JP2011240732A - Power-assisted bicycle having regeneration mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To enable regeneration charge without complicating a device in a power-assisted bicycle of a sensor motor type having an internal change gear.SOLUTION: The power-assisted bicycle includes, at a hub 1 of a drive wheel, a change-speed mechanism 3 composed of a planetary gear mechanism, a one-way clutch 2 for a reverse input, and a change-speed control mechanism 10. The change-speed mechanism 3 has a sun gear 3a, and transmits a drive force to the drive wheel via a sprocket 4. The change-speed control mechanism 10 switches a planetary carrier 3c and the sun gear 3a via a first change-speed one-way clutch 3e in a relatively rotatable manner or a relatively non-rotatable manner, performs change-speed by switching the sun gear 3a in a rotatable manner or a non-rotatable manner around an axle 5 via a second change-speed one-way clutch 3i, and changes the sun gear in speed into a directly-connected state and at least a one-stage high-speed state. Furthermore, related to the reverse input, the reverse input is made to be transmittable by making the sun gear 3a non-rotatable around the axle 5 via the one-way clutch 2 for the reverse input composed of a roller clutch.

Description

  The present invention relates to a battery-assisted bicycle that adds an auxiliary force to a human-powered drive system by an electric motor.

  A battery is mounted as a motor power source for applying an electric assisting force to an electric assisting bicycle that adds an assisting force to the human power drive system by an electric motor. Since it is desirable for this battery to be able to run for a long time with a single charge, a battery-assisted bicycle equipped with a function of charging the battery effectively by utilizing energy during self-running and regenerative power generation during the self-running Has been developed.

  As a battery charging device using regenerative power generation, for example, Patent Literature 1 discloses a technology of a regeneration control device that detects an operation of a brake lever and commands a regeneration operation to the regeneration device (see, for example, Patent Literature 1). ).

When this type of power regeneration function is installed, for example, as shown in Patent Document 2, in the case of a battery-assisted bicycle (hub motor system) in which a motor and a transmission are provided around the axle, the axle and the rotor of the motor are directly connected. Thus, power regeneration can be realized relatively easily (see, for example, Patent Document 2).
However, in the case of this hub motor system, the distance from the motor to the secondary battery tends to be long, and the wiring of the secondary battery tends to be complicated. Further, when the motor is disposed on the front axle, the operability is deteriorated, and when the motor is disposed on the rear side, there is a problem that it is difficult to achieve compatibility with the transmission.

  For this reason, when a power regeneration function is installed, if operability and simplification of the structure are desired, for example, as in Patent Document 3, a manual drive system including a crankshaft and its bearings, and auxiliary power by a motor are provided. It is advantageous to adopt a structure (center motor system) provided with a drive device in which a drive system to be combined with the crankshaft is housed in a single housing, a so-called center motor unit (see, for example, Patent Document 3).

For example, Patent Document 4 discloses a battery-assisted bicycle that is a center motor type and has a power regeneration function.
In this battery-assisted bicycle, a first one-way clutch is provided between the motor output shaft and the drive sprocket, a second one-way clutch is provided between the pedal crankshaft to which the pedal force is input and the drive sprocket, and further for brake operation. Accordingly, by providing direct coupling means for locking the first one-way clutch, power regeneration during braking is realized. The rear hub and the rear sprocket are directly connected so that reverse input torque from the tire can be transmitted to the motor during regeneration.

Similarly, for example, Patent Document 5 discloses a battery-assisted bicycle equipped with a power regeneration function.
In this battery-assisted bicycle, a two-way clutch capable of switching the lock direction in conjunction with the brake operation is provided on the output shaft of the motor in the center motor unit to realize power regeneration during braking.

  That is, at the time of motor assist, by locking the two-way clutch in the forward rotation direction, the output of the motor can be transmitted to the axle, and motor assist becomes possible. In addition, if the two-way clutch lock direction is switched in conjunction with the occupant's brake operation and the two-way clutch is locked in the reverse rotation direction, the reverse input torque (forward rotation direction) from the axle side can be transmitted to the motor. This makes it possible to perform regenerative power generation and brake assist. In this configuration, since the reverse input torque from the axle side needs to be transmitted to the motor side during regeneration, the rear hub and the rear sprocket are directly connected.

JP-A-8-140212 JP 2003-166563 A Japanese Patent Laid-Open No. 10-250673 JP 2001-213383 A JP 2004-268843 A

  As described above, the battery-assisted bicycle can be roughly divided into a center motor system in which the motor is provided around the crankshaft and a hub motor system in which the motor is built in the front hub or the rear hub.

  In the hub motor system, it is necessary to incorporate a reduction gear in addition to the motor into the rear hub, but there is a problem that it is difficult to obtain a high reduction ratio in terms of space and a large torque cannot be obtained. In addition, since heavy objects are arranged at positions away from the center of gravity of the bicycle, there is a problem that maneuverability is poor, and wiring is complicated when the motor and the battery are separated. Furthermore, since the impact from the tire is directly transmitted to the speed reducer and the motor, there is a drawback that failure is likely to occur. For this reason, the center motor system is currently the mainstream.

  In the center motor type drive system, when the power regeneration function is installed, the rear hub and the rear sprocket are directly connected in Patent Document 4 and Patent Document 5 in order to transmit reverse input torque from the wheels to the motor shaft.

In this regard, a general bicycle transmission mechanism is a system in which a multistage sprocket is provided on the same axis of either the crankshaft or the rear axle, or both, and the chain is moved between sprockets by a derailleur (exterior) There is a system (internal transmission) that changes gears by switching between a transmission and a gear provided inside the rear hub. A one-way clutch is usually provided in the internal transmission, and the reverse input from the tire is not transmitted from the rear hub to the rear sprocket.
The exterior transmission has a simple structure and is lightweight, but it causes wear of the sprocket and chain and also causes the chain to come off. On the other hand, internal transmissions are often used for city cycling because they are dustproof and waterproof and maintenance-free. At present, power-assisted bicycles are developed mainly for city cycle bicycles, most of which employ internal transmissions.

However, when the internal transmission is employed as described above, the reverse input from the wheels is not transmitted from the rear hub to the rear sprocket as it is. For this reason, the center motor cannot be rotated and regenerated by reverse input from the wheels.
In order to support reverse input, for example, it is possible to connect the axle to the crankshaft and the axle to the motor shaft with separate power transmission elements, but using two transmission elements is costly in terms of layout. In particular, the product value is greatly reduced.

  Accordingly, an object of the present invention is to enable regenerative charging without complicating the device as much as possible in a center motor type electrically assisted bicycle including an internal transmission.

  In order to solve the above-described problems, the present invention attaches a secondary battery and an auxiliary drive motor to a frame connecting the front wheel and the rear wheel, and applies a pedaling force transmitted from the crankshaft or a driving force based on the output of the motor. In the battery-assisted bicycle having a regenerative mechanism that is capable of transmitting to the drive wheel and that regenerates electric power generated by reverse input from the drive wheel to the output shaft of the motor when the vehicle is not driven forward. A hub provided on the wheel is provided with a speed change mechanism and a reverse input one-way clutch, and the speed change mechanism is constituted by a planetary gear mechanism and has at least one sun gear, and the driving force by the pedal force or the output of the motor Is transmitted to the driving wheel through a sprocket, and the speed change mechanism includes a planetary gear having at least one gear portion engaged with the sun gear, An outer ring gear that engages with the star gear, and a planet carrier that holds the planet gear, and a function of switching the planet carrier and the sun gear to be relatively rotatable or relatively non-rotatable with respect to the driving force. The first speed change one-way clutch, and the second speed change one-way clutch having a function of switching the sun gear relative to the driving force so that the sun gear can be relatively rotated around the axle or not relatively rotatable. A shift control mechanism capable of switching between the one-way clutch for the second gear and the one-way clutch for the second speed change by an external operation, the planetary carrier and the sun gear cannot be rotated relative to the driving force, and the By allowing relative rotation between the sun gear and the axle, the planetary carrier, the planetary gear, and the outer ring teeth are removed from the sprocket. A low-speed state in which the driving force is transmitted to the hub case via the hub, the planetary carrier and the sun gear can be rotated relative to the driving force, and the sun gear and the axle cannot be rotated relative to each other. From the planetary carrier, the planetary gear, and the outer ring gear to at least one stage of high speed that transmits driving force to the hub case, and the reverse input one-way clutch is the sun gear. And a roller clutch provided between the axle and the axle, and has a function of preventing the sun gear from rotating around the axle with respect to the reverse input from the axle. The configuration of a battery-assisted bicycle provided with a hub capable of transmitting the reverse input of the above to the sprocket from the hub case was adopted.

  The roller clutch of the reverse input one-way clutch may be a sprag clutch. That is, the configuration is such that a secondary battery and an auxiliary drive motor are attached to the frame connecting the front wheel and the rear wheel, and the pedaling force transmitted from the crankshaft or the driving force by the output of the motor can be transmitted to the driving wheel, When the forward drive is not driven, in a battery-assisted bicycle equipped with a regenerative mechanism that returns regenerative power generated by reverse input from the drive wheel to the output shaft of the motor to the secondary battery, a shift is made to a hub provided on the drive wheel. A transmission mechanism and a reverse input one-way clutch, wherein the speed change mechanism is constituted by a planetary gear mechanism and has at least one sun gear, and the driving force generated by the stepping force or the output of the motor is applied to the driving wheel through a sprocket. The transmission mechanism has a planetary gear having at least one gear portion that engages with the sun gear, and engages with the planetary gear. A one-way for first speed change comprising a ring gear and a planet carrier for holding the planet gear, and having a function of switching the planet carrier and the sun gear to be relatively rotatable or relatively non-rotatable with respect to a driving force. A clutch, and a second gear-shifting one-way clutch having a function of switching the sun gear relative to the driving force to be rotatable relative to the axle or to be relatively non-rotatable. A shift control mechanism capable of switching the one-way clutch for two speed changes by an external operation, the planetary carrier and the sun gear cannot be rotated relative to the driving force, and the sun gear and the axle By enabling the relative rotation of the hub, the hub case is connected to the sprocket via the planet carrier, the planetary gear, and the outer ring gear. From the sprocket, the low speed state in which the driving force is transmitted, the planetary carrier and the sun gear are rotatable relative to the driving force, and the sun gear and the axle are not relatively rotatable. The planetary carrier, the planetary gear, and the outer ring gear can be shifted to at least one high-speed state that transmits the driving force to the hub case, and the reverse input one-way clutch includes the sun gear and the axle. And has a function of preventing the sun gear from rotating about the axle with respect to the reverse input from the drive wheel, and the reverse input from the drive wheel. A configuration of a battery-assisted bicycle provided with a hub that can transmit the power from the hub case to the sprocket is adopted.

With the above configuration, when driving forward, the driving force is transmitted from the sprocket of the driving wheel to the hub via the speed change mechanism, and the bicycle moves forward. During forward non-drive, the reverse input from the hub of the drive wheel is transmitted to the sprocket via the reverse input one-way clutch, and regenerative power generation is possible by transmitting torque from the sprocket to the motor driven sprocket through the power transmission element. It becomes. The reverse input one-way clutch always idles with respect to the driving force. For this reason, in the battery-assisted bicycle used for the center-motor-type battery-assisted bicycle equipped with the internal transmission, it is possible to realize the transmission of the driving force and the transmission of the reverse input without complicating the device.
In addition, by providing a switchable one-way clutch for shifting between the planetary carrier and the sun gear, a so-called direct connection state can be configured, and the configuration of the apparatus can be simplified while increasing the number of shift stages.

Also, by adopting a roller clutch or sprag clutch as a reverse input one-way clutch, reverse input from the tire during regeneration can be transmitted to the chain with almost no time lag or shock due to engagement. .
In this regard, if a ratchet clutch is used as a one-way clutch for reverse input, the sun gear or the like needs to rotate around an axis until the clutch pawl engages with the clutch cam surface. Since a shock due to engagement occurs, the one-way clutch for reverse input is advantageously a roller clutch or a sprag clutch.

  In this configuration, the planetary gear has a plurality of gear portions, the number of front sun gears is the same as the number of the gear portions, and one sun gear meshes with each gear portion, and the driving force Thus, by selectively disabling any one of the plurality of sun gears relative to the axle, it is possible to adopt a configuration that enables a multi-stage shift in a high speed state. According to this configuration, the number of shift stages in the high speed state can be increased to a plurality of stages such as 2 stages, 3 stages, and the like.

  In each of these configurations, various structures such as a sprag clutch and a roller clutch can be adopted as the one-way clutch for the first shift and the one-way clutch for the second shift, respectively. For example, a ratchet clutch is used as the one-way clutch for the first shift. Can be adopted. Further, when the ratchet clutch is employed as the first shift one-way clutch, the ratchet clutch can be employed as the second shift one-way clutch in any of the configurations other than the ratchet clutch.

In this case, the first speed change one-way clutch may include a speed change one-way clutch pawl provided on the planetary carrier and a speed change clutch cam face provided on the outer surface of the sun gear. .
The second speed change one-way clutch may include a speed change one-way clutch pawl provided on the sun gear and a speed change clutch cam face provided on the outer surface of the axle.

  In this way, the structure of the axle and sun gear can be simplified by providing the one-way clutch pawl of the first shift one-way clutch on the planetary carrier side and the one-way clutch pawl of the second shift one-way clutch on the sun gear side. Can do.

The shift control mechanism includes a shift sleeve having a notch around the axle, the shift sleeve being movable in the axial direction of the axle, and moving the shift sleeve in the axial direction. The notch is moved between the position of the clutch cam surface for shifting the second one-way clutch and the position retracted from the position of the clutch cam surface for shifting the second one-way clutch. It is possible to employ a configuration in which the second shift one-way clutch is switched by the movement.

  Here, if the shift sleeve member covers the shift clutch cam surface of the second shift one-way clutch, the shift one-way clutch pawl does not bite into the cam surface. When the shifting sleeve slides on the cam surface and the notch is positioned between the shifting one-way clutch pawl and the cam surface, the shifting one-way clutch pawl can be engaged with the cam surface.

Further, in the configuration including the gearshift sleeve, the gearshift control mechanism rotates the gearshift sleeve around the axle shaft at one end of the gearshift sleeve so that the first gearshift one-way clutch It is possible to employ a configuration in which a first shift one-way clutch switching member having a convex portion capable of releasing the engagement between the shift one-way clutch pawl and the shift clutch cam surface can be employed.

  That is, when the convex portion of the first speed change one-way clutch switching portion is retracted from one end of the speed change one-way clutch pawl, the gear change one-way clutch pawl is engaged with the gear shift clutch cam surface, When the convex portion of the gear shifts to a position where it comes into contact with one end of the one-way clutch pawl for shifting, the one-way clutch pawl for shifting swings and disengages from the clutch cam surface for shifting. The one-way clutch can be switched. According to this configuration, the shift sleeve having the function of switching the second shift one-way clutch can also be used for switching the first shift one-way clutch.

  For example, here, the shift one-way clutch pawl of the first shift one-way clutch is engaged with the shift clutch cam surface provided on the outer surface of the sun gear when the shift sleeve is not operated, and the planet carrier And the sun gear becomes non-rotatable. At this time, since the cam surface of the second one-way clutch pawl of the second gear shift one-way clutch provided on the inner surface of the sun gear is closed by the gear shift sleeve, the gear shift one-way clutch pawl bites into the cam surface. There is nothing.

  By operating the shifting sleeve in the axial direction from the outside, the shifting clutch provided on the outer surface of the shifting one-way clutch pawl of the first shifting one-way clutch and the sun gear by the first shifting one-way clutch switching member When the engagement with the cam surface is released and the notch of the speed change sleeve is positioned on the speed change one-way clutch pawl, the speed change one-way clutch pawl is engaged with the cam face and the sun gear is fixed to the axle and set. The driving force from the rear sprocket is transmitted to the drive wheels at the increased speed ratio.

Note that the shift sleeve can be moved by an operation unit that is pulled out from the end of the axle along the axle.
Also, in order to synchronize the movement of the operating part in the axial direction and the movement of the shifting sleeve, a lateral hole that penetrates the axle is provided, the pin is inserted, the pin and the shifting sleeve are fixed, and the pin is pushed by the operating part. Thus, the structure may be such that the shift sleeve is moved. At this time, by removing the load from the outside by applying the load in the opposite direction to the operation portion pushing the pin in the axial direction by the elastic member by the elastic member, It can be returned to its original position.

The notch portion of the shift sleeve has a tapered surface at its axial end edge that gradually approaches the outer diameter side toward the outer side in the axial direction, and the taper surface has a taper surface for shifting the second one-way clutch. A configuration in which the one-way clutch pawl abuts can be employed. In this way, when the one-way clutch pawl for shifting bitten on the clutch cam surface comes into contact with the cutout portion, the force for removing the one-way clutch pawl from the cam surface can be increased by the inclined surface of the tapered surface.
Further, a tapered surface can be provided at the circumferential edge of the notch portion of the speed change sleeve. In this way, the one-way clutch pawl moves on the cam surface along the inclined surface of the taper surface during reverse rotation (rotation in the drive direction in the reverse input clutch portion), so smooth rotation is achieved. It becomes possible.

  In the configuration employing a ratchet clutch as the first speed change one-way clutch, a plurality of speed change one-way clutch claws of the first speed change one-way clutch are provided in a circumferential direction. It is possible to adopt a configuration in which at least one other one-way clutch pawl for shifting is set so as not to engage with the shifting clutch cam surface when engaged with the clutch cam surface for shifting. .

  Further, in the configuration employing a ratchet clutch as the second speed change one-way clutch, a plurality of the speed change one way clutch pawls of the second speed change one way clutch are provided in a circumferential direction, Adopting a configuration in which at least one other one-way clutch pawl for shifting is set so as not to engage with the clutch cam surface for shifting when the clutch cam surface for shifting is engaged. Can do.

For example, by shifting the phases of a plurality of shift one-way clutch pawls and a plurality of shift clutch cam surfaces, one shift one-way clutch pawl and the shift clutch cam surface are engaged with each other for another shift. The one-way clutch pawl can be set so as not to engage the clutch clutch surface for shifting.
In this way, the maximum time (rotation angle) until the shifting one-way clutch pawl engages with the shifting clutch cam surface can be shortened.

Further, in each of the first speed change one-way clutch and the second speed change one-way clutch, the speed change clutch cam surface is constituted by unevenness formed along a circumferential direction, and the speed change clutch by the unevenness is provided. The cam surface can be configured to be provided at four or more locations along the circumferential direction.
In this way, the maximum time (rotation angle) until the shifting one-way clutch pawl engages with the shifting clutch cam surface can be further shortened.

In all these configurations, in the center motor unit, the driving force from the motor can be transmitted during the assist between the motor output shaft and the driving force transmitting element, and the driving force transmitting element during the regenerative power generation. The structure provided with the two-way clutch which can transmit the reverse input from can be employ | adopted.
This facilitates switching between assist and regenerative power generation, and is desirable because the resistance of the motor can be disconnected when the pedal is stroked without assist. As this two-way clutch, a roller clutch, a sprag clutch or the like can be employed.

  According to the present invention, regenerative energy can be stored in the secondary battery, and the cruising distance per charge can be greatly extended as compared with the case where regenerative charging is not performed. Moreover, the current battery-assisted bicycle with a regenerative function has a heavy motor arranged in the front or rear hub, but according to the present invention, the motor can be arranged near the crankshaft near the center of gravity. Good maneuverability of the entire bicycle. In addition, since the speed change mechanism is provided, less pedaling force is required at the start, the balance is not easily lost, the assist power can be saved, and the cruising distance is further extended. Since the speed change mechanism is built in the hub, it is highly durable and maintenance-free. Furthermore, a reverse input transmission clutch is provided between the axle and the sun gear, and a shiftable one-way clutch is provided between the planet carrier and the sun gear, so that a so-called direct connection state can be configured. The configuration of the apparatus can be simplified.

Also, by adopting a roller clutch or sprag clutch as a reverse input one-way clutch, reverse input from the tire during regeneration can be transmitted to the chain with almost no time lag or shock due to engagement. .
In this regard, if a ratchet clutch is used as a one-way clutch for reverse input, the sun gear or the like needs to rotate around an axis until the clutch pawl engages with the clutch cam surface. Since a shock due to engagement occurs, the one-way clutch for reverse input is advantageously a roller clutch or a sprag clutch.

Front sectional view showing driving (direct connection / low speed state) of the embodiment 1A is a cross-sectional view taken along the line AA in FIG. 1, FIG. 1B is a cross-sectional view taken along the line BB in FIG. 1, FIG. Figure Front sectional view showing driving (acceleration / transmission second stage) of the embodiment 3A is a cross-sectional view taken along line AA in FIG. 3, FIG. 3B is a cross-sectional view taken along line BB in FIG. 3, FIG. 3C is a cross-sectional view taken along line CC in FIG. Figure Front sectional view showing driving (speed increase / transmission third stage) of the embodiment 5A is a cross-sectional view taken along line AA in FIG. 5, FIG. 5B is a cross-sectional view taken along line BB in FIG. 5, FIG. 5C is a cross-sectional view taken along line CC in FIG. Figure Sectional drawing which shows the effect | action of the one-way clutch switching member for 1st speed changes in embodiment. Overall view of a center motor type battery-assisted bicycle with a secondary battery and auxiliary drive motor (center motor unit) attached to the frame connecting the front and rear wheels

  An embodiment of the present invention will be described with reference to FIGS. The battery-assisted bicycle B of this embodiment has a center in which a secondary battery and an auxiliary drive motor (center motor unit C) are attached to a frame connecting the front wheel and the rear wheel in the vicinity of the center between the front wheel and the rear wheel. It is a motor system.

  FIG. 8 is a side view illustrating an example of the battery-assisted bicycle B. The battery-assisted bicycle B transmits the pedaling force acting on the pedal 20 to the axle 5 of the rear wheel 25 through a driving force transmitting element from the crankshaft 21 to the front sprocket 24, the chain 23, and the rear sprocket 4. In the driving force transmission element, the pedaling force and the output from the motor are combined to assist the traveling.

  In the synthesis, for example, torque by the pedal force acting on the crankshaft 21 is detected by the torque detection means, and when the detected value exceeds a predetermined value, the motor is started and the torque from the motor is used as auxiliary power. It is common to add as The center motor unit C is provided in the vicinity of the crankshaft 21 as shown in FIG. 8, and the motor driving battery 26 and the like are often arranged along the standing pipe of the frame F of the battery-assisted bicycle B.

  That is, when a pedaling force transmitted from the crankshaft 21 through the pedal 20 or a driving force by the output of the motor is input during driving, the crank sprocket (the front sprocket 24) of the center motor unit C and the driving wheel are used. A driving force is transmitted to the rear wheel through a chain 23 that connects a rear sprocket (sprocket) 4 of a certain rear wheel 25.

Further, in the center motor unit C, a regenerative mechanism for reducing regenerative power generated by reverse input from the rear hub (hub) 1 of the rear wheel to the motor output shaft to the secondary battery in the center motor unit C is provided. I have.
For this reason, a two-way clutch is provided between the output shaft of the motor and the driving force transmission element, which can transmit the driving force from the motor during assist, and can transmit the reverse input from the driving force transmission element during regenerative power generation. Yes.

  That is, during forward non-drive, the regenerative power provided by the reverse input from the rear wheel rear hub 1 to the output shaft of the motor is returned to the secondary battery in the center motor unit C by the regenerative mechanism provided in the center motor unit C. The

  As shown in FIG. 1, the rear hub 1 includes a speed change mechanism 3 having a speed change clutch, a reverse input one-way clutch 2 for reverse input transmission, and the like in a hub case 7 provided coaxially with the rear axle 5. I have.

  The speed change mechanism 3 is constituted by a planetary gear mechanism capable of a total of three speeds including direct connection and two speeds. The speed change mechanism 3 includes two sun gears 3a (hereinafter referred to as a first sun gear 3a-1 and a second sun gear 3a-2) provided on the outer periphery of the axle 5, respectively. It is connected to the axle 5 through 3i.

  The second shift one-way clutch 3i includes two parts, a first clutch part 3i-1 and a second clutch part 3i-2, which are arranged in parallel in the axial direction of the axle 5. The first clutch 3i-1 corresponds to the first sun gear 3a-1, and the second clutch 3i-2 corresponds to the second sun gear 3a-2.

In this embodiment, a ratchet clutch is employed as each of the first clutch part 3i-1 and the second clutch part 3i-2 of the second one-way clutch 3i for shifting. The first clutch part 3i-1 and the second clutch part 3i-2 are each a clutch clutch surface for speed change constituted by irregularities provided on the outer periphery of the axle 5, as shown in FIGS. The shift one-way clutch pawl 3j (3j-1, 3j-2) operates to be engaged or disengaged with 3k (3k-1, 3k-2). One end of the one-way clutch pawl 3j (3j-1, 3j-2) for shifting is elastically connected to the clutch cam surface 3k (3k-1, 3k-2) provided on the axle 5 side by an elastic member 3h. It is energized in the direction to get up.
Hereinafter, the cam surface of the first clutch portion 3i-1 is referred to as a shifting clutch cam surface 3k-1, and the cam surface of the second clutch portion 3i-2 is referred to as a shifting clutch cam surface 3k-2. The clutch pawl (ratchet pawl) of the first clutch portion 3i-1 is a one-way clutch pawl 3j-1 for shifting, and the clutch pawl (ratchet pawl) of the second clutch portion 3i-2 is a one-way clutch pawl 3j-2 for shifting. Called.

  The transmission mechanism 3 includes a planetary gear 3b having a two-stage gear portion meshing with the first sun gear 3a-1, the second sun gear 3a-2, a planet carrier 3c that holds the planetary gear 3b, and A hub case 7 that is integral with an outer ring gear 3d that meshes with the planetary gear 3b is provided. Furthermore, a first gear shift one-way clutch 3e is provided between the planet carrier 3c and the second sun gear 3a-2. Of the two-stage gear portions of the planetary gear 3b, the second sun gear 3a-2 is shown in the small diameter gear portion shown on the left side of FIG. 1, and the first sun gear 3a- is shown in the right side gear portion shown in the right side. 1 are engaged with each other.

  In this embodiment, a ratchet clutch is also used for the first speed change one-way clutch 3e. As shown in FIG. 2 (a), the first shift one-way clutch 3e has a planetary carrier mounted on a shift clutch cam surface 3f formed by unevenness provided on the outer periphery of the second sun gear 3a-2. The one-way clutch pawl 3g for shifting provided in 3c operates so as to engage or disengage. One end of the one-way clutch pawl 3g for shifting is urged by the elastic member 3h in the direction of rising toward the shifting clutch cam surface 3f provided on the planet carrier 3c side.

  Further, as shown in FIG. 1, bearings 13 and 14 are provided between the planet carrier 3c and the axle 5, between the planet carrier 3c and the hub case 7, and between the hub case 7 and the axle 5, respectively. Are supported so as to be rotatable relative to each other.

  In this embodiment, the outer ring gear 3d is formed integrally with the hub case 7, but it is also conceivable that the outer ring gear 3d and the hub case 7 are formed separately and meshed so as to rotate together. .

  The first sun gear 3a-1 and the second sun gear 3a-2 are driven by the sprocket 4 by the first clutch portion 3i-1 and the second clutch portion 3i-2 of the one-way clutch 3i for second speed change. On the other hand, either one can be selectively fixed to the axle 5 or both can be free. This switching can be performed by operating a shift control mechanism 10 described later.

  The second sun gear 3a-2 and the planet carrier 3c are fixed to the driving force from the sprocket 4 by the first gear shift one-way clutch 3e (cannot be relatively rotated), or are in a free state. (Relatively rotatable). This switching can also be performed by operating the shift control mechanism 10. Shifting can be performed by each of these operations.

In this embodiment, as shown in FIGS. 2B and 2C, two one-way clutch pawls 3g and 3j for shifting are arranged in the circumferential direction, and when one is engaged, the other is The positions of the one-way clutch pawls 3g, 3j for shifting and the phases of the uneven portions of the clutch cam surfaces 3f, 3k for shifting are set so as not to engage.

  As a result, the maximum time (rotation angle) until each shift one-way clutch pawl 3g, 3j engages with the shift clutch cam surface 3f, 3k is shortened, so that a smooth shift is possible.

Further, a speed change sleeve 10b is disposed in a groove (recess) of the speed change clutch cam surfaces 3f, 3k on the outer surface of the axle 5.
In this embodiment, the shift clutch cam surfaces 3f and 3k formed by the continuity of the unevenness provided on the outer surface of the axle 5 and the second sun gear 3a-2 are used for speed change with the continuity of the unevenness being 6 times. Although the groove portions (concave portions) into which the one-way clutch pawls 3g and 3j enter are six places in the circumferential direction, the number of the irregularities can be further increased. By increasing the unevenness, the maximum time (rotation angle) until the shifting one-way clutch pawls 3g, 3j are engaged with the shifting clutch cam surfaces 3f, 3k is shortened, so that smooth shifting is possible.

  The reverse input one-way clutch 2 is a roller clutch. As shown in FIG. 2 (d), the reverse input one-way clutch 2 is provided between the first sun gear 3a-1 and the axle 5, and the inner ring 2b is coaxially fixed to the axle 5. A roller clutch cam surface is provided on the outer surface of the inner ring 2b.

  Moreover, the outer ring | wheel of the roller clutch is integrally provided in the inner surface of the 1st sun gear 3a-1. A cylindrical roller 2a as an engagement element is held by a cage 2d. The roller 2a is disposed on the roller clutch cam surface of the inner ring 2b, and is urged counterclockwise in FIG. 2, that is, the wedge is narrowed by an elastic member (not shown).

  With these configurations, for example, the first shift one-way clutch 3e prevents the second sun gear 3a-2 from rotating relative to the planetary carrier 3c with respect to the driving force, so that the first clutch of the second shift one-way clutch 3i. When the first sun gear 3a-1 and the second sun gear 3a-2 are brought into a free state with respect to the axle 5 by the part 3i-1 and the second clutch part 3i-2, the driving force is generated from the rear sprocket 4. When input, the driving force is transmitted to the planetary gear 3b via the planetary carrier 3c, but the second sun gear 3a-2 can rotate integrally with the planetary carrier 3c, so that the planetary gear is at a constant speed (direct connection). A driving force is transmitted from the gear 3b to the outer ring gear 3d (hub case 7).

Further, the first sun gear 3a-2 can be rotated relative to the planet carrier 3c with respect to the driving force by the first speed one-way clutch 3e, and the second sun gear 3a-2 is fixed to the axle 5. When the first sun gear 3a-1 is free on the axle 5, if the number of teeth of the second sun gear 3a-2 is a and the number of teeth of the outer ring gear 3d is d, the increase from the planet carrier 3c to the outer ring gear 3d is increased. The speed ratio is (a + d) / d
It becomes. At this time, the first sun gear 3a-1 is idling with respect to the axle 5, and is not involved in torque transmission.

  At this time, as shown in FIG. 7, the first shift one-way clutch 3e is forcibly changed by the convex portion 10j of the first shift one-way clutch switching member 10g provided in the shift control mechanism 10. 3g is in a state where it does not bite into the clutch cam surface 3f for shifting. The convex portion 10j can enter between the one-way clutch pawl 3g for shifting and the clutch cam surface 3f for shifting, and can release the engagement of the one-way clutch pawl 3g for shifting.

When the second sun gear 3a-2 is free with respect to the axle 5 and the first sun gear 3a-1 is fixed to the axle 5, the number of teeth of the first sun gear 3a-1 is a, If the number of teeth of the planetary gear 3b meshing with the gear 3a-2 is b, the number of teeth of the planetary gear 3b meshing with the first sun gear 3a-1 is c, and the number of teeth of the outer ring gear 3d is d. The speed increasing ratio from the planet carrier 3c to the outer ring gear 3d is [(a × b) / (c × d)] + 1
It becomes. At this time, the second sun gear 3a-2 is idle with respect to the axle 5, and is not involved in torque transmission.

  That is, since the first sun gear 3a-1 and the second sun gear 3a-2 have different numbers of teeth, the first sun gear 3a-1 and the second sun gear 3a-2 are free with respect to the axle 5. The second sun gear 3a-2 and the planet carrier 3c are fixed, or the second sun gear 3a-2 and the planet carrier 3c are free, and the first sun gear 3a-1 and second The speed increase ratio can be changed by fixing any one of the sun gears 3a-2.

  Next, the configuration of the shift control mechanism 10 will be described. As described above, the shift clutch cam surface 3f of the first shift one-way clutch 3e is provided on the outer surface of the second sun gear 3a-2. Further, a shift clutch cam surface 3k of the second shift one-way clutch 3i is provided on the outer surface of the axle 5.

  The speed change sleeve 10b is provided intermittently along the circumferential direction, and the speed change clutch cam surface 3k facing the speed change one-way clutch claws 3j-1, 3j-2 of the second speed change one-way clutch 3i is provided. It can be covered from the outer peripheral side. Moreover, it has the notch part 10d in the two axial directions.

  The speed change sleeve 10b is movable in the axial direction of the axle 5. By operating the speed change sleeve 10b to move in the axial direction, the notch portion 10d becomes the speed change clutch cam surface 3k of the second speed change one-way clutch 3i. And the position retracted from the position of the shift clutch cam surface 3k, and the second shift one-way clutch 3i is switched by the movement.

  Further, the speed change control mechanism 10 includes an operation portion 10a that passes through the shaft hole 5a of the axle 5 and has one end thereof drawn out from the axle 5 to be movable in the axial direction from the outside. By operating the operating portion 10a to move in the axial direction, the shifting sleeve 10b is operated, and the switching of the second shifting one-way clutch 3i is possible.

  Here, as shown in FIG. 1, the transmission sleeve 10 b is fixed to the axle 5 by a pin 10 e inserted into a lateral hole 10 f provided in the axle 5. The shifting sleeve 10b can be moved in the axial direction by operating the shifting pin 10e to move in the axial direction within the lateral hole 10f by the operating portion 10a. The speed change sleeve 10b is biased in the axial direction by an elastic member 10c.

Further, the notch 10d of the speed change sleeve 10b has a tapered surface 10h at its axial end and a tapered surface 10i at its circumferential end.
Thus, by providing the tapered surface 10h at the axial end of the notch 10d, the one-way clutch pawls 3j-1, 3j-2 for shifting and the edges of the notch 10d engaged with the clutch cam surface 3k for shifting. Can be increased by the inclined surface of the taper surface 10h so that the shifting one-way clutch pawls 3j-1, 3j-2 are removed from the shifting clutch cam surface 3k.
Further, by providing the tapered surface 10i at the circumferential end, the one-way clutch pawls 3j-1 and 3j-2 for shifting can be tapered when rotating in the reverse direction (in the shifting clutch portion, rotating in the reverse input direction). Since it moves on the cam surface along the inclined surface of 10i, smooth rotation is possible.

  Specifically, the notch portion 10d faces only the shifting clutch cam surface 3k of either the first clutch portion 3i-1 or the second clutch portion 3i-2, so that the shifting one-way clutch on the facing side thereof. The claw 3j (3j-1, 3j-2) enters into the notch 10d by the urging force of the elastic member, and one end thereof engages with the shift clutch cam surface 3k on the axle 5 side. The notch portions arranged in the axial direction so that the two notch portions 10d do not face the clutch cam surfaces 3k-1 and 3k-2 for shifting of the first clutch portion 3i-1 and the second clutch portion 3i-2 at the same time. Since the interval between 10d is determined, the one-way clutch pawls 3j (3j-1, 3j-2) for shifting on the side not facing the notch 10d are moved to the shifting clutch cam surface 3k by the shifting sleeve 10b. Engagement is blocked.

  The operation of this embodiment will be described in more detail. First, the state of the first shift stage (direct connection state) is shown in FIGS. The rear sprocket 4 is provided in the hub case 7 on the one side in the axial direction. The shift control mechanism 10 is arranged on the rear sprocket 4 side.

In this state, the shifting one-way clutch pawl 3j-1 and the shifting one-way clutch pawl 3j-2 of the second shifting one-way clutch 3i are separated from the shifting clutch cam surface 3k by the shifting sleeve 10b.
For this reason, the first sun gear 3 a-1 and the second sun gear 3 a-2 can be rotated around the axis of the axle 5 with respect to the driving force from the rear sprocket 4.

On the other hand, the planetary carrier 3c and the second sun gear 3a-2 are unable to rotate relative to the driving force by the first shift one-way clutch 3e.
Accordingly, the driving force is transmitted from the rear sprocket 4 at a constant speed in the order of the planet carrier 3c, the planet gear 3b, and the hub case 7 (outer ring gear 3d).

  The state of the second speed change (speed increase 1) is shown in FIGS. By pushing the operating portion 10a of the speed change control mechanism 10 to a position in the axial direction by operating from the outside of the axle 5, the speed change sleeve 10b slides in the axial direction, and the one-way clutch for speed change of the first clutch portion 3i-1. The notch 10d of the shift sleeve 10b moves to the position of the claw 3j-1.

Thereby, the one-way clutch pawl 3j-1 for shifting of the first clutch portion 3i-1 is engaged with the clutch cam surface 3k for shifting, and the first sun gear 3a-1 is driven against the axle 5 with respect to the driving force. Relative rotation is impossible.
At this time, at the position of the shifting one-way clutch pawl 3j-2 of the second clutch portion 3i-2, the shifting clutch cam surface 3k and the shifting one-way clutch pawl 3j-2 are separated by the shifting sleeve 10b. For this reason, the second sun gear 3 a-2 is rotatable around the axle 5.

  Further, the first shifting one-way clutch switching member 10g moves in the axial direction together with the shifting sleeve 10b until the convex portion 10j of the first shifting one-way clutch switching member 10g is positioned on the shifting one-way clutch pawl 3g. When moved, the shifting one-way clutch pawl 3g swings along the convex portion 10j of the first shifting one-way clutch switching member 10g by the rotational movement of the planet carrier 3c, and is separated from the shifting clutch cam surface 3f. For this reason, the planet carrier 3c and the second sun gear 3a-2 can be rotated relative to each other.

In this state, the driving force from the rear sprocket 4 is the speed increasing ratio (a + d) / d, where a is the number of teeth of the first sun gear 3a-1 and d is the number of teeth of the outer ring gear 3d.
Is transmitted to the hub case 7.

  The state of the third speed change (speed increase 2) is shown in FIGS. By further pushing the operating portion 10a of the speed change control mechanism 10 from the outside of the axle 5, the speed change sleeve 10b further slides in the axial direction to the right side in the drawing.

  By this slide, the notch portion 10d of the speed change sleeve 10b is moved to the position of the speed change one-way clutch pawl 3j-2 of the second clutch portion 3i-2. Thereby, the one-way clutch pawl 3j-2 for shifting of the second clutch portion 3i-2 is engaged with the clutch cam surface 3k for shifting, and the second sun gear 3a-2 is locked to the axle 5 with respect to the driving force.

  At this time, at the position of the shifting one-way clutch pawl 3j-1 of the first clutch portion 3i-1, the shifting clutch cam surface 3k and the shifting one-way clutch pawl 3j-1 are separated by the shifting sleeve 10b. For this reason, the first sun gear 3 a-1 can rotate around the axis of the axle 5.

  Further, the shift one-way clutch pawl 3g-1 is separated from the shift clutch cam surface 3k of the second sun gear 3a-2 by the first shift one-way clutch switching member 10g. The sun gear 3a-2 is capable of relative rotation.

In this state, the driving force from the rear sprocket 4 is such that the number of teeth of the second sun gear 3a-2 is a, the number of teeth of the planetary gear 3b meshing with the first sun gear 3a-1 is b, and the second sun gear 3a- Speed ratio [(a × b) / (c × d)] + 1 where c is the number of teeth of the planetary gear 3b meshing with 2 and d is the number of teeth of the outer ring gear 3d.
Is transmitted to the hub case 7.

When returning from the third speed to the second speed or returning from the second speed to the first speed, the elastic member 10c is released or released by releasing or reducing the load (pressing force) applied to the operation unit 10a. As a result, the shift sleeve 10b is pushed back. At this time, the force that pushes up the one-way clutch pawl 3j (3j-1, 3j-2) for shifting that is engaged with the clutch clutch surface 3k by the tapered surface 10h provided at the axial end of the notch 10d. It becomes stronger and the shifting sleeve 10b is easily returned, so that smooth switching is possible.

  At the time of forward non-drive (at the time of reverse input from the tire), the rotation directions of the sun gears 3a-1 and 3a-2 with respect to the axle 5 are opposite to those at the time of driving force action. At this time, at any of the shift speeds, the first sun gear 3a-1 is opposed to the reverse input by the one-way clutch 2 for reverse input provided between the first sun gear 3a-1 and the axle 5. Fixed to.

At this time, the reverse input from the tire is the reduction ratio (a + d) / d, where a is the number of teeth of the first sun gear 3a-1 and d is the number of teeth of the outer ring gear 3d.
Is transmitted from the hub case 7 to the rear sprocket 4.

As described above, in the center motor unit C, the driving force from the motor can be transmitted during assisting from the output shaft of the motor to the driving force transmitting element, and from the driving force transmitting element during regenerative power generation. A two-way clutch capable of transmitting reverse input is provided.
As a result, switching between assist and regenerative power generation is facilitated, and the resistance of the motor can be disconnected when the pedal 21 is stroked without assist.

  Further, when the vehicle is not driven backward (when the bicycle is dismounted and pulled backward), the absolute rotational direction is reversed, but the relationship between the relative rotation of the rear sprocket 4 and the hub case 7 is the same as that during forward driving. The same.

  In this embodiment, the reverse input one-way clutch 2 is provided between the first sun gear 3 a-1 and the axle 5, but this is provided between the second sun gear 3 a-2 and the axle 5. May be. Further, the first speed change one-way clutch 3e is provided between the planet carrier 3c and the second sun gear 3a-2, but this is provided between the planet carrier 3c and the first sun gear 3a-2. May be.

  In this embodiment, the planetary gear 3b has two stages, but one or more planetary gears may be used.

When the planetary gear 3b has three or more stages, the speed change mechanism 3 is provided with the same number of sun gears 3a as the number of gears of the planetary gear 3b.
At this time, each of the sun gears 3a is selectively fixed to the axle 5 with respect to the driving force from the sprocket 4 by the one-way clutch 3i for second speed change, or all of the sun gears 3a are free. It is controlled by the shift control mechanism 10 so as to be in a state.

  In this embodiment, the first gear shift one-way clutch 3e and the second gear shift one-way clutch 3i both employ ratchet clutches. However, as long as they can be similarly controlled by the gear shift control mechanism 10, A one-way clutch having another configuration such as a roller clutch or a sprag clutch may be employed. The reverse input one-way clutch 2 can also employ a sprag clutch.

1 Rear hub (hub)
2 reverse input one-way clutch 2a roller 2b inner ring 2d cage 3 speed change mechanism 3a sun gear 3a-1 first sun gear 3a-2 second sun gear 3b planetary gear 3c planet carrier 3d outer ring gear 3e first one-way clutch 3f Shifting clutch cam surface 3g Shifting one-way clutch pawl 3i Second shifting one-way clutch 3i-1 First clutch portion 3i-2 Second clutch portion 3j Shifting one-way clutch pawl 3k Shifting clutch cam surface 4 Rear sprocket (sprocket)
5 Axle 6 Hub flange 7 Hub case 10 Shift control mechanism 10a Operation portion 10b Shift sleeve 10c Elastic member 10d Notch portion 10e Pin 10f Side hole 10g First shift one-way clutch switching member 10h, 10i Tapered surface 13, 14 Bearing portion 20 Crankshaft 21 Pedal 23 Chain 24 Front sprocket 25 Rear wheel 26 Battery B Battery-assisted bicycle C Center motor unit F Frame

Claims (13)

A secondary battery and an auxiliary drive motor are attached to the frame connecting the front wheel and the rear wheel, and the pedaling force transmitted from the crankshaft or the driving force by the output of the motor can be transmitted to the driving wheel. In the battery-assisted bicycle provided with a regenerative mechanism for returning regenerative power generated by reverse input from the drive wheel to the output shaft of the motor to the secondary battery,
The hub (1) provided on the drive wheel is provided with a speed change mechanism (3) and a reverse input one-way clutch (2). The speed change mechanism (3) is constituted by a planetary gear mechanism and includes at least one sun gear ( 3a), and has a function of transmitting the pedaling force or the driving force generated by the motor output to the driving wheel through the sprocket (4), and the speed change mechanism (3) is engaged with the sun gear (3a). A planetary gear (3b) having at least one gear portion to be engaged, an outer ring gear (3d) engaged with the planetary gear (3b), and a planet carrier (3c) holding the planetary gear (3b). A first-speed one-way clutch (3e) having a function of switching the planetary carrier (3c) and the sun gear (3a) to be relatively rotatable or not rotatable with respect to the driving force, and driving And the second gear-shifting one-way clutch (3i) having a function of switching the sun gear (3a) to be rotatable relative to the axle (5) or not relatively rotatable. (3e) and a shift control mechanism (10) capable of switching the second shift one-way clutch (3i) by an external operation,
By making the planetary carrier (3c) and the sun gear (3a) relatively unrotatable with respect to the driving force and making the sun gear (3a) and the axle (5) relatively rotatable, the sprocket ( 4) from the planetary carrier (3c), the planetary gear (3b), the outer ring gear (3d) to the hub case (7) through a low-speed state, and the planetary carrier ( 3c) and the sun gear (3a) are relatively rotatable, and the sun gear (3a) and the axle (5) are not relatively rotatable, so that the planetary carrier (3c) is removed from the sprocket (4). ), The planetary gear (3b), and the outer ring gear (3d) can be shifted to at least one stage of high speed that transmits driving force to the hub case (7),
The one-way clutch for reverse input (2) is constituted by a roller clutch provided between the sun gear (3a) and the axle (5), and the sun gear for the reverse input from the drive wheels. A hub (1) having a function of preventing rotation of (3a) around the axle (5) and transmitting reverse input from the drive wheel from the hub case (7) to the sprocket (4) A power-assisted bicycle equipped with A secondary battery and an auxiliary drive motor are attached to the frame connecting the front wheel and the rear wheel, and the pedaling force transmitted from the crankshaft or the driving force by the output of the motor can be transmitted to the driving wheel. In the battery-assisted bicycle provided with a regenerative mechanism for returning regenerative power generated by reverse input from the drive wheel to the output shaft of the motor to the secondary battery,
The hub (1) provided on the drive wheel is provided with a speed change mechanism (3) and a reverse input one-way clutch (2). The speed change mechanism (3) is constituted by a planetary gear mechanism and includes at least one sun gear ( 3a), and has a function of transmitting the pedaling force or the driving force generated by the motor output to the driving wheel through the sprocket (4), and the speed change mechanism (3) is engaged with the sun gear (3a). A planetary gear (3b) having at least one gear portion to be engaged, an outer ring gear (3d) engaged with the planetary gear (3b), and a planet carrier (3c) holding the planetary gear (3b). A first-speed one-way clutch (3e) having a function of switching the planetary carrier (3c) and the sun gear (3a) to be relatively rotatable or not rotatable with respect to the driving force, and driving And the second gear-shifting one-way clutch (3i) having a function of switching the sun gear (3a) to be rotatable relative to the axle (5) or not relatively rotatable. (3e) and a shift control mechanism (10) capable of switching the second shift one-way clutch (3i) by an external operation,
By making the planetary carrier (3c) and the sun gear (3a) relatively unrotatable with respect to the driving force and making the sun gear (3a) and the axle (5) relatively rotatable, the sprocket ( 4) from the planetary carrier (3c), the planetary gear (3b), the outer ring gear (3d) to the hub case (7) through a low-speed state, and the planetary carrier ( 3c) and the sun gear (3a) are relatively rotatable, and the sun gear (3a) and the axle (5) are not relatively rotatable, so that the planetary carrier (3c) is removed from the sprocket (4). ), The planetary gear (3b), and the outer ring gear (3d) can be shifted to at least one stage of high speed that transmits driving force to the hub case (7),
The one-way clutch for reverse input (2) is constituted by a sprag clutch provided between the sun gear (3a) and the axle (5), and the sun gear for reverse input from the drive wheels. A hub (1) having a function of preventing rotation of (3a) around the axle (5) and transmitting reverse input from the drive wheel from the hub case (7) to the sprocket (4) A power-assisted bicycle equipped with   The planetary gear (3b) has a plurality of gear portions, the sun gear (3a) is provided in the same number as the gear portions, and one sun gear (3a) is provided for each gear portion. Engagement, and by selectively disabling any one of the plurality of sun gears (3a) with respect to the driving force relative to the axle (5), it is possible to perform a multi-stage shift in the high speed state. The battery-assisted bicycle according to claim 1 or 2, wherein The battery-assisted bicycle according to any one of claims 1 to 3, wherein the first speed change one-way clutch (3e) is a ratchet clutch. The battery-assisted bicycle according to any one of claims 1 to 3, wherein the second speed change one-way clutch (3i) is a ratchet clutch. The first shift one-way clutch (3e) includes a shift one-way clutch pawl (3g) provided on the planetary carrier (3c) and a shift clutch cam surface provided on the outer surface of the sun gear (3a). The battery-assisted bicycle according to claim 4, further comprising: 3f). The second shift one-way clutch (3i) includes a shift one-way clutch pawl (3j) provided on the sun gear (3a) and a shift clutch cam surface (3k) provided on the outer surface of the axle (5). The battery-assisted bicycle according to claim 5, further comprising: The shift control mechanism (10) includes a shift sleeve (10b) having a notch (10d) around the axle (5), and the shift sleeve (10b) moves in the axial direction of the axle (5). The notch (10d) is moved to the position of the shift clutch cam surface (3k) of the second shift one-way clutch (3i) by moving the shift sleeve (10b) in the axial direction. And the second retraction one-way clutch (3i) to a position retracted from the position of the clutch clutch cam surface (3k), and the movement causes the switching of the second one-way clutch (3i). The battery-assisted bicycle according to claim 7, wherein: The shift control mechanism (10) rotates the shift sleeve (10b) around one axis of the axle (5) at one end of the shift sleeve (10b), so that the first shift one-way clutch ( A first shifting one-way clutch switching member (10g) having a convex portion (10j) capable of releasing the engagement between the shifting one-way clutch pawl (3g) and the shifting clutch cam surface (3f) of 3e); The battery-assisted bicycle according to claim 8, which is provided. A plurality of the one-way clutch pawls (3g) for shifting of the first one-way clutch (3e) are provided in the circumferential direction. The one-way clutch pawls (3g) for shifting and the clutch cam surface (3f for shifting) ) Is engaged so that at least one other one-way clutch pawl (3g) for shifting does not engage with the clutch cam surface (3f) for shifting. The battery-assisted bicycle according to claim 6. A plurality of the one-way clutch pawls (3j) for shifting of the second one-way clutch (3i) are provided in the circumferential direction, and the one-way clutch pawls (3j) for shifting and the clutch cam surface (3k for shifting) ) Is engaged so that at least one other one-way clutch pawl (3j) for shifting is not engaged with the clutch clutch surface (3k) for shifting. The battery-assisted bicycle according to claim 7.   The shift clutch cam surfaces (3f, 3k) are constituted by irregularities formed along the circumferential direction, and the shift clutch cam surfaces (3f, 3k) due to the irregularities are 4 along the circumferential direction. The battery-assisted bicycle according to claim 11, wherein more than one portion is provided. A two-way clutch is provided between the motor output shaft and the driving force transmission element, which can transmit the driving force from the motor during assisting and can transmit the reverse input from the driving force transmission element during regenerative power generation. The battery-assisted bicycle according to any one of claims 1 to 12.

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