JP2011189839A - Power-assisted bicycle with regeneration mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To perform regenerative charging without complicating a device in a center motor type power-assisted bicycle with an internal transmission. <P>SOLUTION: In this power-assisted bicycle, a hub 1 of a driving wheel includes a shift mechanism 3 constituted of a planetary gear mechanism, a one-way clutch 2 for a reverse input and a shift control mechanism 10. The shift mechanism 3 includes a sun gear 3a and transmits a driving force to the driving wheel through a sprocket 4. The shift control mechanism 10 is capable of switching a planetary carrier 3c and the sun gear 3a to be relatively rotatable or relatively non-rotatable via a one-way clutch 3e for a first shift in relation to the driving force, performing the shift by switching the sun gear 3a to be rotatable or non-rotatable around an axle 5 via a one-way clutch 3i for second shift and shifting to a direct connection state and a high speed state of at least one stage. As for the reverse input, the sun gear 3a is made non-rotatable around the axle 5 via the one-way clutch 2 for the reverse input to transmit the reverse input. <P>COPYRIGHT: (C)2011,JPO&INPIT

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 driving force is transmitted to the hub case via the hub, the planetary carrier and the sun gear can be relatively rotated with respect to the driving force, and the sun gear and the axle are not relatively rotatable. It is possible to shift from a sprocket to at least one high-speed state in which driving force is transmitted to the hub case via the planet carrier, the planetary gear, and the outer ring gear, and the one-way clutch for reverse input is The one-way clutch for reverse input provided between the gear and the axle has a function of making the sun gear unrotatable around the axle with respect to the reverse input from the drive wheel, A configuration of a battery-assisted bicycle having a hub that allows reverse input from the drive wheel to be transmitted 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.

  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 each one-way clutch. For example, a ratchet clutch can be adopted as the one-way clutch for the first speed change. In addition, when a ratchet clutch is used as the first-speed one-way clutch, and when any other than the ratchet clutch is used, either the one-way clutch for the second shift, the one-way clutch for reverse input, or both A ratchet clutch can be employed.

  At this time, by providing the one-way clutch pawls of the second speed change one-way clutch and the reverse input one-way clutch on the sun gear side, the structure of the axle can be simplified. That is, the one-way clutch for second speed change includes a one-way clutch pawl for speed change provided on the sun gear, and a clutch cam surface for speed change provided on the outer surface of the axle, and the one-way clutch for reverse input is provided on the sun gear. The reverse input one-way clutch pawl and the reverse input clutch cam surface provided on the outer surface of the axle are provided.

  In addition, a configuration is used in which the outer periphery of the axle is provided with irregularities that function as both the second shift clutch cam surface of the second shift one-way clutch and the reverse input clutch cam surface of the reverse input one-way clutch. can do. In this way, the unevenness becomes a two-way clutch cam surface having both functions of the shift clutch cam surface and the reverse input clutch cam surface, and the structure of the axle can be simplified.

  In the configuration in which the one-way clutch pawls of the second-shift one-way clutch and the reverse input one-way clutch are provided on the sun gear side, the shift control mechanism includes a shift sleeve having a notch around the axle, and the shift sleeve is It is movable in the axial direction of the axle, and by operating the shifting sleeve to move in the axial direction, the notch is located at the position of the shifting clutch cam surface of the second shifting one-way clutch and the second shifting one-way clutch. It is possible to adopt a configuration in which the second shift one-way clutch is switched by moving between the position of the shift clutch cam surface and the position retracted.

The first speed change one-way clutch is a ratchet clutch provided with a speed change one-way clutch pawl supported on the outer surface of the sun gear so as to be capable of swinging movement, and a speed change clutch cam surface provided on the inner surface of the planet carrier. In this case, the shifting sleeve includes a first shifting one-way clutch switching portion, and the first shifting one-way clutch switching portion is retracted from the shifting one-way clutch pawl by the movement operation of the shifting sleeve in the axial direction. It is possible to adopt a configuration that moves between a position and a position in contact with the one-way clutch pawl for shifting, and switches the first one-way clutch for shifting by the movement.
That is, when the first shift one-way clutch switching unit is retracted from one end of the shift one-way clutch pawl, the shift one-way clutch pawl is engaged with the shift clutch cam surface, and the first shift one-way clutch switching unit is When moving to a position where it comes into contact with one end of the one-way clutch pawl, the shifting one-way clutch pawl swings and disengages from the shifting clutch cam surface, thereby switching the first shifting one-way clutch. The configuration to be performed can be adopted. 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.

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

At this time, 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 second shift one-way clutch shifts on the tapered surface. A configuration in which the one-way clutch pawl is in contact can be employed.
Further, the first speed change one-way clutch switching portion of the speed change sleeve has a tapered surface at its axial end that gradually approaches the inner diameter side as it approaches the first speed change one-way clutch along the axial direction. A configuration in which the one-way clutch pawl for shifting of the first one-way clutch contacts with the tapered surface can be employed.

If the taper surface is provided on the edge of the notch portion of the speed change sleeve and the end edge of the first speed change one-way clutch switching portion, and the corresponding one-way clutch pawl is in contact with the taper surface, the clutch cam surface When the one-way clutch pawl that has been bitten into one end of the notch or the first-speed one-way clutch switching portion comes into contact, the inclined surface of the tapered surface can increase the force to remove the one-way clutch pawl from the cam surface. .
Further, a tapered surface can be provided in the notch portion of the transmission 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 each of these configurations, it is desirable to apply a sleeve having a configuration different from that of the speed change sleeve for the reverse input one-way clutch. That is, the shift control mechanism includes a reverse input sleeve having a notch around the axle, and the reverse input sleeve is movable in the axial direction of the axle, but the notch is for reverse input at any gear stage. It is positioned on the one-way clutch pawl, and it is possible to adopt a configuration in which the reverse input one-way clutch pawl can always be engaged with the reverse input clutch cam surface during forward non-drive.
When the forward drive is not driven, the reverse input one-way clutch is always locked at any shift speed, and the reverse input sleeve has a function of preventing the shift one-way clutch pawl from being caught in the two-way clutch cam surface.

  A configuration in which a taper surface is provided at the circumferential end of the cutout portion of the reverse input sleeve can be employed. The effect of the tapered surface is the same as that of the speed change sleeve.

  In addition, the speed change sleeve and the reverse input sleeve are configured to be movable in the axial direction from the outside of the axle by an operating portion that passes through the inside of the axle and is pulled out to the outside of the axle. Can be adopted. If it does in this way, the switching function in the one-way clutch for the 1st shift, the one-way clutch for the 2nd shift, and the one-way clutch for the reverse input can be realized with a simple configuration.

  At this time, the shifting sleeve and the reverse input sleeve can be configured to be urged in the axial direction by an elastic member. In this way, when the operating portion is operated to move the speed change sleeve and the reverse input sleeve in the axial direction, the biasing force of the elastic member is used for the movement in the axial direction in the one direction or the other direction. It is possible to simplify the configuration of the device provided for operating the operation unit outside the axle.

Further, at this time, in order to link the movement of the operation portion in the axial direction and the movement of the shifting sleeve and the reverse input sleeve, a lateral hole penetrating the axle is provided, and a pin in a direction intersecting the axial direction of the axle is provided in the lateral hole. It is possible to adopt a structure in which the pin, the speed change sleeve and the reverse input sleeve are inserted, and the speed change sleeve and the reverse input sleeve are both moved by pushing the pin by the operating portion.
At this time, when the load from the outside to the operation unit is removed by applying the load in the direction opposite to the direction in which the operation unit pushes the pin in the axial direction by the elastic member for the shift sleeve and the reverse input sleeve, The shift sleeve and the reverse input sleeve can be returned to their original positions by the member.

  Further, at this time, the sprocket is disposed closer to one axial direction in the hub case, and a configuration in which the shift control mechanism is disposed closer to the other axial direction can be employed. Thus, it is preferable to dispose the speed change control mechanism on the opposite side of the rear sprocket because the device becomes compact.

  In addition, a configuration in which the unevenness that functions as both the shifting clutch cam surface of the second shifting one-way clutch and the reverse input clutch cam surface of the reverse input one-way clutch is provided on the outer periphery of the axle, that is, in both directions on the axle In the configuration provided with the clutch cam surface, each of the speed change sleeve and the reverse input sleeve can be shaped so as to cover the concave portion (the concave portion to which the one-way clutch pawl is engaged) of the bidirectional clutch cam surface.

In this configuration with the two-way clutch cam surface, the reverse input sleeve always has a notch on the reverse input one-way clutch pawl of the reverse input one-way clutch, and always reverse input for reverse input. The one-way clutch pawl can be configured to bite into the cam surface. For this reason, the sun gear is fixed to the axle, and the reverse input from the drive wheel is always transmitted to the rear sprocket when the forward drive is not driven.
On the other hand, for the one-way clutch pawl of the second shift one-way clutch, the cam surface is normally closed by the shift sleeve and the reverse input sleeve, so that the one-way clutch pawl for the shift is the cam surface. Don't bite into. By operating the shifting sleeve in the axial direction, when the notch is positioned on the shifting one-way clutch pawl of the second shifting one-way clutch, the shifting one-way clutch pawl is engaged with the cam surface, and the sun gear is The driving force from the rear sprocket is transmitted to the driving wheels at a set speed increasing ratio.

In each of these configurations, the portion that covers the shifting one-way clutch pawl of the second shifting one-way clutch in the shifting sleeve and the portion that covers the reverse input one-way clutch pawl of the reverse input one-way clutch in the reverse input sleeve are: A portion that is provided intermittently along the circumferential direction and covers a portion of the shifting one-way clutch claw of the second shifting one-way clutch in the shifting sleeve, and a reverse input one-way of the reverse input one-way clutch in the reverse input sleeve It is possible to employ a configuration in which portions covering the clutch pawls are alternately arranged along the circumferential direction.
Further, in particular, the portion that covers the one-way clutch pawl for shifting of the one-way clutch for second gear shifting in the sleeve for shifting, and the portion that covers the one-way clutch pawl for reverse input of the one-way clutch for reverse input in the sleeve for reverse input, respectively It is possible to adopt a configuration in which the vehicle is disposed on both sides with respect to the axis of the axle and is disposed at a position where the phase is shifted by 90 ° around the axle.

  By doing so, the reverse input sleeve and the shift sleeve do not interfere with each other, and both the shift switching and the reverse input transmission switching can be performed smoothly. In addition, both mechanisms can be established in a small space.

However, when emphasis is placed on the shift changeability, it is possible to adopt a configuration in which the shift sleeve is relatively more numerous than the reverse input sleeve and appears between the cam surface and the one-way clutch pawl.
For example, the speed change sleeve and the reverse input sleeve are provided intermittently along the circumferential direction, and the number of repetitions in the circumferential direction of the reverse input sleeve is greater than the number of repetitions in the circumferential direction of the speed change sleeve. In this configuration, the number of intermittent repetitions is set larger.

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.

Front sectional view showing driving (direct connection / low speed state) of the embodiment (A) is AA sectional drawing of FIG. 1, (b) is BB sectional drawing of FIG. 1, (c) is CC sectional drawing of FIG. Front sectional view showing driving (acceleration / transmission second stage) of the embodiment (A) is AA sectional drawing of FIG. 3, (b) is BB sectional drawing of FIG. 3, (c) is CC sectional drawing of FIG. Front sectional view showing driving (speed increase / transmission third stage) of the embodiment (A) is AA sectional drawing of FIG. 5, (b) is BB sectional drawing of FIG. 5, (c) is CC sectional drawing of FIG. Front sectional view showing a state in which reverse input torque can be transmitted in the embodiment (shifting is at the first stage) (A) is AA sectional drawing of FIG. 7, (b) is BB sectional drawing of FIG. 7, (c) is CC sectional drawing of FIG.

  An embodiment of the present invention will be described with reference to FIGS. The battery-assisted bicycle of this embodiment has a center motor system in which a secondary battery and an auxiliary drive motor (center motor unit) 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.

  When driving, that is, when the pedaling force transmitted from the crankshaft through the pedal or the driving force due to the output of the motor is input, the crank sprocket of the center motor unit (not shown) and the rear sprocket of the rear wheel as the driving wheel ( The driving force can be transmitted to the rear wheel via a power transmission element such as a chain connecting the sprocket 4. Further, a regenerative mechanism is provided that reduces regenerative power generated by reverse input from the rear wheel rear hub (hub) 1 to the output shaft of the motor to the secondary battery of the center motor unit during forward non-drive.

  As shown in FIG. 1, the rear hub 1 includes a speed change mechanism 3 having a speed change clutch, a reverse input transmission clutch, and the like in a hub case 7 provided coaxially with the rear wheel axle 5. 1, 3, 5, and 7, the upper side from the central axis is a cross-sectional view of the transmission clutch, and the lower side is a cross-sectional view of the reverse input clutch.

  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 portion 3i-1 and the second clutch portion 3i-2 are respectively provided with a shift clutch cam surface 3f (3f-1) provided on the outer periphery of the axle 5, as shown in FIGS. , 3f-2), the shifting one-way clutch pawl 3g (3g-1, 3g-2) operates so as to engage or disengage. The shift one-way clutch pawl 3g (3g-1, 3g-2) is provided with a shift clutch cam surface 3f (3f-1, 3f-2) having one end provided on the axle 5 side by an elastic member (not shown). 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 3f-1, and the cam surface of the second clutch portion 3i-2 is referred to as a shifting clutch cam surface 3f-2. The clutch pawl (ratchet pawl) of the first clutch portion 3i-1 is a one-way clutch pawl 3g-1 for shifting, and the clutch pawl (ratchet pawl) of the second clutch portion 3i-2 is a one-way clutch pawl 3g-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. Further, a first gear shift one-way clutch 3e is provided between the planet carrier 3c and the first sun gear 3a-1. Of the two-stage gear portions of the planetary gear 3b, the first sun gear 3a-1 is shown in the gear portion with the large diameter shown on the left side of FIG. 1, and the second sun gear 3a- is shown in the gear portion with the small diameter shown on the right side. 2 mesh 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. 2A, the first shift one-way clutch 3e is provided on the first sun gear 3a-1 on the shift clutch cam surface 3k provided on the inner periphery of the planet carrier 3c. The one-way clutch pawl 3j for shifting is operated so as to engage or disengage. One end of the one-way clutch pawl 3j for shifting is urged in an upward direction by an elastic member (not shown) toward the shifting clutch cam surface 3k provided on the planet carrier 3c side.

  Further, as shown in FIG. 1, bearing portions 13, 14, 15 are provided between the planet carrier 3 c and the axle 5, between the planet carrier 3 c and the hub case 7, and between the hub case 7 and the axle 5, respectively. Provided and supported so as to be rotatable relative to each other.

  In this embodiment, the outer ring gear 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.

  Also, the first sun gear 3a-1 and the planet carrier 3c are fixed to the driving force from the sprocket 4 by the first gear shift one-way clutch 3e (relative rotation is impossible) or 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, the reverse input one-way clutch 2 is also formed of a ratchet clutch. As shown in FIG. 2 (b), the reverse input one-way clutch 2 has a reverse input one-way clutch pawl 2g on the inner periphery of the first sun gear 3a-1, and the reverse input one-way clutch pawl. One end of 2g is urged by an elastic member (not shown) in the direction of rising toward the reverse input clutch cam surface 2f provided on the axle 5 side.

  Further, on the outer surface of the axle 5, a bidirectional clutch cam having both functions of a reverse input clutch cam surface 2f of the reverse input one-way clutch 2 and a shift clutch cam surface 3f-1 of the first clutch portion 3i-1. A surface 11 is provided. That is, the two-way clutch cam surface 11 is configured by irregularities in which concave portions and convex portions are alternately arranged in the circumferential direction, and the one-way clutch 2 for reverse input and the first clutch portion 3 i-1 are arranged in the axial direction of the axle 5. They are provided at substantially the same position (see FIG. 2B). Therefore, the bidirectional clutch cam surface 11 can exhibit both functions of the shift clutch cam surface 3f-1 and the reverse input clutch cam surface 2f.

  Note that the shift clutch cam surface 3f-2 corresponding to the second clutch portion 3i-2 is provided on the outer surface of the axle 5 so as to function alone (see FIG. 2C).

  With these structures, for example, the first sun gear 3a-1 cannot be rotated relative to the planetary carrier 3c with respect to the driving force by the first speed change one-way clutch 3e, and the first clutch of the second speed change 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. However, since the first sun gear 3a-1 can rotate integrally with the planetary carrier 3c, the planetary gear can be driven at a constant speed (direct connection). A driving force is transmitted from the gear 3b to the outer ring gear 3d (hub case 7).

In addition, the first sun gear 3a-1 can be rotated relative to the planetary carrier 3c with respect to the driving force by the first shift one-way clutch 3e, and the first sun gear 3a-1 is fixed to the axle 5. When the second sun gear 3a-2 is free on the axle 5, if the number of teeth of the first sun gear 3a-1 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 second sun gear 3a-2 is idle with respect to the axle 5, and is not involved in torque transmission.

  At this time, the one-way clutch 3e for shifting is forcibly engaged with the one-way clutch pawl 3j for shifting by the first-shifting one-way clutch switching portion 10e included in the shift control mechanism 10 at the shifting clutch cam surface 3k. There is no state.

When the first sun gear 3a-1 is free with respect to the axle 5 and the second sun gear 3a-2 is fixed to the axle 5, the number of teeth of the second sun gear 3a-2 is a, If the number of teeth of the planetary gear 3b meshing with the gear 3a-1 is b, the number of teeth of the planetary gear 3b meshing with the second sun gear 3a-2 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 first sun gear 3a-1 is idling 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 first sun gear 3a-1 and the planet carrier 3c are fixed, or the first sun gear 3a-1 and the planet carrier 3c are free, and the first sun gear 3a-1 and the second sun gear 3a-1 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 3k of the first shift one-way clutch 3e is provided on the inner surface of the planet carrier 3c. Further, on the outer surface of the axle 5, both the reverse input clutch cam surface 2f of the reverse input one-way clutch 2 and the shift clutch cam surface 3f-1 of the first clutch portion 3i-1 of the second shift one-way clutch 3i are provided. A bi-directional clutch cam surface 11 is provided which is formed of irregularities having the functions described above. Further, a shift clutch cam surface 3 f-2 of the second clutch portion 3 i-2 of the second shift one-way clutch 3 i is also provided on the outer surface of the axle 5.
Shift sleeves 10b and reverse input sleeves 10c are alternately arranged on the outer periphery of the axle 5 along the circumferential direction so as to cover the bidirectional clutch cam surface 11 and the shift clutch cam surface 3f-2 (FIG. 2). (See (b) and (c)).

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

  The reverse input sleeve 10c is also provided intermittently along the circumferential direction, and the reverse input clutch cam surface 2f facing the reverse input one-way clutch pawl 2g of the reverse input one-way clutch 2 is disposed on the outer peripheral side. It can be covered from. Moreover, it has the notch 10h in the one axial direction.

  A portion of the shift sleeve 10b covering the second shift one-way clutch pawl 3g (shift clutch cam surface 3f) and the reverse input one-way clutch pawl 2g (reverse input clutch cam) of the reverse input sleeve 10c. The portions covering the surface 2f) are alternately arranged along the circumferential direction.

  In particular, in this embodiment, a portion covering the shifting one-way clutch pawl 3g-1 of the first clutch portion 3i-1 in the shifting sleeve 10b and a portion covering the reverse input one-way clutch pawl 2g in the reverse input sleeve 10c. Are arranged on both sides with the axis of the axle 5 in between, and at a position where the phase is shifted by 90 ° around the axle 5. That is, in the cross section orthogonal to the axis shown in FIG. 2B, the shift sleeve 10b and the reverse input sleeve 10c appear alternately every 90 °. For this reason, both do not interfere and both mechanisms can be established in a small space.

  In the cross section shown in FIG. 2C corresponding to the second clutch portion 3i-2, the arrangement of the shifting sleeve 10b and the reverse input sleeve 10c is the same. That is, the cross-section where the shift sleeve 10b and the reverse input sleeve 10c appear alternately every 90 ° is continuous along the axial direction at least in the effective range for the second shift one-way clutch 3i and the reverse input one-way clutch 2. ing.

  Here, each of the speed change sleeve 10b and the reverse input sleeve 10c is intermittently provided with “parts with members” and “parts without members” along the circumferential direction. The circumferential length of the “portion” and the circumferential length of the “portion without the member” are set to be the same between the sleeves 10b and 10c, respectively. Also, the number of repeated repetitions is the same.

  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 10i is positioned at the position of the speed change clutch cam surface 3f, and the second speed change gear. The second shift one-way clutch 3i is switched by the movement from the position of the clutch cam surface 3f to the retracted position.

  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 speed change sleeve 10 b is fixed to the axle 5 by a pin 10 f inserted in a lateral hole 10 g provided in the axle 5. The shifting sleeve 10b can be moved in the axial direction by operating the shifting pin 10f in the axial direction within the lateral hole 10g by the operating portion 10a. The speed change sleeve 10b is biased in the axial direction by an elastic member 10d.

The notch 10i of the speed change sleeve 10b has a tapered surface 10j at its axial end and a tapered surface at its circumferential end.
Thus, by providing the tapered surface 10j at the axial end of the notch 10i, when the shift one-way clutch pawl 3g engaged with the shift clutch cam surface 3f comes into contact with the edge of the notch 10i, Due to the inclined surface of the tapered surface 10j, the force for removing the one-way clutch pawl 3g for shifting from the clutch cam surface 3f for shifting can be increased.
Also, by providing a tapered surface at the circumferential end, the one-way clutch pawl 3g for shifting is cammed along the inclined surface of the tapered surface during reverse rotation (in the reverse clutch direction, rotation in the reverse input direction). Smooth movement is possible because it moves on the surface.

  The notch portion 10i faces only the shifting clutch cam surface 3f (3f-1, 3f-2) of either the first clutch portion 3i-1 or the second clutch portion 3i-2. The one-way clutch pawl 3g (3g-1, 3g-2) for shifting enters the notch 10i (10i-1, 10i-2) by the biasing force of the elastic member, and one end of the shifting one-way clutch pawl 3g (3g-1, 3g-2) The clutch cam surface 3f (3f-1, 3f-2) is engaged. The cutout portions 10i (10i-1, 10i-2) do not face the shift clutch cam surfaces 3f-1, 3f-2 of the first clutch portion 3i-1 and the second clutch portion 3i-2 at the same time. Since the interval between the notches 10i (10i-1, 10i-2) arranged in the axial direction is determined, the one-way clutch pawl for shifting on the side where the notches 10i (10i-1, 10i-2) do not face 3g (3g-1, 3g-2) is prevented from engaging with the clutch clutch cam surface 3f (3f-1, 3f-2) by the shift sleeve 10b.

  The reverse input sleeve 10c is also movable in the axial direction of the axle 5 together with the speed change sleeve 10b. By operating the reverse input sleeve 10c to move in the axial direction, the notch 10h included in the reverse input sleeve 10c moves, but the notch 10h is always located on the reverse input clutch cam surface 2f.

The reverse input sleeve 10c can also be moved in the axial direction by moving the operation portion 10a in the axial direction.
The connection structure between the reverse input sleeve 10c and the operation portion 10a is the same as the connection structure between the transmission sleeve 10b and the operation portion 10a. The reverse input sleeve 10c is biased in the axial direction by a common elastic member 10d.

  Further, the notch 10h of the reverse input sleeve 10c can also be provided with a tapered surface at its circumferential end. The effect of the tapered surface is the same as that of the speed change sleeve 10b.

  With these configurations, during driving, the driving force from the sprocket 4 is transmitted to the driving wheels through the speed change mechanism 3, and when the forward drive is not driven, the sun gear 3a and the axle 5 are reversed by the reverse input one-way clutch 2. By being unable to rotate with respect to the input, the function of transmitting the reverse input torque from the drive wheel to the sprocket 4 can be exhibited.

  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 disposed on the opposite side of the rear sprocket 4.

  In this state, the shifting one-way clutch pawl 3g-1 and the shifting one-way clutch pawl 3g-2 of the second shifting one-way clutch 3i are separated from the bidirectional clutch cam surface 11 by the shifting sleeve 10b and the reverse input sleeve 10c. It has been.

With respect to the driving force from the rear sprocket 4, the first sun gear 3 a-1 and the second sun gear 3 a-2 are relatively rotatable around the axle 5. On the other hand, the planetary carrier 3c and the first sun gear 3a-1 are not rotatable 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 an operation from outside the axle 5, the shifting sleeve 10b and the reverse input sleeve 10c slide in the axial direction, and the first clutch portion 3i- The notch portion 10i of the shift sleeve 10b moves to the position of the one shift one-way clutch pawl 3g-1.

Thereby, the one-way clutch pawl 3g-1 for shifting of the first clutch portion 3i-1 is engaged with the bidirectional clutch cam surface 11, and the first sun gear 3a-1 is relative to the axle 5 with respect to the driving force. It becomes impossible to rotate.
At this time, at the position of the one-way clutch pawl 3g-2 for shifting of the second clutch portion 3i-2, the one-way clutch pawl 3g- for shifting of the bidirectional clutch cam surface 11 and the second clutch portion 3i-2 by the shifting sleeve 10b. 2 are separated. For this reason, the second sun gear 3 a-2 is rotatable around the axle 5.

  At this time, the one-way clutch pawl 3j for shifting of the first one-way clutch 3e contacts the tapered surface 10k of the first one-way clutch switching portion 10e and is pressed to the outer diameter side. Therefore, as shown in FIG. 4A, the shift one-way clutch pawl 3j is separated from the shift clutch cam surface 3k of the planet carrier 3c. For this reason, the planet carrier 3c and the first sun gear 3a-1 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 and the reverse input sleeve 10c are further slid in the axial direction to the left in the drawing.

  By this sliding, the notch portion 10i of the speed change sleeve 10b is moved to the position of the speed change one-way clutch pawl 3g-2 of the second clutch portion 3i-2. Thereby, the one-way clutch pawl 3g-2 for shifting of the second clutch part 3i-2 is engaged with the bidirectional clutch cam surface 11, 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 one-way clutch pawl 3g-1 for shifting of the first clutch portion 3i-1, the one-way clutch pawl 3g- for shifting of the bidirectional clutch cam surface 11 and the first clutch portion 3i-1 by the shifting sleeve 10b. 1 are separated. For this reason, the first sun gear 3 a-1 can rotate around the axis of the axle 5.

  Further, since the one-way clutch pawl 3j for shifting of the first one-way clutch 3e is separated from the shifting clutch cam surface 3k of the planetary carrier 3c by the first one-way clutch switching portion 10e, the planetary carrier 3c The first sun gear 3a-1 is relatively rotatable.

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 10d 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 3g (3g-1, 3g-2) for shifting, which is engaged with the bidirectional clutch cam surface 11, is strong by the tapered surface 10j provided at the axial end of the notch 10i. Thus, since the shifting sleeve 10b is easily returned, smooth switching is possible.

  FIGS. 7 and 8 show the state when the vehicle is not driven forward (at the time of reverse input from the tire). At this time, the rotation directions of the sun gears 3a-1 and 3a-2 with respect to the axle 5 are opposite to those when the driving force is applied.

In this state, as shown in FIG. 7, the reverse input one-way clutch pawl 2g of the reverse input one-way clutch 2 provided on the inner surface of the first sun gear 3a-1 It is located on the notch 10h of the sleeve 10c.
For this reason, the one-way clutch pawl 2g for reverse input is engaged with the bidirectional clutch cam surface 11, and the first sun gear 3a-1 is locked to the axle 5 against reverse input.

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.

  Although FIG. 7 shows the state of the first gear stage with respect to the transmission mechanism 3, the first sun gear 3a-1 is locked to the axle 5 with respect to the reverse input at any gear stage. The transmission path of the reverse input from is constant.

Although not shown, in the center motor unit, the driving force from the motor can be transmitted during assisting from the motor output shaft to the driving force transmission element, and from the driving force transmission 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 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 first sun gear 3a-1, but this is provided between the planet carrier 3c and the second sun gear 3a-2. May be.

  Further, in this embodiment, the same number of the shift sleeves 10b and the reverse input sleeves 10c are arranged along the circumferential direction. However, the number of the shift sleeves 10b can be relatively increased. .

  That is, as described above, in this embodiment, as shown in FIGS. 2B and 2C, the speed change sleeve 10b and the reverse input sleeve 10c are each “parts with members” along the circumferential direction. And “the part without the member” are intermittently provided, and the circumferential length of the “part with the member” and the circumferential length of the “part without the member” are the same in both the sleeves 10b and 10c. Is set. Also, the number of repeated repetitions is the same.

  For example, this may be set so that the total length in the circumferential direction is greater in the “portion with the member” of the shifting sleeve 10b than in the “portion with the member” of the reverse input sleeve 10c. it can. In order to achieve this, for example, the circumferential length of each "portion with the member" of the speed change sleeve 10b is equal to the circumference of the "portion with the member" of the reverse input sleeve 10c. If the length is the same as the length in the direction, the number of repetitions of intermittent engagement of the speed change sleeve 10b in the circumferential direction may be set larger than the number of repetitions of intermittent engagement of the reverse input sleeve 10c in the circumferential direction. it can. In this way, the time lag for gear change can be reduced, and an emphasis can be placed on the gear change.

  The axle 5 has a hole extending in the axial direction from one side in the axial direction, and the other axial end of the axle 5 is solid, but these are through holes extending over the entire axial length of the axle 5. It is good.

  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, the second gear shift one-way clutch 3i, and the reverse input one-way clutch 2 all employ ratchet clutches. As long as it can be controlled, a one-way clutch having another configuration such as a roller clutch or a sprag clutch may be employed.

1 Rear hub (hub)
2 Reverse input one-way clutch 2f Reverse input clutch cam surface 2g Reverse input one-way clutch pawl 3 Transmission mechanism 3a Sun gear 3a-1 First sun gear 3a-2 Second sun gear 3b Planetary gear 3c Planetary carrier 3d Outer ring gear 3e First shift one-way clutch 3f shift clutch cam surface 3g shift one-way clutch pawl 3i second shift one-way clutch 3i-1 first clutch portion 3i-2 second clutch portion 3j shift one-way clutch pawl 3k shift 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 Reverse input sleeve 10d Elastic member 10e First shift one-way clutch switching portion 10f Pin 10g Horizontal hole 10h, 10i Notch 10j, 10k Tapered surface 11 Concavity and convexity (bidirectional clutch cam surface)
13, 14, 15 Bearing part

Claims (18)

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 reverse input one-way clutch (2) is provided between the sun gear (3a) and the axle (5), and the reverse input one-way clutch (2) is used for reverse input from the drive wheels. On the other hand, the sun gear (3a) has a function of making the sun gear (3a) unrotatable around the axle (5), and reverse input from the drive wheel can be transmitted from the hub case (7) to the sprocket (4). A motor-assisted bicycle equipped with a hub (1).   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, wherein:   The battery-assisted bicycle according to claim 1 or 2, wherein the first speed change one-way clutch (3e) is a ratchet clutch.   4. The battery-assisted bicycle according to claim 1, wherein the one-way clutch for second speed change (3 i) and the one-way clutch for reverse input (2) are constituted by a ratchet clutch. 5.   The second shift one-way clutch (3i) includes a shift one-way clutch pawl (3g) provided on the sun gear (3a) and a shift clutch cam surface (3f) provided on the outer surface of the axle (5). The reverse input one-way clutch (2) includes a reverse input one-way clutch pawl (2g) provided on the sun gear (3a) and a reverse input provided on the outer surface of the axle (5). The battery-assisted bicycle according to claim 4, further comprising a clutch cam surface (2f).   Concavities and convexities (11) exhibiting both functions of the shift clutch cam surface (3f) of the second shift one-way clutch (3i) and the reverse input clutch cam surface (2f) of the reverse input one-way clutch (2). ) Is provided on the outer periphery of the axle (5).   The shift control mechanism (10) includes a shift sleeve (10b) having a notch (10i) around the axle (5), and the shift sleeve (10b) moves in the axial direction of the axle (5). When the shift sleeve (10b) is moved and operated in the axial direction, the notch (10i) is positioned on the shift clutch cam surface (3f) of the second shift one-way clutch (3i). And a position retracted from the position of the shift clutch cam surface (3f) of the second shift one-way clutch (3i), and by the movement, the second shift one-way clutch (3i) is switched. The battery-assisted bicycle according to claim 5 or 6, characterized in that:   The first shifting one-way clutch (3e) is provided on the inner surface of the planetary carrier (3c) and the shifting one-way clutch pawl (3j) supported on the outer surface of the sun gear (3a) so as to be swingable. A shift clutch cam surface (3k), the shift sleeve (10b) includes a first shift one-way clutch switching portion (10e), and the shift sleeve (10b) is moved in the axial direction. Accordingly, the first shift one-way clutch switching portion (10e) moves between a position retracted from the shift one-way clutch pawl (3j) and a position in contact with the shift one-way clutch pawl (3j). The battery-assisted bicycle according to claim 7, wherein the first-speed one-way clutch (3 e) is switched by the movement.   The notch (10i) of the speed change sleeve (10b) has a tapered surface (10j) gradually approaching the outer diameter side toward the outer side in the axial direction at the axial end edge thereof, and the tapered surface (10j) 9. The battery-assisted bicycle according to claim 7, wherein a shift one-way clutch pawl (3 g) of the second shift one-way clutch (3 i) is in contact with the second shift one-way clutch (3 i).   The first speed change one-way clutch switching portion (10e) of the speed change sleeve (10b) is gradually increased in diameter toward the axial end thereof as it approaches the first speed change one-way clutch (3e) along the axial direction. A taper surface (10k) that approaches the taper surface (10k), wherein the one-way clutch pawl (3j) for shifting of the first gear-shifting clutch (3e) abuts on the tapered surface (10k). The battery-assisted bicycle according to any one of the above.   The shift control mechanism (10) includes a reverse input sleeve (10c) having a notch (10h) around the axle (5), and the reverse input sleeve (10c) is in the axial direction of the axle (5). Even if the reverse input sleeve (10c) is moved in the axial direction, the notch (10h) always keeps the reverse input clutch cam surface (2) of the reverse input one-way clutch (2). The battery-assisted bicycle according to any one of claims 6 to 10, which is located at a position 2f). The speed change sleeve (10b) and the reverse input sleeve (10c) pass through the axle (5) and one end thereof is pulled out of the axle (5) by an operating portion (10a). (5) The battery-assisted bicycle according to claim 11, wherein a movement operation in the axial direction is possible from the outside.   The battery-assisted bicycle according to claim 12, wherein the shift sleeve (10b) and the reverse input sleeve (10c) are urged in an axial direction by an elastic member (10d).   14. The sprocket (4) is disposed closer to one axial direction in the hub case (7), and the shift control mechanism (10) is disposed closer to the other axial direction. Electric assist bicycle.   The shift sleeve (10b) and the reverse input sleeve (10c) are provided intermittently along the circumferential direction, and the second shift one-way clutch (3i) in the shift sleeve (10b). And a portion covering the reverse input one-way clutch pawl (2g) of the reverse input one-way clutch (2) in the reverse input sleeve (10c) in the circumferential direction. The battery-assisted bicycle according to any one of claims 11 to 14, wherein the bicycle is alternately disposed along the battery.   A portion of the shift sleeve (10b) covering the shift one-way clutch pawl (3g) of the second shift one-way clutch (3i), and the reverse input one-way clutch (2) in the reverse input sleeve (10c) The portions that cover the one-way clutch pawl (2g) for reverse input are located on both sides of the axle (5) and are 90 ° out of phase with each other around the axle (5). The battery-assisted bicycle according to claim 15, wherein the battery-assisted bicycle is disposed in the vehicle.   The speed change sleeve (10b) and the reverse input sleeve (10c) are provided intermittently along the circumferential direction, and the number of repetitions of the reverse input sleeve (10c) in the circumferential direction is repeated. The battery-assisted bicycle according to any one of claims 11 to 14, wherein a greater number of repetitions of the intermittent in the circumferential direction is set in the shift sleeve (10b).   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 17.

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