Bicycle derailleur

Abstract

A bicycle derailleur includes a derailleur input and a derailleur output each associated with a first axis and a second axis offset from the first axis. A bicycle derailleur includes a parallel derailleur providing parallel transmission stages between a parallel derailleur input associated with a first axis and a parallel derailleur output associated with a second axis. The bicycle derailleur also includes a planetary derailleur associated with the second axis.

Description

Technical Field

[0001] The invention relates to a transmission for a bicycle. Background Art

[0002] Typically, a bicycle includes a transmission that is selectively operable according to a plurality of gear ratios. Bicycle hub transmissions are known, in which a shifting mechanism is housed by a hub of a driven wheel of the bicycle. Bicycle crank transmissions are also known, in which a shifting mechanism is housed by a housing at or near the crank of the bicycle. Some bicycles may include an electric propulsion motor. The output torque of the electric propulsion motor, which may be relatively significant, may be transmitted through the bicycle transmission in certain circumstances, thereby increasing the overall load on the bicycle transmission. Summary of the invention

[0003] The overall object is to provide a durable and mechanically efficient bicycle transmission which is lightweight and can be produced at minimal cost. A further object is to provide a bicycle transmission which can be shifted under load, preferably in an energy efficient manner.

[0004] According to one aspect, a bicycle transmission is provided, comprising a transmission input associated with a first axis and a transmission output associated with a second axis offset from the first axis. The bicycle transmission comprises a parallel transmission providing parallel transmission stages between the parallel transmission input associated with the first axis and the parallel transmission output associated with the second axis. The bicycle transmission also comprises a planetary transmission. The planetary transmission provides a planetary transmission stage between the planetary transmission input associated with the second axis and the planetary transmission output associated with the second axis, wherein the planetary transmission is arranged so that the planetary transmission stage selectively has one of a plurality of different transmission ratios. The bicycle transmission comprises a clutch mechanism. The clutch mechanism is arranged to selectively clutch one or more rotating members of the planetary transmission to a fixed portion for transmitting torque through the planetary transmission according to one of a plurality of different transmission ratios. By having a planetary transmission associated with the second axis in the transmission path after the parallel transmission, the mechanical load on the planetary transmission can be minimized. This can improve the durability and overall efficiency of the bicycle transmission. In addition, by having the offset first and second axes, it is convenient to shift gears using the planetary transmission through the clutch mechanism.

[0005] Optionally, the first axis does not have a transmission output associated therewith. Specifically, the first axis does not have a gear transmission output associated therewith. Thus, the first axis may be associated only with a transmission input, such as a parallel transmission input, for providing parallel transmission steps for the second axis. Thus, the bicycle transmission may be without a transmission, such as a planetary transmission, for providing transmission steps from the input associated with the first axis to the output associated with the first axis.

[0006] Optionally, the bicycle transmission has no additional parallel transmission. Thus, the planetary transmission may not include another parallel transmission that provides another parallel transmission stage between a parallel transmission input associated with the second axis and a parallel transmission output associated with the first axis. Thus, the bicycle transmission may receive a torque input about the first axis, transfer the torque from the first axis to the second axis through the parallel transmission stage, and output the transferred torque about the second axis to a driven element, such as a sprocket.

[0007] Alternatively, the bicycle transmission may include a continuously variable transmission. If the bicycle transmission includes a continuously variable transmission, it is associated with the second axis and is arranged in series with the parallel transmission. If the bicycle transmission includes both a planetary transmission and a continuously variable transmission, the planetary transmission and the continuously variable transmission may be arranged in series with each other. Advantageously, the continuously variable transmission may be arranged at the input side of the planetary transmission, i.e. in the transmission path between the parallel transmission and the planetary transmission.

[0008] A bicycle transmission may include a first axle extending along a first axis. The bicycle transmission may include a second axle extending along a second axis. Thus, the second axle may be offset from the first axle. The first axle may be considered a main axle or an input axle of the bicycle transmission. The second axle may be considered an output axle, a lay axle, or a secondary axle of the bicycle transmission. In an example, the second axle may, for example, remain fixed relative to a transmission housing. For example, the second axle may form a fixed portion. The first axle may, for example, be a rotatable axle or a non-rotatable axle relative to the transmission housing.

[0009] Optionally, the planetary transmission has three rotating members, wherein the clutch mechanism is arranged to clutch one of the rotating members to the fixed part. Thus, one of the rotating members can be selectively fixedly mounted to the fixed part in a non-rotatable manner. The three rotating members may include a ring gear, a planet carrier carrying one or more planetary gears, and a sun gear. One of these rotating members may be clutched to the fixed part by a clutch mechanism. For example, the fixed part may be a transmission housing of a bicycle transmission or a fixed axle, such as a second axle, of a bicycle transmission.

[0010] Optionally, the planetary gear set of the planetary transmission is a sunless planetary gear set having only one planet carrier carrying one or more planetary gears and two ring gears. Optionally, only one planet carrier can be selectively connected to the fixed part in a clutch mechanism in a clutched manner.

[0011] Optionally, the planetary gear set of the planetary transmission is a ringless planetary gear set having only one planet carrier carrying one or more planetary gears and two sun gears. Optionally, only one planet carrier can be selectively connected to the fixed part in a clutch mechanism in a clutched manner.

[0012] Optionally, one or more planetary gears of the planetary transmission are stepped planetary gears comprising a large-radius gear portion and a small-radius gear portion which are mounted rotationally fixed to each other.

[0013] Optionally, each planetary radius cooperates with a corresponding sun gear or ring gear, and wherein the clutch mechanism is arranged to selectively clutch one of the cooperating sun gear or ring gear to the fixed part for selectively transmitting torque according to one of a plurality of gear ratios.

[0014] Optionally, the planetary transmission comprises a plurality of sun gears, and wherein one or more of the planet gears are stepped planet gears, each stepped planet gear comprising a plurality of different planetary radii, wherein each sun gear cooperates with the stepped planet gear at a corresponding radius of the plurality of different radii.

[0015] Optionally, the stepped planetary gear comprises at least three different planetary radii, such as at least four different planetary radii.

[0016] Optionally, the clutch mechanism comprises one or more actuatable clutches.

[0017] Optionally, each actuatable clutch is associated with a respective sun gear and is arranged to selectively couple and / or disconnect the respective sun gear with the stationary part.

[0018] Optionally, the stepped planetary gear comprises two, for example identical, small radius gear parts, which are rotationally fixedly mounted to the large radius gear part on opposite sides of the large radius gear part. Thus, a symmetrical planetary gear can be obtained, which can provide an effective support for the stepped planetary gear. For example, the large radius gear part can mesh with the ring gear, so that the torque can be transmitted from the planet carrier to the ring gear via the large radius planet gear part, wherein, for example, two small radius planet gear parts on opposite sides of the large radius planet gear part mesh with corresponding sun gear parts of a single diameter sun gear. Thus, a strong and compact construction can be obtained.

[0019] Optionally, the clutch mechanism comprises a rotatable camshaft extending along the second axis and is arranged for selectively actuating the one or more actuatable clutches by rotation of the rotatable camshaft about the second axis relative to the stationary part.

[0020] Optionally, one or more actuable clutches are shape-enclosed clutches configured to transmit torque in at least one rotational direction. Typically, any actuable clutch described herein may be a shape-enclosed clutch configured to transmit torque in at least one rotational direction.

[0021] Optionally, each actuatable clutch is configured for coupling and disconnection under load.Generally, any actuatable clutch described herein may be configured for coupling and disconnection under load.

[0022] Alternatively, each actuatable clutch may be independently actuatable.

[0023] Optionally, one or more actuatable clutches are identical to each other. Thus, a bicycle may include a single type of actuatable clutch.

[0024] Optionally, the planetary transmission is selectively operable according to a single gear ratio. Optionally, the planetary transmission is selectively operable according to a speed increasing gear ratio. Optionally, the planetary transmission is selectively operable according to a speed decreasing gear ratio. Optionally, the speed increasing gear ratio and the speed decreasing gear ratio of the planetary transmission are reciprocal of each other. Any actuatable clutch described herein, optionally, may be an actuatable clutch having a clutch input and a clutch output, the actuatable clutch comprising:

[0025] a first unit connectable to the clutch input, comprising a gripping member having at least one first abutment surface;

[0026] a second unit connectable to the clutch output, comprising at least one second abutment surface arranged to selectively engage the first abutment surface, the first abutment surface and the second abutment surface being adapted to each other to allow disengagement under load, preferably in both directions;

[0027] A third unit comprising at least one retaining member, the third unit being arranged to be selectively in a first mode or a second mode relative to the second unit, wherein the at least one retaining member in the first mode locks the at least one second abutment surface for coupling the second unit to the first unit rotationally, e.g. in both directions, and in the second mode releases the at least one second abutment surface for disconnecting the second unit from the first unit. A bicycle transmission comprising such an actuatable clutch (or these actuatable clutches) can be manufactured in a small form factor suitable for integration in a two-wheeled bicycle.

[0028] Optionally, the actuatable clutch comprises a bearing, such as a rolling contact bearing or a sliding contact bearing between the at least one retaining member and the at least one grasping member.

[0029] Optionally, the actuatable clutch comprises an actuator for moving the third unit from the first position to the second position or from the second position to the first position relative to the second rotatable unit.

[0030] Optionally, the third unit comprises at least one actuation member arranged to move the third unit from the first position to the second position or from the second position to the first position relative to the second rotatable unit.

[0031] Optionally, the clutch includes a first rotatable unit connectable to an input portion; a second rotatable unit connectable to an output portion; a third rotatable unit arranged to rotate together with the second rotatable unit, the third rotatable unit being arranged to be selectively in a first rotational position or a second rotational position relative to the second rotatable unit, wherein the actuatable clutch is arranged to selectively rotationally couple the second rotatable unit to the first rotatable unit in the first rotational position, and to disconnect the second rotatable unit from the first rotatable unit in the second rotational position; wherein the actuatable clutch is arranged to temporarily change the rotational speed of the third rotatable unit relative to the second rotatable unit so as to rotate from the first position to the second position, or from the second position to the first position.

[0032] Optionally, any one or more of the first unit, the second unit and the third unit of the actuatable clutch are associated with the second axis. For example, the first unit, the second unit and the third unit of the actuatable clutch may rotate around the second axis.

[0033] Optionally, any actuatable clutch described herein may be similar or identical to the clutch described in WO2018 / 199757A2, WO2020 / 085911A2 or WO2021 / 080431A1, the contents of which are incorporated herein in their entirety.

[0034] Optionally, the parallel transmission stage is formed by a mating gear pair having a primary gear rotatable about a first axis and a secondary gear rotatable about a second axis.

[0035] Optionally, the primary gear and the secondary gear of the mating gear pair cooperate with each other in a meshing manner, or wherein the primary gear and the secondary gear of the mating gear pair cooperate with each other in a non-meshing manner, for example by means of corresponding endless drive members, such as a chain or a belt. Optionally, the parallel transmission is a non-shiftable transmission, which can be operated according to a single fixed gear ratio.

[0036] Optionally, the parallel transmission is arranged so that the parallel transmission stage selectively has one of a plurality of different parallel transmission ratios. For example, the parallel transmission may include a plurality of mating gear pairs, wherein torque is selectively transmitted from or through any one of the mating gear pairs.

[0037] Optionally, the parallel transmission comprises an actuatable clutch for shifting the parallel transmission from one of the plurality of parallel gear ratios to another and / or vice versa.

[0038] Optionally, an actuatable clutch for actuating the parallel transmission is associated with the second axis. For example, a clutch member of the actuatable clutch may rotate around the second axis, or may be coupled or coupleable to the second axle.

[0039] Optionally, each actuatable clutch thereat is associated with a second axis.

[0040] Optionally, the parallel transmission stage is selectively formed by a first mating gear pair arranged in a first transmission path or a second mating gear pair arranged in a second transmission path parallel to the first transmission path, wherein each of the first mating gear pair and the second mating gear pair has a main gear rotatable about a first axis and a secondary gear rotatable about a second axis, and the first actuable clutch is arranged to transfer torque from the parallel transmission input to the parallel transmission output through either the first transmission path or the second transmission path.

[0041] Optionally, the primary gear and the secondary gear of each first and / or second mating gear pair cooperate with each other in a meshing manner. Alternatively and optionally, the primary gear and the secondary gear of each first and / or second mating gear pair cooperate with each other in a non-meshing manner, such as via a corresponding endless drive member, such as a chain or a belt.

[0042] Optionally, the bicycle transmission includes a continuously variable transmission (CVT) providing CVT gear steps between a CVT transmission input associated with the second axis and a CVT transmission output associated with the second axis.

[0043] Optionally, a continuously variable transmission (CVT) includes:

[0044] A first drive element, which is rotatable about a first CVT axis; a second drive element, which is rotatable about a second CVT axis, the first drive element being movable relative to the second drive element in a direction transverse to the first CVT axis and the second CVT axis; a coupling element, which is disposed at a constant first radius from the first CVT axis and a variable second radius from the second CVT axis, or at a constant first radius from the second CVT axis and a variable second radius from the first CVT axis, for transmitting torque between the first drive element and the second drive element. The first drive element and the second drive element are movable relative to each other in a direction transverse to the first CVT axis and the second CVT axis, thereby transmitting torque at different transmission ratios. By changing the relative displacement between the first drive element associated with the first CVT axis and the second drive element associated with the second CVT axis, the variable second radius at which torque is transmitted between the input portion and the second drive element is changed. Therefore, various transmission ratios can be obtained between the first drive element and the second drive element. The CVT can be made into a relatively small form factor, with a relatively small number of components and a small mass.

[0045] Optionally, the coupling element is coupled to the second drive element in a tangential direction and is movable in a radial direction relative to the second drive element, wherein the coupling element is coupled to the first drive element in a radial direction at a first radius from the first CVT axis and is movable in a tangential direction relative to the first drive element, and wherein the coupling element is coupled to the first drive element in a second tangential direction opposite to the first tangential direction. Thus, the coupling element can be maintained at a predetermined radial distance relative to the first CVT axis. The coupling element can, for example, be freely movable in a first tangential direction relative to the first drive element and be coupled to the first drive element in a second tangential direction relative to the first drive element. Thus, the first drive element can drive the coupling element to rotate in the first tangential direction, and the first drive element can freely move in the second tangential direction relative to the coupling element. In addition, the coupling element can drive the first drive element to rotate in the second tangential direction, and the coupling element can freely move in the first tangential direction relative to the first drive element.

[0046] Optionally, the second CVT axis coincides with the second axis, and wherein a drive element thereof is movable relative to the second drive element to an eccentric position offset from the second axis.

[0047] Optionally, the first drive element is pivotally movable about a pivot axis extending parallel to the first CVT axis to pivotally move relative to the second drive element in a direction transverse to the first CVT axis.

[0048] Optionally, the first drive element comprises a first concentric guide extending concentrically around the first CVT axis, wherein the first concentric guide is arranged to guide movement of the coupling element in the first tangential direction. The first concentric guide may for example be a slot provided in the first drive element, the slot extending concentrically around the first CVT axis.

[0049] Optionally, the first concentric guide and the coupling element form or include a one-way coupling for allowing movement of the coupling element relative to the first concentric guide in a first tangential direction and for preventing movement of the coupling element relative to the first concentric guide in a second tangential direction. For example, the one-way coupling may be a wedge or ratchet coupling. Each coupling element may, for example, include a one-way unit arranged to wedge between the inner and outer tracks of the first concentric guide when driven in the second tangential direction.

[0050] Optionally, each coupling element comprises a wedging body which can be tilted about the tilting axis between a neutral position in which the coupling element is allowed to move freely relative to the first concentric guide and a wedging position in which the wedging body is wedgingly engaged with the first concentric guide. For example, the wedging body can be wedged between two tracks of the first concentric guide, for example between the inner track and the outer track. It will be understood that the neutral position and the wedging position can differ only slightly, for example by a few micrometers at the extreme point. In order to assume the neutral position, it is sufficient that the wedging body is no longer wedgingly engaged with the first concentric guide.

[0051] Optionally, each coupling element comprises at least one roller for initiating the tilting of the wedging body from the neutral position to the wedging position.

[0052] Optionally, the first end of the wedge body is provided with a converging wedge recess for cooperating with the first roller, and the second end of the wedge body opposite to the first end is provided with a diverging wedge recess for cooperating with the second roller. Here, convergence and divergence are defined as being observed from a direction away from the center of the wedge body. Relative to the flywheel direction of the wedge body, the converging wedge recess may be arranged at the front end of the wedge body, and the diverging recess may be arranged at the tail end of the wedge body. The first roller may, for example, be arranged between the inner track of the first concentric guide and the converging wedging surface of the converging wedge recess. The second roller may, for example, be arranged between the outer track of the first concentric guide and the diverging wedging surface of the diverging wedge recess. Optionally, the first and / or second rollers are biased in the wedging direction, for example, by a spring, for example, by elastic bias. The first roller and / or the second roller may be biased toward the converging side of the wedge recess. The advantage provided by this is that the wedge body is biased in the wedging state and can be released by movement in the flywheel direction.

[0053] Optionally, the second drive element comprises a first radial guide which extends radially at least relative to the second CVT axis, i.e. has a radial component. The first radial guide is arranged for guiding the movement of the coupling element in a radial direction and for transmitting torque in a tangential direction. The first radial guide may comprise a radially extending groove in the body of the second drive element.

[0054] Optionally, each coupling element comprises a guide wheel for running along the first radial guide.

[0055] Optionally, the coupling element is movably connected to the second drive element, such as hingedly, to allow radial movement of the coupling element relative to the second drive element.

[0056] Optionally, each wedging body is tiltable about the tilting axis between a neutral position in which free movement of the coupling element relative to the first concentric guide is allowed and a wedging position in which each wedging body is wedgingly engaged with the first concentric guide.

[0057] Optionally, each coupling element comprises two wedging bodies. Optionally, each wedging body of the first coupling element can be tilted about a common tilting axis between a neutral position in which the coupling element is allowed to move freely relative to the first concentric guide and a wedging position in which each wedging body is wedgingly engaged with the first concentric guide.

[0058] Alternatively, the guide wheels are rotatable about a common tilting axis, wherein two wedging bodies are arranged on both sides of the guide wheels.

[0059] Optionally, the transmission is arranged to pivot the first drive element about the pivot axis between first and second extreme positions, for example between a concentric position where the first CVT axis coincides with the second CVT axis and an eccentric position where the first CVT axis is offset from the second CVT axis.

[0060] Optionally, the first drive element is pivotable about the pivot axis to a selected position defined in a continuous pivot range between a first extreme position and a second extreme position, for example between a concentric position and an eccentric position, wherein the continuous pivot range is symmetrical relative to a horizontal plane passing through the pivot axis.

[0061] Optionally, the first drive element of the CVT is fixedly mounted to or integrated with the secondary gear of the parallel transmission stage.

[0062] Optionally, the primary and secondary gears of the parallel transmission stage cooperate with each other non-meshingly, such as via an annular drive member.Thereby, movement of the first drive element relative to the second drive element is facilitated.

[0063] Optionally, the continuously variable transmission includes a third drive element rotatable about a third axis parallel to the second axis. The third drive element and the second drive element can move relative to each other in a direction transverse to the third axis and the second axis. The CVT may include a second coupling element arranged at a third constant radius from the third axis and a fourth variable radius from the second axis for transmitting torque between the third drive element and the second drive element. Thus, torque can be transmitted from the first drive element to the second drive element according to the first CVT transmission ratio, and from the second drive element to the third drive element according to the second CVT transmission ratio. The first CVT transmission ratio and the second CVT transmission ratio are particularly arranged in series, so that the number of CVT unit transmission ratios obtainable using the CVT unit can be increased. Optionally, the constant first radius corresponds to the constant third radius, that is, the constant first radius and the constant third radius are equal. Optionally, the variable second radius corresponds to the variable fourth radius, that is, the variable second radius and the variable fourth radius are equal.

[0064] Optionally, the second coupling element is coupled to the second drive element in a tangential direction and is movable relative to the second drive element in a radial direction. Thus, the second coupling element can move radially relative to the second axis while remaining tangentially coupled to the third drive element. Optionally, the second coupling element is coupled to the third drive element in a radial direction at a constant third radius and is movable relative to the third drive element in a fourth tangential direction. Optionally, the second coupling element can be coupled to the third drive element in a third tangential direction opposite to the fourth tangential direction. Optionally, the third tangential direction corresponds to the first tangential direction, i.e., the third tangential direction and the first tangential direction are the same. Optionally, the fourth tangential direction corresponds to the second tangential direction, i.e., the fourth tangential direction and the second tangential direction are the same. Thus, the second coupling element can be coupled to the third drive element in a radial direction at the third radius and is movable relative to the third drive element in the second tangential direction, and the second coupling element can be coupled to the third drive element in the first tangential direction. Thus, the second coupling element can drive the third drive element to rotate in the first tangential direction, and the second coupling element can freely move relative to the third drive element in the second tangential direction. In addition, the third driving element can drive the second coupling element to rotate in the second tangential direction, and the third driving element can freely move in the first tangential direction relative to the second coupling element.

[0065] Optionally, the third drive element comprises a second concentric guide extending concentrically around the third axis, wherein the second concentric guide is arranged to guide the movement of the second coupling element in the third tangential direction. The second concentric guide may for example be a slot provided in the third drive element, the slot extending concentrically around the third axis.

[0066] Optionally, the second concentric guide and the second coupling element form or include a one-way coupling portion for allowing movement of the second coupling element relative to the second concentric guide in a fourth tangential direction and for preventing movement of the second coupling element relative to the second concentric guide in a third tangential direction.

[0067] Optionally, each second coupling element comprises a wedging body which can be tilted about the tilting axis between a neutral position and a wedging position, in which the coupling element is allowed to move freely relative to the first concentric guide, and in which the wedging body is allowed to be wedgedly engaged with the second concentric guide. For example, the wedging body can be wedged between two tracks of the second concentric guide, for example between the inner track and the outer track. It will be understood that the neutral position and the wedging position can differ only slightly, for example by a few micrometers at the extreme point. In order to assume the neutral position, it is sufficient that the wedging body is no longer wedgedly engaged with the first concentric guide.

[0068] Optionally, each second coupling element comprises at least one roller for initiating the tilting of the wedging body from the neutral position to the wedging position.

[0069] Optionally, the first end of the wedge body is provided with a converging wedging recess for cooperating with the first roller, and the second end of the wedge body opposite to the first end is provided with a diverging wedging recess for cooperating with the second roller. Relative to the flywheel direction of the wedge body, the converging wedging recess can be arranged at the front end of the wedge body, and the diverging recess can be arranged at the tail end of the wedge body. The first roller can be arranged, for example, between the inner track of the second concentric guide and the converging wedging surface of the converging wedging recess. The second roller can be arranged, for example, between the outer track of the second concentric guide and the diverging wedging surface of the diverging wedging recess. Optionally, the first and / or second rollers are biased in the wedging direction, for example, by elastic biasing, for example, using a spring. The first roller and / or the second roller can be biased toward the converging side of the wedging recess. The advantage provided by this is that the wedge body is biased in the wedging state and can be released by movement in the flywheel direction.

[0070] Optionally, the second drive element comprises a second radial guide extending radially relative to the second axis, wherein the second radial guide is arranged for guiding movement of the second coupling element in a radial direction and for transmitting torque in a tangential direction. The second radial guide may comprise a radially extending slot in the body of the second drive element.

[0071] Optionally, each second coupling element comprises a guide wheel for running along the second radial guide.

[0072] Optionally, the second coupling element is movably, such as hingedly, connected to the second drive element to allow radial movement of the second coupling element relative to the second drive element.

[0073] Optionally, each wedging body is tiltable about the tilting axis between a neutral position in which free movement of the coupling element relative to the second concentric guide is allowed and a wedging position in which each wedging body is wedgingly engaged with the second concentric guide.

[0074] Optionally, each second coupling element comprises two wedging bodies. Optionally, each wedging body of the second coupling element can be tilted about a common tilting axis between a neutral position in which the coupling element is allowed to move freely relative to the second concentric guide and a wedging position in which each wedging body is wedgingly engaged with the second concentric guide.

[0075] Alternatively, the guide wheels are rotatable about a common tilting axis, wherein two wedging bodies are arranged on both sides of the guide wheels.

[0076] Optionally, the first axis and the third axis coincide.The first drive element and the third drive element may for example rotate about a common axis.

[0077] Optionally, the second drive element can be pivotally moved about a pivot axis extending parallel to the first axis and the second axis to pivotally move relative to the first drive element in a direction transverse to the first axis and the second axis. Thus, the second drive element can be moved relative to the first drive element about the pivot axis by a rotary drive.

[0078] Optionally, the continuously variable transmission comprises a second transmission wheel, which is concentrically coupled to the second drive element and can rotate together with it around the second axis; and a parallel transmission wheel, which is drivingly connected to the second transmission wheel for transmitting torque between the first transmission wheel and the second transmission wheel, wherein the parallel transmission wheel has a rotation axis that coincides with the pivot axis. The parallel transmission wheel and the second transmission wheel can, for example, be the first gear and the second gear, respectively, wherein the first gear and the second gear mesh to transmit torque. The parallel transmission wheel and the second transmission wheel can also be the first sprocket and the second sprocket, respectively, which are connected via a chain.

[0079] Optionally, the continuously variable transmission comprises an annular drive member, such as a chain or a belt, which drivingly engages the parallel transmission wheel and the second transmission wheel for transmitting torque between the first transmission wheel and the second transmission wheel. Thus, a gearless transmission can be obtained. In addition, for example, when the first drive member is driven to rotate about the first axis, the driving force is transmitted to the second drive element via the first coupling element. This force acts on the second drive element in a substantially opposite direction as a reaction force from the annular drive member. Therefore, at least with respect to the gear drive arrangement, the actuation force for moving the second drive element relative to the first drive element can be reduced.

[0080] Optionally, the continuously variable transmission is arranged to pivot the second drive element between a concentric position where the first axis and the second axis coincide and an eccentric position where the first axis and the second axis are offset, and wherein, if the first drive element drives the second drive element in a driven rotation direction around the second axis, the continuously variable transmission is arranged to pivot the second drive element from the concentric position to the eccentric position in a rotation direction around the pivot axis opposite to the driven rotation direction; and if the second drive element drives the first drive element in a driven rotation direction around the pivot axis, the continuously variable transmission is arranged to pivot the second drive element in the driven rotation direction around the pivot axis from the concentric position to the eccentric position. Therefore, the actuation force for moving the second drive element relative to the first drive element can be minimized.

[0081] Optionally, for example alternatively or additionally, the first drive element may be pivotally movable about a pivot axis extending parallel to the first axis and the second axis to pivotally move relative to the second drive element in a direction transverse to the first axis and the second axis. Thus, the continuously variable transmission may be arranged to pivot the first drive element between a concentric position where the first axis and the second axis coincide and an eccentric position where the first axis and the second axis are offset, and wherein, if the second drive element drives the first drive element in a driven rotation direction around the second axis, the continuously variable transmission is arranged to pivot the first drive element from the concentric position to the eccentric position in a rotation direction around the pivot axis opposite to the driven rotation direction; and if the first drive element drives the second drive element in a driven rotation direction around the first axis, the continuously variable transmission is arranged to pivot the first drive element in the driven rotation direction around the pivot axis from the concentric position to the eccentric position. Thus, the actuation force for moving the first drive element relative to the second drive element can be minimized.

[0082] Optionally, the continuously variable transmission comprises a pivot arm for coupling the parallel transmission wheel to the second transmission wheel and indicating a constant distance between the second axis and the pivot axis, the pivot arm extending between a first end, at which the pivot arm is coupled to the parallel transmission wheel at the pivot axis, and a second end, at which the pivot arm is coupled to the second transmission wheel at the second axis. Because the first transmission wheel is rotationally associated with the pivot axis and the second transmission wheel is rotationally associated with the second axis, the first transmission wheel and the second transmission wheel can remain drivingly engaged while the second transmission wheel is pivoted relative to the parallel transmission wheel together with the second drive member, for example by direct meshing engagement or by an endless drive member such as a belt or chain.

[0083] Optionally, the continuously variable transmission includes a fourth transmission wheel, which is concentrically connected to the second drive element and can rotate together with the second drive element around the second axis; and a third transmission wheel, which is drivingly connected to the fourth transmission wheel for transmitting torque between the third transmission wheel and the fourth transmission wheel, wherein the third transmission wheel has a rotation axis coinciding with the pivot axis.

[0084] Alternatively, the continuously variable transmission may be similar to that disclosed in co-pending patent application PCT / EP1022 / 060920, the entire contents of which are incorporated herein by reference.

[0085] Optionally, the bicycle transmission comprises a transmission housing holding a parallel transmission and a planetary transmission and / or a continuously variable transmission. The housing can seal the components of the bicycle transmission from the surrounding environment. For example, the housing defines a sealed cavity, in which the parallel transmission and the planetary transmission, and optionally the continuously variable transmission, are arranged.

[0086] Optionally, the bicycle transmission comprises an electric propulsion motor arranged to drive the parallel transmission input about a first axis. For example, the electric propulsion motor may have a motor output axis coinciding with the first axis. Optionally, the bicycle transmission comprises an electric propulsion motor having a motor output axis coinciding with the second axis.

[0087] Optionally, the electric propulsion motor is configured to output a maximum output power of at most 10 kW, preferably at most 4 kW. For example, the electric propulsion motor may have a rated power of at most 10 kW, preferably at most 4 kW.

[0088] Optionally, the electric propulsion motor is held by the transmission housing.

[0089] Optionally, the bicycle transmission comprises a crank connected to the transmission input for being rotatably driven about a first axis. Thus, the crank can be connected to the first axle, for example, to rotate together with the first axle about the first axis. The chain ring can be connected to the transmission output for being rotatably driven about a second axis. Thus, the chain ring can be rotatably coupled to, for example, a fixed second axle.

[0090] On the other hand, a transmission module for a modular bicycle transmission is provided, comprising: a planetary transmission, which provides a planetary transmission stage between a planetary transmission input part suitable for being associated with a fixed axle and a planetary transmission output part suitable for being associated with the fixed axle, wherein the planetary transmission is arranged to provide the planetary transmission stage to selectively have one of a plurality of different gear ratios; and a clutch mechanism suitable for being associated with the fixed axle, which is arranged to selectively associate one or more components of the planetary transmission with the fixed axle in a clutched manner for transmitting torque through the planetary transmission according to one of a plurality of different gear ratios; wherein the transmission module is suitable for being associated with a fixed hub axle and with a fixed crank axle.

[0091] In one aspect, a modular bicycle transmission system is provided, comprising a hub transmission having a fixed hub axle and a transmission module as described herein, the clutch mechanism being adapted to be associated with the fixed hub axle and being arranged to selectively clutch one or more rotating members of a planetary transmission to the fixed hub axle. Additionally or alternatively, the modular bicycle transmission comprises: a crank transmission having a crank transmission input associated with a first axle and a crank transmission output associated with a fixed second axle offset from the first axle; a parallel transmission providing parallel transmission stages between the parallel transmission input associated with the first axle and the parallel transmission output associated with the fixed second axle; and a transmission module according to claim 23, wherein the clutch mechanism is arranged to selectively clutch one or more rotating members of the planetary transmission to the fixed crank axle. The hub axle and the crank axle are similar to each other, for example having the same diameter, for allowing the transmission module to mate with the hub axle and the crank axle.

[0092] Another aspect provides a method of producing a bicycle crank transmission, comprising: providing: a crank transmission including a crank transmission input associated with a first axle and a crank transmission output associated with a fixed second axle offset from the first axle; a parallel transmission providing a parallel transmission stage between the parallel transmission input associated with the first axle and the parallel transmission output associated with the fixed second axle. The method also includes: providing a bicycle hub transmission, the bicycle hub transmission including: a planetary transmission providing a planetary transmission stage between a planetary transmission input adapted to be associated with the fixed hub axle and a planetary transmission output adapted to be associated with the fixed hub axle, wherein the planetary transmission is arranged to provide the planetary transmission stage to selectively have one of a plurality of different gear ratios; and a clutch mechanism adapted to be associated with the fixed hub axle, arranged to selectively clutch one or more rotating members of the planetary transmission to the fixed hub axle for selectively transmitting torque through the planetary transmission according to one of a plurality of different gear ratios. The method also includes: mounting the planetary transmission and the clutch mechanism of the hub transmission on the fixed second axle.

[0093] In one aspect, a method of producing a bicycle hub transmission is provided, comprising: providing a fixed hub axle and providing a bicycle crank transmission, the bicycle crank transmission comprising: a planetary transmission providing a planetary transmission stage between a planetary transmission input associated with the fixed axle and a planetary transmission output associated with the fixed axle, wherein the planetary transmission is arranged to provide the planetary transmission stage to selectively have one of a plurality of different gear ratios; and a clutch mechanism adapted to be associated with the fixed axle, arranged to selectively clutch one or more rotating members of the planetary transmission to the fixed axle for transmitting torque through the planetary transmission according to one of a plurality of different gear ratios. The method also comprises: mounting the planetary transmission and the clutch mechanism of the crank transmission on the fixed hub axle.

[0094] On the one hand, a bicycle transmission system is provided, comprising: a hub housing arranged to receive a transmission module as described herein; a crank housing arranged to receive a transmission module as described herein; and a transmission module as described herein; wherein the bicycle transmission system is arranged so that the transmission module can be selectively received in the hub housing or the crank housing.

[0095] In one aspect there is provided a hub housing arranged to receive a transmission module as described herein.

[0096] In one aspect there is provided a combination of a hub housing as described herein and a transmission module as described herein.

[0097] In one aspect there is provided a crank housing arranged to receive a transmission module as described herein.

[0098] In one aspect there is provided a crank housing as described herein in combination with a transmission module as described herein.

[0099] Another aspect provides a bicycle comprising a bicycle transmission as described herein. It should be understood that bicycles cover similar human-powered, especially pedaled vehicles, such as tricycles, quadricycles, etc. The bicycle transmission can be implemented as a hub transmission of a bicycle and / or a crank transmission of a bicycle.

[0100] According to one aspect, an electric vehicle is provided, such as a light electric vehicle, for example an electric bicycle or a scooter. The electric vehicle comprises a bicycle transmission as described herein, and an electric propulsion motor having a maximum output power of at most 10 kW, preferably at most 4 kW; the electric propulsion motor is arranged to propel or assist in propulsion of the vehicle, wherein the output power of the propulsion motor is at least partially transmitted through the bicycle transmission.

[0101] It should be understood that any aspects, features and options described herein can be combined. It should be particularly understood that any aspects, features and options described for bicycle transmissions are also applicable to bicycles and electric vehicles, and vice versa. BRIEF DESCRIPTION OF THE DRAWINGS

[0102] Embodiments of the present invention will now be described in detail with reference to the accompanying drawings, in which:

[0103] Figure 1 A bicycle transmission, in particular a crank transmission, is shown;

[0104] Figure 2 A bicycle transmission, in particular a hub transmission, is shown;

[0105] Figure 3A and Figure 3B An actuatable clutch is shown;

[0106] Figure 4 A bicycle is shown. DETAILED DESCRIPTION

[0107] Figure 1 An example of a bicycle transmission 1 having a transmission input I and a transmission output O is shown. The bicycle transmission 1 comprises a parallel transmission 600. The parallel transmission 600 provides parallel transmission stages between a parallel transmission input 601 associated with a first axis A1 and a parallel transmission output 602 associated with a second axis A2. The first axis A1 and the second axis A2 are offset from each other. The bicycle transmission 1 here comprises a first axle 47 extending along the first axis A1. The first axle 47 may comprise a plurality of first axle parts rotatable relative to each other. The bicycle transmission 1 here also comprises a second axle 10 extending along the second axis A2. Therefore, the first axle 47 and the second axle 10 are also offset from each other. Here, the second axle 10 is a fixed axle which is non-rotatably fixedly mounted to a housing 49 of the bicycle transmission 1.

[0108] The parallel transmission 600 can be operated in this example only according to one fixed transmission ratio. It will be appreciated that the parallel transmission 600 can also be operated according to more than one transmission ratio, such as two transmission ratios. Here, the parallel transmission 600 comprises a mating gear pair having a main gear 600A rotatable about a first axis A1 and a secondary gear 600B rotatable about a second axis A2. Here, the main gear 600A of the parallel transmission 600 is mounted to the first axle 47. The first flywheel V1 is associated with the first axis A1 in this example.

[0109] exist Figure 1In the example of , the primary-secondary gear pair 600A, 600B of the parallel transmission 600 meshes with each other through direct meshing engagement. Alternatively, the primary-secondary gear pair 600A, 600B of the parallel transmission 600 may be non-meshingly engaged with each other, for example, via a chain or a belt.

[0110] In this example, the bicycle transmission 1 further comprises a planetary transmission 500 providing a planetary transmission stage between a planetary transmission input 501 and a planetary transmission output 502. The planetary transmission input 501 and the planetary transmission output 502 are associated with the second axis A2. The planetary transmission 500 comprises a planetary gear set having three rotating members, in particular a ring gear, a planet carrier carrying one or more planetary gears, and a sun gear.

[0111] Figure 1 The bicycle transmission system 1 shown has an exemplary planetary gear set 500 including a first planetary gear set 100 and a second planetary gear set 200. Here, each of the first planetary gear set 100 and the second planetary gear set 200 includes three rotating members. The first planetary gear set 100 includes a first sun gear 101, a first planet carrier 102 carrying one or more first planetary gears 103, and a first ring gear 104. The first sun gear 101 and the first ring gear 104 mesh with the one or more first planetary gears 103. The second planetary gear set 200 includes a second sun gear 201, a second planet carrier 202 carrying one or more second planetary gears 203, and a second ring gear 204. The second sun gear 201 and the second ring gear 204 mesh with the one or more second planetary gears 203.

[0112] In this example, the first planet carrier 102 forms a first rotational input member of the first planetary gear set 100, and the first ring gear 104 forms a first rotational output member of the first planetary gear set 100. Here, the first sun gear 101 forms a first further rotational member of the first planetary gear set 100. In this example, the second ring gear 204 forms a second rotational input member of the second planetary gear set 200, and the second planet carrier 202 forms a second rotational output member of the second planetary gear set 200. Here, the second sun gear 201 forms a second further rotational member of the second planetary gear set 200.

[0113] The first rotation input component and the second rotation input component are mounted fixedly to each other so as to rotate together. Here, the first planet carrier 102 and the second ring gear 204 are mounted fixedly to each other so as to rotate together, for example, integrated. The first rotation output component and the second rotation output component are mounted fixedly to each other so as to rotate together. Here, the first ring gear 104 and the second planet carrier 202 are mounted fixedly to each other so as to rotate together, for example, integrated. Figure 1An example is shown in which one or more first planet gears 103 mesh with the second planet carrier 202. In an alternative configuration, one or more second planet gears 203 may mesh with the first planet carrier 102.

[0114] Here, the first sun gear 101 and the second sun gear 201 can be selectively associated with a fixed part in a clutched manner. Here, the fixed part is or includes the axle 10. Alternatively, the fixed part can be or include a housing. It will be understood that the fixed part can be or include other non-rotatable parts of the bicycle. Therefore, here the first sun gear 101 and the second sun gear 201 can be selectively braked.

[0115] The first planetary gear set 100 is arranged to transfer torque according to an overdrive ratio, ie increase the rotational speed from the first planet carrier 102 to the first ring gear 104. The second planetary gear set 200 is arranged to transfer torque according to an underdrive ratio, ie reduce the rotational speed from the second ring gear 204 to the second planet carrier 202.

[0116] The bicycle transmission system 1 includes a clutch mechanism 50, which is here arranged to selectively clutch one of the first sun gear 101 and the second sun gear 201 to the fixed axle 10. Therefore, torque can be selectively transmitted through the first planetary gear set 100 or through the second planetary gear set 200.

[0117] In this example, the clutch mechanism includes a first clutch 11 associated with the first planetary gear set 100. Here, the first clutch 11 is an activated first clutch 11, which is configured to be actuated between a first state and a second state. In its first state, the activated first clutch 11 clutches the first sun gear 101 to the fixed axle 10 in at least one rotational direction. In its second state, the activated first clutch 11 disengages the first sun gear 101 from the fixed axle 10 in at least one rotational direction.

[0118] Here, the clutch mechanism includes a second clutch 12 associated with the second planetary gear set 200. In this example, the second clutch 12 is a passive second clutch 12, in particular a flywheel clutch. The passive second clutch 12 has only one state, and is configured here to clutch the second sun gear 201 to the fixed axle 10 in one relative rotation direction, and to be overtaken in another opposite relative rotation direction. When the first actuable clutch 11 is in its second non-clutched state, the passive second clutch 12 passively clutches the second sun gear 201 to the fixed axle 10 in a clutched manner, and when the first actuable clutch 11 is in its first clutched state, the passive second clutch 12 is overtaken. Therefore, in this example, the transmission system 1 can be selectively operated by actuating the activated first clutch 11 according to the overdrive gear ratio or the subdrive gear ratio. The passive second clutch 12 automatically engages and disengages the clutch association with the second sun gear 201 independently of the state of the first actuable clutch 11. Alternatively, the second clutch 12 may also be an activated second clutch 12, for example similar to the activated first clutch 11. When both the activated first clutch 11 and the activated second clutch 12 are in their second disengaged clutched state, a neutral gear may be provided, wherein no rotational power may be transmitted through the first planetary gear set 100 or the second planetary gear set 200. When both the activated first clutch 11 and the activated second clutch 12 are in their first engaged clutched state, the transmission system 1 may be locked. For example, both situations may be used as anti-theft features.

[0119] exist Figure 1 In the example of the present invention, the planetary gear set 500 further includes a third planetary gear set 300. The third planetary gear set 300 is arranged in series with the first planetary gear set 100 and the second planetary gear set 200. Here, the third planetary gear set 300 is arranged upstream of the first planetary gear set 100 and the second planetary gear set 200. The third planetary gear set 300 is arranged to selectively operate according to a plurality of different transmission ratios, here four different transmission ratios. In particular, the third planetary gear set 300 is arranged to selectively operate according to three overdriven transmission ratios and a unitary transmission ratio. Therefore, the bicycle transmission system 1 here can provide an eight-speed transmission system.

[0120] The third planetary gear set 300 comprises a plurality of, here three, third sun gears 301a, 301b, 301c, a planet carrier 302 carrying one or more stepped third planet gears 303, and a ring gear 304. Each third planet gear 303 comprises a plurality of, here three different radii 303a, 303b, 303c. Each radius 303a, 303b, 303c meshes with a corresponding third sun gear 301a, 301b, 301c. The third ring gear 304 meshes with a single radius 303b of the stepped third planet gear 303. The third planet carrier 302 forms a third rotation input member of the third planetary gear set 300. The third ring gear 304 forms a third rotation output member of the third planetary gear set 300. The third planet carrier 302 can be clutched to the third ring gear 304 in a relative rotation direction by a non-actuable, passive clutch 15, such as a flywheel clutch, for providing a single gear ratio using the third planetary gear set 300. The third ring gear 304 is fixedly mounted for common rotation to the first planet carrier 102 and the second ring gear 204. In this example, the second ring gear 204 and the third ring gear 304 have the same radius. For example, the second ring gear 204 and the third ring gear 304 may be integrated into a single radius ring gear bus.

[0121] The bicycle transmission 1 further comprises a housing 49. The housing 49 holds the parallel transmission 100 and the planetary transmission 500. In addition, the housing 49 can also hold any additional transmissions of the transmission system 1.

[0122] Figure 1 The transmission system 1 in further comprises a generator 50. Here, the generator 50 is arranged to drive the first axle 47 in rotation about the first axis A1. Thus, here the generator 50 drives the input 601 of the parallel transmission 600.

[0123] exist Figure 1 An example is shown in which the transmission system 1 can be used as a crank transmission. Thus, the transmission input I can be coupled to a crank 1017 of a bicycle. The sprocket 1019 can be coupled to the transmission output O. Thus, the housing 49 can be a crank transmission housing.

[0124] Figure 2 Examples of hub transmissions are shown, including Figure 1 The planetary transmission 500 is shown. Here, the housing 49 may be a hub shell 30 that accommodates the planetary transmission 500. The hub shell 30 is coupled to or forms an output O of the transmission system 1. A rear sprocket 31 is coupled to or forms an input I of the transmission system 1. The rear sprocket 31 may engage a chain or a belt that is driven by the rider of the bicycle by means of a crank.

[0125] The actuatable clutches 11, 13a-13c can be actuated using a rotatable camshaft 60. In this example, the camshaft 60 extends through the hollow fixed second axle 10. The camshaft 60 can have one or more cams. The actuatable clutches 11, 13a-13c can be controlled by rotation of the camshaft 60 about the second axis A2, here the hub axis. Figure 2 The hub transmission does not include the parallel transmission 600 , nor the first axle 47 .

[0126] Thus, the planetary transmission 500 and the clutch mechanism may form part of a transmission module that may be used, for example, Figure 1 The crank transmission shown, and Figure 2 The hub transmission shown. The transmission module may be adapted to a standard hub axle, wherein the crank transmission second axle 10 is substantially similar to the standard hub axle for allowing the transmission module to be mounted thereon.

[0127] Figure 3A-3B An example of an actuatable clutch 11 is shown. The clutch of Figure 3 is shown by way of example, and it should be noted that alternative clutches may also be used in the transmission system 1. For example, the actuated clutch may be a clutch as described in co-pending Netherlands application 2034230, which is incorporated herein by reference.

[0128] The exemplary actuatable clutch 11 has an input and an output. Here, the input is connected to the first sun gear 101. Here, the output is connected to the second axle 10. The exemplary clutch 11 can be operated under load. Therefore, the clutch can be coupled or disconnected under load. Figure 3A-3B The clutch in comprises a first clutch unit 2. Here, the first clutch unit 2 forms the clutch output. Here, the first clutch unit 2 is designed as a housing part of a clutch 11. The clutch 11 comprises a second clutch unit 4. Here, the second clutch unit 4 forms the clutch input. The first clutch unit 2 comprises at least one first abutment surface 6. In this example, the first clutch unit 2 comprises a plurality of first abutment surfaces 6 evenly distributed along the circumference of the first clutch unit 2. For the sake of clarity, Figure 3A-3BOnly one first abutment surface 6 is shown. The second clutch unit 4 comprises at least one second abutment surface 8. In these examples, the second clutch unit has only one second abutment surface 8. However, in alternative examples, the first clutch unit 2 may include more than one second abutment surface, such as only two second abutment surfaces, only three second abutment surfaces, only four second abutment surfaces, only five second abutment surfaces or more than five second abutment surfaces. In the example, the second clutch unit 4 comprises three second abutment surfaces 8, which are evenly distributed at 120 degrees from each other along the periphery of the second clutch unit 4. In another example, the second clutch unit 4 comprises two second abutment surfaces 8, which are evenly distributed at 180 degrees from each other along the periphery of the second clutch unit 4. Here, the second abutment surface 8 is formed by a gripping member 4a. Here, the second clutch unit 4 has only one gripping member 4a, but it should be noted that the second clutch unit 4 may include a plurality of gripping members 4a. Here, the gripping member 4a is implemented as a separate part that is hingedly coupled to the body part 4b of the second clutch unit 4. In this example, the second abutment surface 8 is part of the gripping member 4a of the second clutch unit 4. Here, the second abutment surface 8 is formed by the gripping member 4a, which is arranged to selectively engage one of the first abutment surfaces 6. The first abutment surface and the second abutment surface are oriented at an angle relative to the radial direction of the first clutch unit and the second clutch unit, respectively. This enables the first abutment surface to be disengaged from the second abutment surface under load.

[0129] The clutch 11 further comprises a third clutch unit 60. Here, the third clutch unit 60 is formed by a camshaft 60. The third clutch unit 60 comprises at least one retaining member 12. In these examples, the third clutch unit 60 comprises only one retaining member 12, but it should be noted that the third clutch unit 60 comprises more than one retaining member, such as only two retaining members, only three retaining members, only four retaining members or only five retaining members, for example, these retaining members are evenly distributed along the circumference of the third clutch unit 60 at the same angle. The third clutch unit 60 is arranged relative to the second clutch unit 4 in a manner such as Figure 3A The first position shown or Figure 3B It should be noted that in this example, the first position is a first rotational position and the second position is a second, different rotational position.

[0130] In the first position ( Figure 3A), the retention member 12 is rotationally aligned with the gripping member 4a. Therefore, in the first position, the gripping member 4a is forced to pivot to the radially outer position. In the first position, the second abutment surface 8 is positioned to touch or approach the first abutment surface 6. There is a retention member 12 below the gripping member 4a to prevent the second abutment surface 8 from pivoting radially inward to be enough to disengage from the first abutment surface 6. Therefore, the retention member 12 locks the second abutment surface 8 in the first position to engage with the first abutment surface 6. When the second abutment surface is locked and engaged with the first abutment surface 6, the second clutch unit 4 is rotationally coupled to the first clutch unit 2. When a rotational load is applied to the first clutch unit 2 and / or the second clutch unit 4, if there is no retention member 12 to prevent the gripping member 4a from moving radially inward, the second abutment surface 8 will disengage from the first abutment surface 6.

[0131] In the second position ( Figure 3B ), the retention member 12 is positioned rotationally out of alignment with the gripping member 4a. Thus, in the second position, the gripping member 4a is free to pivot to a radially inner position. In this example, the resilient member bias force pivots the gripping member 4a, wherein the second abutment surface 8 is radially inwardly sufficient to disengage from the first abutment surface 6. Thus, the first clutch unit 2 is free to rotate independently of the second clutch unit 4. Thus, in the second position, the second clutch unit 4 is disconnected from the first clutch unit 2.

[0132] Thus, when the first abutment surface 6 and the second abutment surface 8 are adapted to each other so as to allow engagement and disengagement under load, the relative positioning of the second clutch unit 4 and the third clutch unit 60 can selectively lock the second abutment surface 8 in a first position in engagement with the first abutment surface 6, and release the second abutment surface 8 for disengagement from the first abutment surface 6 in a second position. It should be noted that when the first clutch unit 2 is disconnected from the second clutch unit 4, rotating the third clutch unit 60 relative to the second clutch unit 4 from the first position to the second position couples the first clutch unit with the second clutch unit. When the first clutch unit 2 is coupled to the second clutch unit 4, rotating the third clutch unit 60 relative to the second clutch unit 4 from the second position to the first position couples the first clutch unit with the second clutch unit.

[0133] Changing the position of the third clutch unit 60 from the first position to the second position or vice versa relative to the second clutch unit 4 can be performed in a number of different ways. Changing the position of the third clutch unit 60 from the first position to the second position relative to the second clutch unit 4 can be performed by rotating the third clutch unit 60 in a forward direction relative to the second clutch unit 4, and changing the position of the third clutch unit 60 from the second position to the first position relative to the second clutch unit 4 can be performed by rotating the third clutch unit 60 in an opposite, rearward direction relative to the second clutch unit 4. It is also possible to rotate the third clutch unit 60 in the same rotational direction relative to the second clutch unit 4 from the first position to the second position and from the second position to the first position. Alternatively or in addition to the rotation, the third clutch unit 4 can also be translated axially from the first position to the second position and / or vice versa.

[0134] An actuator may be provided to rotate the third clutch unit and / or the second clutch unit from the first position to the second position, and / or from the second position to the first position.

[0135] In some examples, the third clutch unit 60 may be arranged to rotate together with the second clutch unit 4. Thus, changing the position of the third clutch unit 60 relative to the second clutch unit 4 from the first position to the second position or vice versa may be performed by temporarily changing the speed of the third clutch unit relative to the second clutch unit, for example by temporarily accelerating, braking or stopping the second and / or third clutch unit for a rotation from the first position to the second position or from the second position to the first position.

[0136] In this example, an optional bearing 20 is arranged between the second clutch unit 4 and the third clutch unit 60, in particular between the gripping member 4a of the second clutch unit 4 and the retention member 12 of the third clutch unit 60. Here, the bearing is a rolling contact bearing 20, but it will be understood that a sliding contact bearing can be provided in addition or alternatively. Specifically, when the retention member 12 moves the gripping member radially inward and outward, the rolling contact bearing 20 provides rolling contact, for example, rather than sliding contact, between the gripping member 4a and the retention member 12, thereby facilitating the movement of the third clutch unit 60 relative to the second clutch unit 4 between the first position and the second position and reducing wear. When the retention member 12 locks the gripping member 4a to engage with the first clutch unit, the normal force between the gripping member 4a and the retention member 12 is proportional to the load applied to the clutch system, for example, by the rider. The normal force and the friction force associated therewith between the gripping member 4a and the retention member 12 can be reduced by providing a rolling contact bearing 20.

[0137] The rolling contact bearing 20 may include one or more rollers. Figure 1 In the examples of A and 1B, the roller 20a is associated with the gripping member 4a, where the roller 20a is rotatably mounted to the gripping member 4a. Therefore, the roller 20a can be regarded as part of the gripping member 4a. When the third clutch 60 moves to the first position, the roller 20a is rollingly engaged by the retaining member 12 so as to push the gripping member 40 to the radially outer position for engaging the first clutch unit 2. When the third clutch unit 60 moves to the second position, the retaining member 12 rollingly engages the roller 20a for enabling the gripping member 4a to be released from the first clutch unit 2 and returned to the radially inward position. It should be understood that the roller 20a does not have to engage the third clutch unit 60 in the second position. Figure 2 A and Figure 2 In the example of B, the roller 20 a is associated with the third clutch unit 60 , where the roller 20 a is rotatably mounted to the third clutch unit 60 .

[0138] Each sun gear 101, 201, 301, 401 can be connected to a corresponding clutch 11, 12, 13, 14, such as Figure 3A-3B . The corresponding third clutch units 4 of the clutch system can be rotatably coupled to each other, for example integrated into a single camshaft. The integrated camshaft can particularly have a circular cross-section and can be rotatably driven around an eccentric axis. The integrated camshaft can be arranged eccentrically relative to the second clutch unit 4 of the clutch 11-14. The second clutch unit 4 can also be integrated, wherein the corresponding gripping members 4a are arranged angularly staggered relative to each other. Here, each second clutch unit 4 includes only one gripping member, wherein the gripping members of different clutches are angularly spaced from each other. The angular staggered arrangement can be approximately 90 degrees. The first clutch units 2 of different clutches 11-14 can be rotatable relative to each other for allowing relative rotation between the sun gears. Each first clutch unit 2 includes a corresponding first abutment surface. Therefore, the integrated camshaft 60 can be used to selectively associate one of the sun gears 101, 201, 301, 401 with the fixed second axle 10 in a clutched manner.

[0139] Figure 4A bicycle 1000 is shown. The bicycle 1000 includes a frame 1002 having a front fork 1005 and a rear fork 1007, and a front wheel 1011 and a rear wheel 1013 located in the front fork and the rear fork, respectively. The bicycle 1000 also includes a crank 1017 and a front sprocket 1019. The bicycle 1000 includes a transmission system 1, which is implemented as a hub transmission in this example. Alternatively, the transmission system 1 can be implemented as a crank transmission. The bicycle 1000 also includes a rear sprocket 31, wherein a chain 1023 passes through the front sprocket 1019 and the rear sprocket 31.

[0140] In this document, the present invention is described with reference to specific examples of embodiments of the invention. However, it will be apparent that various modifications and changes may be made therein without departing from the spirit of the invention. For purposes of clarity and concise description, features are described herein as being part of the same or separate embodiments, however, alternative embodiments having a combination of all or some of the features described in these separate embodiments are also contemplated.

[0141] However, other modifications, variations and substitutions are possible.Accordingly, the specification, drawings and examples are to be regarded in an illustrative rather than a restrictive sense.

[0142] In the claims, any reference signs placed between parentheses shall not be construed as limiting the claim. The word "comprising" does not exclude the presence of other features or steps than those listed in a claim. Furthermore, the words "a" and "an" shall not be construed as being limited to "only one", but are used to mean "at least one", and do not exclude a plurality. The mere fact that certain measures are recited in mutually different claims does not indicate that a combination of these measures cannot be used to advantage.

Claims

1. A bicycle transmission, comprising: a transmission input associated with a first axis and a transmission output associated with a second axis offset from the first axis; a parallel transmission providing parallel gear stages between a parallel transmission input associated with the first axis and a parallel transmission output associated with the second axis; a planetary transmission providing a planetary transmission stage between a planetary transmission input associated with the second axis and a planetary transmission output associated with the second axis, wherein the planetary transmission is arranged so that the planetary transmission stage selectively has one of a plurality of different gear ratios; A clutch mechanism is arranged to selectively clutch one or more rotating members of the planetary transmission to a fixed portion for selectively transmitting torque through the planetary transmission according to one of the plurality of different gear ratios.

2. The bicycle transmission according to claim 1, characterized in that: The first axis has no transmission output associated therewith.

3. The bicycle transmission according to claim 1 or 2, characterized in that: The planetary transmission has three rotating members and wherein the clutch mechanism is arranged to couple one of the rotating members, in particular the sun gear or the ring gear, to the stationary part in a clutched manner.

4. A bicycle transmission according to any one of the preceding claims, characterized in that The fixed part comprises or is an axle extending non-rotatably along the second axis, or wherein the fixed part comprises or is a transmission housing.

5. A bicycle transmission according to any one of the preceding claims, characterized in that The clutch mechanism includes one or more actuatable clutches.

6. The bicycle transmission according to claim 5, characterized in that: The clutch mechanism comprises a rotatable camshaft extending along the second axis and is arranged for selectively actuating the one or more actuatable clutches by rotation of the rotatable camshaft about the second axis relative to the stationary part.

7. The bicycle transmission according to claim 5 or 6, characterized in that: The one or more actuatable transmissions include or are form-locking clutches configured to transmit torque in at least one rotational direction.

8. The bicycle transmission according to any one of claims 5 to 7, characterized in that: Each of the one or more actuatable clutches is configured to be coupled and decoupled under load.

9. The bicycle transmission according to claim 6, characterized in that: At least one electric actuator is included that is arranged to actuate the rotatable camshaft in rotation about the second axis.

10. A bicycle transmission according to any one of the preceding claims, characterized in that The planetary transmission is selectively operable according to a single gear ratio.

11. A bicycle transmission according to any one of the preceding claims, characterized in that The planetary transmission is selectively operable according to a speed-increasing and / or speed-reducing gear ratio, wherein, optionally, the speed-increasing gear ratio and the speed-reducing gear ratio are reciprocal of each other.

12. A bicycle transmission according to any one of the preceding claims, characterized in that The parallel transmission is a non-shiftable transmission which is arranged to transmit torque according to a single gear ratio.

13. The bicycle transmission according to claim 12, characterized in that: The parallel transmission is arranged to transmit torque with increasing gear ratios as a function of speed.

14. A bicycle transmission according to any one of the preceding claims, characterized in that The parallel transmission stage is formed by a mating gear pair having a main gear rotatable about the first axis and a secondary gear rotatable about the second axis.

15. The bicycle transmission according to claim 14, characterized in that: The primary gear and the secondary gear of the mating gear pair meshingly cooperate with each other, or wherein the primary gear and the secondary gear of the mating gear pair non-meshingly cooperate with each other, such as via respective endless drive members, such as a chain or a belt.

16. A bicycle transmission according to any one of the preceding claims, characterized in that A continuously variable transmission is included that provides a fourth gear stage between a fourth transmission input associated with the second axis and a fourth transmission output associated with the second axis.

17. A bicycle transmission according to any one of the preceding claims, characterized in that A transmission housing is included to hold the parallel transmission and the planetary transmission.

18. A bicycle transmission according to any one of the preceding claims, characterized in that An electric propulsion motor is included that is arranged to drive the parallel transmission input.

19. The bicycle transmission according to claim 18, characterized in that: The electric propulsion motor is designed to deliver a maximum output power of a maximum of 10 kW, preferably a maximum of 4 kW.

20. A bicycle transmission according to claim 18 or 19, when dependent on claim 16, characterized in that The electric propulsion motor is held by the transmission housing.

21. A bicycle transmission according to any one of the preceding claims, when dependent on claim 16, characterized in that A generator is included for generating electrical power, wherein the generator is held by the transmission housing.

22. A bicycle transmission according to any one of the preceding claims, comprising: a crank connected to the transmission input for being rotatably driven about the first axis; and a chain ring connected to the transmission output for being rotatably driven about the first axis.

23. A transmission module for a modular bicycle transmission, comprising: a planetary transmission providing a planetary transmission stage between a planetary transmission input adapted to be associated with a stationary axle and a planetary transmission output adapted to be associated with the stationary axle, wherein the planetary transmission is arranged so that the planetary transmission stage selectively has one of a plurality of different gear ratios; and a clutch mechanism adapted to be associated with the stationary axle and arranged to selectively clutch one or more rotating members of the planetary transmission to the stationary axle for selectively transmitting torque through the planetary transmission according to one of the plurality of different gear ratios; Therein, the transmission module is adapted to be associated with a fixed hub axle and with a fixed crank axle.

24. A bicycle transmission system, comprising: a hub housing arranged to receive a transmission module according to claim 23; a crank housing arranged to receive a transmission module according to claim 23; as well as The transmission module according to claim 23; Therein, the bicycle transmission system is arranged such that the transmission module can be selectively received in the hub housing or the crank housing.

25. A hub housing arranged for receiving a transmission module according to claim 23.

26. A combination having a transmission module according to claim 23 and a hub housing arranged for receiving the transmission module according to claim 23.

27. A crank housing arranged to receive a transmission module according to claim 23.

28. An assembly having a transmission module according to claim 23 and a crank housing arranged for receiving the transmission module according to claim 23.

29. A modular bicycle transmission system comprising: a wheel hub transmission having a fixed hub axle and a transmission module according to claim 23, the clutch mechanism being adapted to be associated with the fixed hub axle and arranged to selectively clutch the one or more rotating members of the planetary transmission to the fixed hub axle; and / or a crank transmission having a crank transmission input associated with a first axle and a crank transmission output associated with a fixed second axle offset from the first axle; a parallel transmission providing parallel gear ratios between a parallel transmission input associated with the first axle and a parallel transmission output associated with the stationary second axle; and a transmission module according to claim 23, wherein the clutch mechanism is arranged to clutch the one or more rotating members of the planetary transmission to the stationary crank axle; Therein, the hub axle and the crank axle are similar to each other, for example having the same diameter, for allowing the transmission module to cooperate with the hub axle and the crank axle.

30. A method for producing a bicycle crank transmission, comprising: Providing a bicycle crank transmission including a crank transmission input associated with a first axle and a crank transmission output associated with a fixed second axle offset from the first axle; A parallel transmission providing parallel gear stages between a parallel transmission input associated with the first axle and a parallel transmission output associated with the stationary second axle, the method comprising: A bicycle hub transmission is provided, the bicycle hub transmission comprising: a planetary transmission providing a planetary transmission stage between a planetary transmission input adapted to be associated with a fixed hub axle and a planetary transmission output adapted to be associated with the fixed hub axle, wherein the planetary transmission is arranged such that the planetary transmission stage selectively has one of a plurality of different gear ratios; and a clutch mechanism adapted to be associated with the fixed hub axle and arranged to selectively clutch one or more rotating members of the planetary transmission to the fixed hub axle for selectively transmitting torque through the planetary transmission according to one of the plurality of different gear ratios; and The planetary transmission and the clutch mechanism of the hub transmission are mounted on the fixed second axle.

31. A method for producing a bicycle hub transmission, comprising: Fixed hub axles are available; A bicycle crank transmission is provided, the bicycle crank transmission comprising: a planetary transmission providing a planetary transmission stage between a planetary transmission input associated with a stationary axle and a planetary transmission output associated with the stationary axle, wherein the planetary transmission is arranged so that the planetary transmission stage selectively has one of a plurality of different gear ratios; and a clutch mechanism adapted to be associated with the stationary axle and arranged to selectively clutch one or more rotating members of the planetary transmission to the stationary axle for selectively transmitting torque through the planetary transmission according to one of the plurality of different gear ratios; and The planetary transmission and the clutch mechanism of the crank transmission are mounted on the fixed hub axle.

32. A bicycle comprising a bicycle transmission according to any one of the preceding claims.

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