring gear via a freewheel clutch or a freewheel bearing. [9] Bicycle transmission according to claim 7 or 8, wherein the input of the transmission is connected to the carrier via a first actuated clutch mechanism. [10] Bicycle transmission according to one of claims 1-9, wherein an output of the transmission can be connected either to the ring gear or to the carrier of the planetary gear set. [11] Bicycle gearbox according to claim 10, wherein the carrier is connected to the output of the gearbox via a freewheel clutch or a freewheel bearing. [12] Bicycle transmission according to claim 10 or 11, wherein the ring gear is connected to the output of the transmission via a second actuable clutch mechanism. [13] Bicycle transmission according to one of claims 1-12, wherein the or each clutch mechanism comprises a first pawl and a second pawl configured to be actuated by a camshaft such that the first pawl engages selectively with the respective sun gear in the first mode and the second pawl engages selectively with the respective sun gear in the second mode. [14] Bicycle transmission according to one of claims 1-13, wherein the at least one of the clutch mechanisms comprises a passive freewheel clutch or a passive freewheel bearing to generate a first or a second mode. [15] Bicycle transmission according to claim 13, or 14 if dependent on claim 13, wherein the camshaft is mounted inside the axle to actuate the at least one clutch mechanism. [16] Bicycle transmission according to claim 15 when dependent on claim 4, wherein the camshaft mounted inside the axle is configured to actuate the respective clutch mechanisms of the at least one clutch mechanism. [17] Bicycle transmission according to claim 16 when dependent on claims 9 and 12, wherein the camshaft mounted inside the axle is configured to actuate the first and the second actuated clutch mechanism. [18] Bicycle transmission according to one of claims 1-17, wherein the at least one clutch mechanism is designed such that it can separate from a sun gear subjected to torque in at least one direction. [19] Bicycle transmission according to claim 18 when dependent on claim 13, wherein the pawls are designed such that they separate under torque load on the sun gear and the camshaft is configured to make it possible to prevent separation. [20] Bicycle transmission according to one of claims 1-19, wherein a rolling bearing is provided between the camshaft and the pawls. [21] Bicycle transmission according to one of claims 1-20, wherein at least one rolling bearing is provided between the camshaft and the axle. [22] Bicycle gearbox, comprising: an axle, such as a wheel axle or a countershaft in a crank mechanism, which is configured to be fixed non-rotatably to a bicycle frame; at least one sun wheel, which is mounted rotatably around the axis; at least one coupling mechanism for selectively preventing rotation of the at least one sun gear in at least one direction of rotation around the axis; and a camshaft mounted inside the axle to actuate the at least one clutch mechanism. [23] Bicycle transmission according to claim 22, further comprising an electromechanical actuator, such as an electric motor, on or in the axle and configured to move the camshaft, such as to rotate it. [24] Bicycle gearbox, comprising: an axis; a coupling mechanism that surrounds the axle and / or is located within it; and an electromechanical actuator, such as an electric motor, in the axis and configured to actuate the clutch mechanism. [25] Bicycle transmission according to claim 24, further comprising a camshaft mounted inside the axle such that it is moved by the electromechanical actuator, the camshaft being configured to actuate the clutch mechanism. [26] Bicycle gearbox according to claim 24 or 25, wherein the axle is configured to be non-rotatably fixed to a frame of the bicycle, the gearbox further comprising: at least one sun gear rotatably mounted about the axis, wherein the coupling mechanism is configured to selectively prevent rotation of the at least one sun gear about the axis in at least one direction of rotation. [27] Bicycle gearbox, comprising: an axle, such as a wheel axle or a countershaft in a crank mechanism, which is configured to be fixed non-rotatably to a bicycle frame; a multitude of sun wheels, mounted rotatably around the axis; a plurality of coupling mechanisms for selectively preventing rotation of one or more of the plurality of sun gears in at least one direction of rotation around the axis; and a camshaft that incorporates a single-notch profile for actuating the multitude of clutch mechanisms. [28] Bicycle transmission according to claim 27, wherein the camshaft is mounted inside the axle. [29] Bicycle transmission according to claim 27 or 28, further comprising an electromechanical actuator, such as an electric motor, on or in the axle and configured to move the camshaft, such as to rotate it. [30] Bicycle transmission according to one of claims 22-29, wherein the camshaft comprises a single notch profile for actuating the plurality of clutch mechanisms. [31] Bicycle transmission according to claim 22 or 23 or one of claims 26-30, 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 with or is disengaged from the respective sun gear. [32] Bicycle transmission according to claim 31, wherein the at least one pawl is configured to move in a radial direction relative to the axis. [33] Bicycle transmission according to claim 22 or 23 or one of claims 25-32, wherein each clutch mechanism has a bushing associated with it, and wherein the camshaft comprises one or more grooves for axially moving the selector bushing(s). [34] Bicycle transmission according to claim 23, 24, 25 or 26 or one of claims 29-33 when dependent on claim 23, 24, 25 or 26, comprising an elastic element, such as a conformal mechanism, connecting the camshaft to the electromechanical actuator. [35] Bicycle gearbox according to claim 34, wherein the elastic element is prestressed in two opposite directions. [36] Bicycle transmission according to one of claims 1-35, comprising an electric drive for driving or assisting the driving of the bicycle, wherein the electric drive is mounted concentrically inside or outside the axle or is mounted on another axle, such as parallel to the axle. [37] Bicycle transmission according to claim 36, wherein the electric drive comprises an electric motor and optionally a planetary gear set. [38] Bicycle transmission according to one of claims 1-37, wherein the camshaft or the electric drive comprises a rotation sensor and / or a position sensor. [39] Bicycle transmission according to one of claims 1-38, further comprising control electronics for controlling the electromechanical actuator, wherein optionally the control electronics are mounted distal to a drive-side or non-drive-side hub bearing. [40] Bicycle transmission, as according to one of claims 1-39, comprising: a hub housing for connection to a wheel of a bicycle; a wheel axle; a driver part for connection with one or more sprockets, wherein the driver part is mounted on the wheel axle via a first bearing and wherein the hub housing is mounted on the wheel axle via a second bearing and on the driver part via a third bearing; a transmission system that provides a variety of selectable different gear ratios between the rider and the hub housing, with the transmission system being positioned between the second and third bearings; an electromechanical actuator for operating a gear change from one transmission ratio to another; Control electronics for controlling the electromechanical actuator; the control electronics are positioned behind the second bearing when viewed from the perspective of the transmission system. [41] Bicycle transmission, as according to one of claims 1-39, comprising: a hub housing for connection to a wheel of a bicycle; a wheel axle; a driver part for connection with one or more gear rings, wherein the driver part is mounted on the wheel axle via a first bearing and wherein the hub housing is mounted on the wheel axle via a second bearing and on the driver part via a third bearing, wherein the hub housing encloses a first cavity between the second bearing and the third bearing; a transmission system that provides a variety of selectable different gear ratios between the rider and the hub housing, wherein the transmission system is positioned in the first cavity; an electromechanical actuator for operating a gear change from one transmission ratio to another; Control electronics for controlling the electromechanical actuator; the control electronics are positioned outside the first cavity. [42] Bicycle transmission according to claim 40 or 41, wherein the hub housing extends beyond the second bearing when viewed from the transmission system and encloses the control electronics. [43] Bicycle transmission according to one of claims 39-42, wherein the control electronics are e.g. immobilely mounted on the axle, such as concentrically on the axle. [44] Bicycle transmission according to one of claims 39-43, wherein the control electronics comprise at least one of a generator, a battery, a circuit board, a wireless receiver / transmitter, an antenna, an LED, a charging plug, a connecting element or a microchip. [45] Bicycle gearbox according to one of claims 39-44, wherein the control electronics are mounted inside, behind or connected with a plastic housing. [46] Bicycle transmission according to one of claims 39-45, wherein the hub housing comprises an inner hub housing that encloses the axle and an outer hub housing configured for connection, e.g., with a rim of a wheel, e.g., via spokes, wherein the control electronics are positioned so that they are replaceable after the inner hub housing has been removed from the outer hub housing. [47] Bicycle gearbox comprising the bicycle gearbox according to any one of claims 1-46. [48] ​​Bicycle crank gear comprising the bicycle gear according to one of claims 1-39 or 43-46. [49] Bicycle, human-powered vehicle or light electric vehicle comprising the bicycle gear hub according to claim 47 and / or the bicycle crank gear according to claim 48.

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