JP2012025332A - Power-assisted bicycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a center motor type power-assisted bicycle with a regeneration mechanism, for securing a great gear ratio (a speed increasing ratio) without increasing the outer diameter of a device in a hub of a driving wheel.SOLUTION: In the hub of the driving wheel, a first planetary gear mechanism and a second planetary gear mechanism are provided in parallel to each other along the axial direction of an axle for enabling a speed change in three stages, namely, a low speed condition in which driving force is transmitted from the input side directly to a hub case, a first speed increasing condition in which the driving force is transmitted from the input side to the hub case via either the first planetary gear mechanism or the second planetary gear mechanism for a speed increase, and a second speed increasing condition in which the driving force is transmitted from the input side to the hub case via the first planetary gear mechanism and the second planetary gear mechanism for a speed increase.

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 having a function of effectively using running energy and charging the battery by regenerative power generation 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, a drive wheel, an output shaft of the motor, By direct connection, 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 battery (secondary battery) to the motor tends to be long, and the wiring to the secondary battery tends to be complicated. Further, when the motor is arranged on the front side, the operability is deteriorated, and when the motor is arranged on the rear side, there is a problem that compatibility with the transmission becomes difficult.

  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, the first one-way clutch is provided between the motor output shaft and the drive sprocket, the second one-way clutch is provided between the pedal crankshaft to which the pedal force is input and the drive sprocket, and the brake operation is further performed. 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 rear wheel can be transmitted to the motor during regeneration (see, for example, Patent Document 4).

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, the output of the motor can be transmitted to the rear wheels by locking the two-way clutch in the forward rotation direction, 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 rear wheel side can be transmitted to the motor. This enables regenerative power generation and brake assist. In this configuration, since it is necessary to transmit the reverse input torque from the rear wheel side to the motor side during regeneration, the rear hub and the rear sprocket are directly connected (for example, see Patent Document 5).

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

By the way, a general bicycle speed change mechanism is a system in which a multistage sprocket is provided on the same axis of one or both of a crankshaft and a rear axle, and a chain is moved between sprockets by a derailleur (external gear change). Machine) and a system (internal transmission) that changes gears by changing gears provided inside the rear hub.
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, battery-assisted bicycles are developed mainly in the city cycle, and most of them adopt an internal transmission.

  In this regard, in Patent Document 4 and Patent Document 5 described above, since the rear hub and the rear sprocket are directly connected, it is not possible to cope with the internal transmission.

  Further, a one-way clutch is usually provided in the internal transmission to cope with inertial running. For this reason, even if the structure is applied as it is to a battery-assisted bicycle having a regeneration mechanism, the reverse input from the rear wheel is not transmitted from the rear hub to the rear sprocket. That is, since the one-way clutch rotates idly, the center motor cannot be rotated and regenerated by reverse input from the rear wheels.

  In order to cope with reverse input, for example, it is possible to connect the rear wheel to the crankshaft and the rear wheel to the motor shaft with separate power transmission elements, but using two transmission elements in terms of layout In addition, the product value is greatly reduced in terms of cost.

  Therefore, in Patent Document 6, in a center-motor-type battery-assisted bicycle equipped with an internal transmission, a reverse mechanism from a rear wheel is connected to a chain by a reverse mechanism by providing a transmission mechanism and a reverse input clutch on a rear hub. Regenerative power generation is possible by being transmitted to the motor via

  In this battery-assisted bicycle, the speed change mechanism uses a planetary gear mechanism and is a speed increasing type in which an input is transmitted at a constant speed or higher, or a speed reducing type in which an input is transmitted at a constant speed or lower.

  In the case of the speed increasing type, the planetary carrier is used as an input, and a direct connection state in which the driving force is transmitted to the wheels (hub case) through the driving one-way clutch provided between the planet carrier and the hub case can be achieved. In addition, planetary gears having a plurality of gear portions with different numbers of teeth are engaged with sun gears provided around the axles, respectively, and transmission clutches provided between the sun gears and the axles that are engaged with the respective gear portions are provided. By switching, a plurality of speed increasing states are switched.

  Further, the reverse input transmission clutch (hereinafter referred to as “reverse input clutch”) is provided between the sun gear fixed to the axle and the axle when the speed ratio is the highest.

  In this configuration, if a normal one-way clutch is used as the reverse input clutch, the reverse input clutch engages and the wheel locks when attempting to move backward (when the bicycle is pushed backward by hand). End up. For this reason, it will be in the state which cannot reverse. In order to avoid such a situation, a mechanism for releasing (not engaging) the reverse input clutch at the time of reverse is necessary.

JP-A-8-140212 JP 2003-166563 A Japanese Patent Laid-Open No. 10-250673 JP 2001-213383 A JP 2004-268843 A JP 2010-095203 A

  In the configuration disclosed in Patent Document 6, the transmission mechanism uses a planetary gear having a plurality of gear portions having different numbers of teeth. For this reason, when trying to increase the gear ratio (speed increasing ratio), the outer diameter tends to increase.

  As a mechanism for releasing (not engaging) the reverse input clutch at the time of reverse, for example, a structure that automatically switches using the rotation of the hub case at the time of reverse can be adopted. However, in this case, depending on the state of each clutch, the reverse input clutch may be locked before being released, and after that, there is a possibility that it cannot be switched. Further, for example, in the case of a mechanism for manually switching, it is inconvenient to perform a switching operation each time when the vehicle moves backward.

  In view of this, the present invention provides a center-motor-type battery-assisted bicycle equipped with a regenerative mechanism that secures a large gear ratio (speed increase ratio) without increasing the outer diameter of the device in the hub of the drive wheels. As a second problem, a second problem is to enable easy switching to a state in which the engagement of the reverse input clutch is released (not engaged) during reverse.

  In order to solve the first problem, the present invention attaches a secondary battery and an auxiliary drive motor to a frame connecting the front wheel and the rear wheel, and drives the pedal by the pedaling force transmitted from the crankshaft or the output of the motor. A regenerative mechanism that allows power to be transmitted to the drive wheels via a drive force transmission element, and that reduces regenerative power generated by reverse input from the drive wheels to the output shaft of the motor to the secondary battery during forward non-drive. The motor-assisted bicycle includes a transmission mechanism, a reverse input one-way clutch, and a clutch switching device inside a hub provided on the drive wheel, wherein the transmission mechanism includes at least two planets arranged in parallel along the axial direction of the axle. The first planetary gear mechanism, which is one of the planetary gear mechanisms, includes a first sun gear provided around the axle, a first planetary gear meshing with the first sun gear, and the first planetary gear mechanism. The second planetary gear mechanism, which has a first planet carrier that holds the first planetary gear and is another planetary gear mechanism, includes a second sun gear provided around the axle and a second sun gear that meshes with the second sun gear. A second planetary gear and a second planetary carrier that holds the second planetary gear, and the speed change mechanism is capable of relatively rotating the first sun gear and the second sun gear around the axle with respect to the driving force, or A shift one-way clutch that can be switched to be relatively non-rotatable, and a shift control mechanism that performs the switching of the shift one-way clutch, and the second planet carrier includes a first outer ring gear that meshes with the first planet gear. The hub case rotates integrally with a second outer ring gear meshing with the second planetary gear, and the first sun gear and the front gear are rotated by the speed change control mechanism. By making one of the second sun gears non-rotatable relative to the axle with respect to the driving force and making the other rotatable relative to the axle, the driving force is transferred from the first planet carrier to the first planetary gear mechanism or the second The first speed increasing state that is increased through one of the planetary gear mechanisms and transmitted to the hub case, and both the first sun gear and the second sun gear cannot be rotated relative to the axle with respect to the driving force. As a result, the driving force can be shifted from the first planetary carrier to the second acceleration state in which the driving force is increased through the first planetary gear mechanism and the second planetary gear mechanism and transmitted to the hub case. The one-way clutch for reverse input is provided between the first sun gear and the second sun gear and the axle in each planetary gear mechanism, and when the forward drive is not driven, the clutch switching device Operate By making the at least one sun gear non-rotatable around the axle with respect to the reverse input from the driving wheel, the reverse input from the driving wheel can be transmitted from the hub case to the driving force transmitting element. It was a battery-assisted bicycle with a hub.

  In this way, at least two planetary gear mechanisms, that is, the first planetary gear mechanism and the second planetary gear mechanism are arranged in parallel along the axial direction of the axle, and the driving force is changed from the input side to the first planetary gear mechanism or the second planetary gear mechanism. The first acceleration state is increased through one of the planetary gear mechanisms and transmitted to the hub case, and is accelerated from the input side via the first planetary gear mechanism and the second planetary gear mechanism and transmitted to the hub case. By making it possible to shift to the second speed increasing state, it is possible to obtain a larger gear ratio while maintaining a compact configuration that does not increase the size of the device in the radial direction.

This is because when the planetary carrier is input, the outer ring gear is output, and the sun gear is fixed, the speed increasing ratio is (a + d) / d, where the number of teeth of the sun gear is d and the number of teeth of the outer ring gear is d. When the number of teeth of the sun gear is fixed, the speed increase ratio becomes larger as the number of teeth of the outer ring gear decreases.
That is, by arranging the first planetary gear mechanism and the second planetary gear mechanism in parallel along the axial direction of the axle, the corresponding outer ring gear can be set separately for each planetary gear mechanism. When each of the mechanisms employs a single planetary gear (not having a plurality of gears), the smaller the outer diameter of the outer ring gear meshing with the planetary gear (the smaller the number of teeth of the outer ring gear), the greater the increase. Since the speed ratio is increased, a large gear ratio can be obtained even with a compact configuration in which the outer diameter of the outer ring gear is small.

  In order to solve the above second problem, in the present invention, the clutch switching device can engage the reverse input one-way clutch with respect to the reverse input in conjunction with the brake operation. Adopted a configuration to switch to a different state.

That is, if the brake is operated (when the brake is in effect), the one-way clutch for reverse input can be engaged with the reverse input, and if the brake is released (the brake is not effective) In this state, the one-way clutch for reverse input cannot be engaged with the reverse input.
As a result, the reverse input one-way clutch will not be in an engageable state unless the brake is operated even during reverse, so that the function does not interfere with other clutches and the vehicle can reverse.

  In each of these configurations, a first one-way clutch is provided between the first planet carrier and the second planet carrier, and a second one-way clutch is provided between the second planet carrier and the hub case. By making the first sun gear and the second sun gear rotatable relative to the axle with respect to the driving force, the driving force is transmitted from the first planet carrier to the hub case via the first one-way clutch and the second one-way clutch. It is possible to adopt a configuration that allows shifting to a low speed state that is transmitted directly to the vehicle.

  According to this configuration, in addition to the first acceleration state and the second acceleration state described above, the driving force is transmitted from the first planet carrier to the hub case via the first one-way clutch and the second one-way clutch. A total of three speeds in the low speed state (direct connection state) can be realized.

The reverse input one-way clutch needs to be provided between the sun gear and the axle for all the planetary gear mechanisms arranged in parallel.
That is, it is necessary to provide a reverse input one-way clutch between the sun gears and the axles of the planetary gear mechanisms arranged in parallel. However, in each planetary gear mechanism, when the planetary gear has a plurality of gear portions, it is desirable to provide between the sun gear meshing with the gear portion having the smallest number of teeth and the axle.

  For example, in a configuration in which two planetary gear mechanisms are arranged in parallel, the one-way clutch for reverse input includes a first one-way clutch for reverse input provided between the first sun gear and the axle, and the second sun gear. And the second one-way clutch for reverse input provided between the first axle and the axle. When the forward drive is not driven, the first one-way clutch for reverse input and the second one-way clutch for reverse input are reversed by the clutch switching device. By switching to a state in which the input can be engaged, a reverse input from the hub case can be transmitted to the driving force transmission element.

  In addition, the first planetary gear mechanism and the second planetary gear mechanism are configured by the same planetary gear mechanism, that is, the sun gear, the planetary gear, and if possible, the same gear specifications. By using an outer ring gear composed of the above-mentioned gear specifications, it is possible to share the parts of both planetary gear mechanisms and realize cost reduction.

  In each of these configurations, the first one-way clutch and the second one-way clutch can be configured by a ratchet clutch. Further, the first one-way clutch and the second one-way clutch can be constituted by a roller clutch or a sprag clutch.

  Further, the reverse input one-way clutch may employ a configuration such as a sprag clutch or a roller clutch. In particular, a configuration including a ratchet clutch may be employed.

When a ratchet clutch is employed as the one-way clutch for reverse input, for example, the following configuration can be employed as the clutch switching device.
In other words, the clutch switching device has a reverse input operation unit pulled out through the axle, and the reverse input one-way clutch is switched by moving the reverse input operation unit in the axial direction. It is the structure which is made. According to this configuration, the reverse input one-way clutch can be switched from the outside by a simple mechanism.

The reverse input one-way clutch has a swingable reverse input clutch pawl provided on the outer surface of the axle, and a reverse input clutch cam surface engaged with the reverse input clutch pawl provided on the inner surface of the sun gear. A configuration can be adopted.
According to this configuration, the number of engaging grooves on the clutch cam surface of the one-way clutch for reverse input can be easily secured, so that the free angle of the clutch (time lag until engagement) can be reduced. That is, it is more advantageous to provide the clutch cam surface on the sun gear side having a larger diameter than to provide the clutch cam surface on the axle side.

  The reverse input clutch pawl may be urged by an elastic member so that one end of the reverse input clutch pawl rises toward the reverse input clutch cam surface, and the other end contacts a reverse input sleeve provided on the outer periphery of the axle. When the reverse input operation portion is moved in the axial direction, the notch portion provided in the reverse input sleeve moves the position of the reverse input clutch pawl and the reverse input clutch pawl. It is possible to adopt a configuration in which the one-way clutch for reverse input can be switched by moving between each position and the retracted position.

Further, the reverse input sleeve moves in the axial direction of the axle so that the cutout portion is moved, and approaches the outer diameter side toward the axially outer end of the cutout portion. A configuration in which a tapered surface is provided can be employed.
According to this configuration, when the clutch pawl bitten on the clutch cam surface and the cutout portion come into contact with each other, the force to remove the clutch pawl from the cam surface can be increased by the inclined surface of the tapered surface. it can.
In addition, when the reverse input sleeve moves in the direction around the axis of the axle to move the notch, a tapered surface can be provided at the circumferential edge of the notch of the speed change sleeve. .

  In addition, as the one-way clutch for shifting, a configuration such as a sprag clutch or a roller clutch may be employed, but in particular, a configuration including a ratchet clutch may be employed.

  For example, in a configuration in which two planetary gear mechanisms are arranged in parallel, the one-way clutch for shifting includes a first one-way clutch for shifting provided between the first sun gear and the axle, the second sun gear, and the In the case where the second one-way clutch for shifting provided between the axle and the axle is included, each of the first one-way clutch for shifting and the second one-way clutch for shifting can be constituted by a ratchet clutch.

  In this configuration, the shift control mechanism has a shift operation unit that is pulled out through the axle, and moves the shift operation unit in the axial direction so that the first one-way clutch for shifting and A configuration in which the second one-way clutch for shifting can be switched can be employed. According to this configuration, the shift one-way clutch can be switched from the outside by a simple mechanism.

Further, in this configuration, the first shift one-way clutch has a first shift clutch clutch surface in which the first clutch pawl for swinging meshes with the outer surface of the axle and the first clutch pawl for shifting. The shift second one-way clutch is provided on the inner surface of the first sun gear, and the second shift one-way clutch has a second shift clutch pawl that can swing freely and the second clutch pawl for shifting meshes with the outer surface of the axle. A configuration in which a two-clutch cam surface is provided on the inner surface of the second sun gear can be employed.
According to this configuration, in each of the first one-way clutch for shifting and the second one-way clutch for shifting, it is easy to secure the number of engaging grooves on the clutch cam surface, so the free angle of the clutch (time lag until engaging) Can be reduced. That is, it is more advantageous to provide the clutch cam surface on the sun gear side having a larger diameter than to provide the clutch cam surface on the axle side.

  The first clutch pawl for shifting and the second clutch pawl for shifting are each urged by an elastic member so that one end thereof rises toward the first clutch cam surface for shifting or the second clutch cam surface for shifting. The other end can come into contact with the speed change sleeve provided on the outer periphery of the axle, and the notch portion provided in the speed change sleeve is provided by the movement operation of the speed change operation portion in the axial direction. , By moving between the position of the first clutch pawl for shifting and the second clutch pawl for shifting and the position retracted from the first clutch pawl for shifting and the second clutch pawl for shifting, respectively. A configuration in which the first one-way clutch and the second one-way clutch for shifting can be switched can be adopted.

The shift sleeve moves in the axial direction of the axle so that the notch is moved, and a tapered surface that approaches the outer diameter side toward the outer side in the axial direction is formed at the axial end of the notch. The provided configuration can be employed.
According to this configuration, when the clutch pawl bitten on the clutch cam surface comes into contact with the cutout portion, the force for removing the clutch pawl from the cam surface can be increased by the inclined surface of the tapered surface.
In addition, when the shift sleeve moves in the direction around the axle, the notch is moved, and a tapered surface can be provided at the circumferential edge of the notch of the shift sleeve.

  In these configurations, a bidirectional first clutch cam portion having functions of both the first clutch cam surface for shifting and the first clutch cam surface for reverse input is provided on the inner surface of the first sun gear, The structure which provided the bi-directional 2nd clutch cam part which has a function of both the 2nd clutch cam surface for said and the 2nd clutch cam surface for said reverse inputs on the inner surface of said 2nd sun gear can be employ | adopted.

  That is, a bidirectional first clutch cam portion having both functions of a first clutch cam surface for shifting and a first clutch cam surface for reverse input is provided on the inner surface of the first sun gear, and the shifting is performed on the inner surface of the second sun gear. By providing a bi-directional second clutch cam part that functions as both a second clutch cam surface for use and a second clutch cam surface for reverse input, the first one-way clutch for shifting and the reverse input use are provided at positions overlapping in the axial direction. A first one-way clutch, a second one-way clutch for shifting, and a second one-way clutch for reverse input can be arranged. For this reason, the structure of a more compact apparatus is attained.

  In addition, a first one-way clutch for shifting and a first one-way clutch for reverse input, and a second one-way clutch for shifting and a second one-way clutch for reverse input can be arranged at the same position in the axial direction. At this time, the first clutch pawl for shifting and the first clutch pawl for reverse input, and the second clutch pawl for shifting and the second clutch pawl for reverse input are in the same position with respect to the axial direction of the axle, respectively. To place.

  The present invention relates to a center motor-type battery-assisted bicycle equipped with a regenerative mechanism, in which at least two planetary gear mechanisms, that is, a first planetary gear mechanism and a second planetary gear mechanism are driven in parallel along the axial direction of the axle. A first acceleration state in which force is accelerated from the input side via either the first planetary gear mechanism or the second planetary gear mechanism and transmitted to the hub case, and the first planetary gear mechanism and the second planetary gear mechanism are input from the input side. By making it possible to shift to the second speed-up state where the speed is increased via the planetary gear mechanism and transmitted to the hub case, a large gear ratio is obtained without increasing the outer diameter of the device in the hub of the drive wheel. It becomes possible.

  In addition, the clutch switching device adopts a configuration that switches the one-way clutch for reverse input to a state in which it can be engaged with reverse input in conjunction with the brake operation. Can be easily switched to a state of releasing (not engaging).

Sectional drawing of the hub which shows the 1st speed change stage (direct connection state) of embodiment of this invention 1A is a cross-sectional view taken along line AA in FIG. 1, FIG. 1B is a cross-sectional view taken along line BB, FIG. 1C is a cross-sectional view taken along line CC, and FIG. Sectional drawing of the hub which shows the 2nd speed change (1st speed increase) of embodiment of this invention 3A is a sectional view taken along the line AA in FIG. 3, FIG. 3B is a sectional view taken along the line BB, FIG. 3C is a sectional view taken along the line CC, and FIG. Sectional drawing of the hub which shows the 3rd speed change (2nd speed increase) of embodiment of this invention 5A is a cross-sectional view taken along line AA in FIG. 5, FIG. 5B is a cross-sectional view taken along line BB, FIG. 5C is a cross-sectional view taken along line CC, and FIG. Sectional drawing of the hub which shows the time of forward non-drive (regenerative state) of embodiment of this invention 7A is a cross-sectional view taken along the line AA in FIG. 7, FIG. 7B is a cross-sectional view taken along the line BB, FIG. 7C is a cross-sectional view taken along the line CC, and FIG. Overall view of a battery-assisted bicycle

  An embodiment of the present invention will be described with reference to FIGS. The battery-assisted bicycle of this embodiment is a center motor unit in which a secondary battery and an auxiliary drive motor are built in a frame F connecting the front wheel 22 and the rear wheel 25 in the vicinity of the center between the front wheel 22 and the rear wheel 25. C is a center motor system attached.

  At the time of driving, for example, when the pedaling force transmitted from the crankshaft 21 is input through the pedal 20 shown in FIG. 9, the front sprocket 24 and the rear wheel 25 sprocket 4 (hereinafter referred to as “rear sprocket 4”). The driving force can be transmitted to the rear wheel 25 via a power transmission element such as a chain 23 that connects the two wheels.

  When the forward drive is not driven, a reverse input is transmitted from the hub 1 of the rear wheel 25 (hereinafter referred to as “rear hub 1”) to the output shaft of the motor, and the regenerative electric power generated by the reverse input is used as the center motor unit. A regenerative mechanism is provided that returns to the C secondary battery. The regeneration mechanism is attached to the frame F around the center motor unit C and the battery 26.

  As shown in FIG. 1, the rear hub 1 includes a transmission mechanism 3 constituted by a planetary gear mechanism, a reverse input one-way clutch 2, and a reverse input thereof in a hub case 7 provided coaxially with the axle 5 of the rear wheel 25. A clutch switching device 9 for controlling the one-way clutch 2 is provided. The axle 5 is fixed to the frame F so as not to rotate.

  The structure of the speed change mechanism 3 includes a first planetary gear mechanism 3p-1 and a second planetary gear mechanism 3p-2 arranged in parallel along the axial direction of the axle 5 as two planetary gear mechanisms 3p. In this embodiment, the speed change mechanism 3 enables a total of three speeds including direct connection and two speeds.

  The first planetary gear mechanism 3p-1 is a first sun gear 3a-1 provided around the axle 5, a first planetary gear 3b-1 meshing with the first sun gear 3a-1, and the first planetary gear. The first planet carrier 3c-1 holding the gear 3b-1 is provided.

  The second planetary gear mechanism 3p-2 includes a second sun gear 3a-2 provided around the axle 5, a second planetary gear 3b-2 that meshes with the second sun gear 3a-2, and the second planetary gear 3b-2. It has the 2nd planet carrier 3c-2 holding planetary gear 3b-2.

  Between the first planet carrier 3c-1 and the axle 5, between the first planet carrier 3c-1 and the hub case 7, and between the hub case 7 and the axle 5, there are bearing portions 13, 14, 13 respectively. Is provided. The first planet carrier 3c-1 and the axle 5, the first planet carrier 3c-1 and the hub case 7, and the hub case 7 and the axle 5 are supported by the bearing portions 13, 14, and 13 so as to be relatively rotatable. Yes.

  Furthermore, the speed change mechanism 3 can change the first sun gear 3 a-1 and the second sun gear 3 a-2 with respect to the driving force so that each of the first sun gear 3 a-1 and the second sun gear 3 a-2 can be rotated relative to the axle 5. A clutch 3e and a shift control mechanism 10 for switching the shift one-way clutch 3e are provided.

The one-way clutch for shifting 3e is provided between the first one-way clutch for shifting 3e-1 provided between the first sun gear 3a-1 and the axle 5, and between the second sun gear 3a-2 and the axle 5. And a second one-way clutch for shifting 3e-2.
In this embodiment, the first shift one-way clutch 3e-1 and the second shift one-way clutch 3e-2 are constituted by a ratchet clutch (ratchet mechanism).

  When three or more planetary gear mechanisms 3p are arranged in parallel in the axial direction of the axle 5, the speed change one-way clutch 3e corresponds to the number of planetary gear mechanisms 3p arranged in parallel, that is, the number of sun gears 3a. The same number is provided. The sun gears 3a of all the planetary gear mechanisms 3p are each provided with a shift one-way clutch 3e between the sun gear 3a and the axle 5.

  The first shifting one-way clutch 3e-1 has a first shifting clutch claw 3f-1 that is swingable about an axis of a swinging shaft (clutch pawl shaft) 3i fixed to the axle 5 on the outer surface of the axle 5. A first clutch cam surface 3g-1 for shifting with which the first clutch pawl 3f-1 for shifting is engaged is provided on the inner surface of the first sun gear 3a-1 (see FIG. 2A).

  The second shift one-way clutch 3e-2 has a second shift clutch claw 3f-2 that can swing around the swing shaft 3i fixed to the axle 5 on the outer surface of the axle 5, and the second clutch for shifting. A second clutch cam surface 3g-2 for shifting with which the claw 3f-2 meshes is provided on the inner surface of the second sun gear 3a-2 (see FIG. 2B).

The speed change control mechanism 10 has a speed change operation part 10a drawn out through the axle 5 and a speed change sleeve 10b connected to the speed change operation part 10a.
By operating the shift operation portion 10a to move in the axial direction, the first shift one-way clutch 3e-1 and the second shift one-way clutch 3e-2 are engaged or disengaged through the shift sleeve 10b. And can be switched. In other words, the first sun gear 3a-1 and the second sun gear 3a-2 can be switched to be rotatable relative to the axle 5 or not rotatable relative to the driving force.

  The operation will be described in more detail. The first clutch pawl 3f-1 for shifting and the second clutch pawl 3f-2 for shifting are shifted at their first clutch cam surface 3g-1 by an elastic member (not shown). Alternatively, a load is applied in the direction of rising toward the second clutch cam surface 3g-2 for shifting. On the other hand, the other end is in contact with the speed change sleeve 10b in the speed change control mechanism 10, and against the elastic force of the elastic member, the speed change first clutch cam surface 3g-1 or the speed change second clutch cam surface 3g. -2 side is suppressed from rising (for example, refer to FIGS. 2A and 2B).

  Here, the shift sleeve 10 b is provided with two notches 10 d along the axial direction of the axle 5. When the speed change operation portion 10a drawn out through the axle 5 is moved in the axial direction by an external operation from outside the axle 5, the speed change sleeve 10b is also moved in the axial direction, and the notch 10d is used for speed change. It moves to the position of the first clutch pawl 3f-1, the second clutch pawl 3f-2 for shifting, or both positions.

  Then, the shifting first clutch pawl 3f-1 and the shifting second clutch pawl 3f-2 facing the notch 10d are released from the restraint by the shifting sleeve 10b, and one end of the shifting first clutch pawl 3f-1 is shifted to the first clutch cam for shifting. It rises to the side of the surface 3g-1 and the second clutch cam surface 3g-2 for shifting, and can be engaged with the driving force. For example, FIGS. 4A and 4B show that only the second clutch claw 3f-2 for shifting out of the first clutch claw 3f-1 for shifting and the second clutch claw 3f-2 for shifting rises and is engaged. FIGS. 6 (a) and 6 (b) show that both the first clutch pawl 3f-1 for shifting and the second clutch pawl 3f-2 for shifting rise, It shows that it has become.

  A tapered surface 10e is provided at one axial end of the notch 10d. The tapered surface 10e is engaged with the first clutch claw surface 3g-1 and the second clutch cam surface 3g-2 for transmission. When trying to release the engagement from the combined state, the taper surface 10e contacts one end of each of the clutch claws 3f-1 and 3f-2, thereby smoothly releasing the engagement. That is, by the inclined surface of the tapered surface 10e, it is possible to increase the force for removing the clutch pawls 3f-1, 3f-2 from the cam surfaces 3g-1, 3g-2.

  The speed change operation unit 10a has a shaft shape, is inserted in a shaft hole 5b provided in the axle shaft 5 so as to freely advance and retract, and is urged outward in the axial direction by an elastic member 10g. Therefore, the movement operation in the axial direction of the speed change operation portion 10a is performed against the urging force of the elastic member 10g when the speed change operation portion 10a is pushed into the hub 1, and when the force to be pushed is released, The shift operation unit 10a automatically returns to the original state by the biasing force.

  The speed change sleeve 10b is fixed to the axle 5 by a pin 10f inserted into a lateral hole 10c provided in the axle 5. The shifting sleeve 10b can be moved in the axial direction by moving the pin 10f in the axial direction within the lateral hole 10c by the shifting operation portion 10a.

  A first one-way clutch 3k is provided between the first planet carrier 3c-1 and the second planet carrier 3c-2. Further, a second one-way clutch 3m is provided between the second planet carrier 3c-2 and the hub case 7.

  The second planet carrier 3c-2 is formed integrally with a first outer ring gear 3d-1 that meshes with the first planetary gear 3b-1, but the second planet carrier 3c-2 and the first outer ring gear 3d-1 are formed. May be formed as separate bodies and connected together by a spline or the like to rotate together.

  The hub case 7 is integrally formed with a second outer ring gear 3d-2 that meshes with the second planetary gear 3b-2. The second planetary gear 3b-2 and the second outer ring gear 3d-2 are separated from each other. You may make it rotate integrally by forming in a body and combining these with a spline etc.

  The first one-way clutch 3k is provided on the outer surface of the first planet carrier 3c-1 and on the inner surface of the second planet carrier 3c-2, and the first clutch pawl 3q meshes with the first clutch pawl 3q. A cam surface 3n is provided. One end of the first clutch pawl 3q is urged by an elastic member (not shown) in a direction to rise toward the first clutch cam surface 3n (see FIG. 2C).

  The second one-way clutch 3m includes a second clutch pawl 3r provided on the outer surface of the second planet carrier 3c-2 and a second clutch cam surface 3s provided on the inner surface of the hub case 7 and meshed with the second clutch pawl 3r. ing. One end of the second clutch pawl 3r is biased by an elastic member (not shown) in a direction to rise toward the second clutch cam surface 3s. (See Fig. 2 (d))

The one-way clutch for reverse input 2 is provided between the first one-way clutch for reverse input 2a-1 provided between the first sun gear 3a-1 and the axle 5, and between the second sun gear 3a-2 and the axle 5. And a second input one-way clutch 2a-2 for reverse input.
The reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 are constituted by ratchet clutches.

  When three or more planetary gear mechanisms 3p are arranged in parallel in the axial direction of the axle 5, the reverse input one-way clutch 2 corresponds to the number of planetary gear mechanisms 3p arranged in parallel, that is, the number of sun gears 3a. It is possible to employ the same number of configurations. The sun gears 3 a of all the planetary gear mechanisms 3 p are each provided with the reverse input one-way clutch 2 between the axle 5.

  The reverse input first one-way clutch 2 a-1 has a reverse input first clutch pawl 2 c-1, which can swing around the swing shaft 2 d fixed to the axle 5, on the outer surface of the axle 5. A first clutch cam surface 2b-1 for shifting with which the first clutch pawl 2c-1 meshes is provided on the inner surface of the first sun gear 3a-1 (see FIG. 2A).

  The reverse input second one-way clutch 2 a-2 has a reverse input second clutch pawl 2 c-2, which can swing around the swing shaft 2 d fixed to the axle 5, on the outer surface of the axle 5. A second clutch cam surface 2b-2 for reverse input with which the second clutch pawl 2c-2 meshes is provided on the inner surface of the second sun gear 3a-2 (see FIG. 2B).

  The clutch switching device 9 has a reverse input operation unit 9a drawn out through the axle 5 and a reverse input sleeve 9b connected to the reverse input operation unit 9a. By operating the reverse input operation portion 9a to move in the axial direction, the reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 are engaged with each other through the reverse input sleeve 9b. The state is switched to the disengageable state. That is, the first sun gear 3a-1 and the second sun gear 3a-2 can be switched to be rotatable relative to the axle 5 or not rotatable relative to the reverse input from the drive wheels.

  The operation will be described in more detail. The first clutch claw 2c-1 for reverse input and the second clutch claw 2c-2 for reverse input have their one ends made of an elastic member (not shown) and the first clutch cam surface 2b for reverse input. −1 or a reverse input second clutch cam surface 2b-2, the load is applied in the direction of rising. On the other hand, the other end is in contact with the reverse input sleeve 9b in the clutch switching device 9, and against the elastic force of the elastic member, the reverse input first clutch cam surface 2b-1 or the reverse input second clutch. It is suppressed that the cam surface 2b-2 rises (see, for example, FIGS. 2A and 2B).

  Here, the reverse input sleeve 9 b is provided with two notches 9 d along the axial direction of the axle 5. When the reverse input operation portion 9a drawn out through the axle 5 is moved in the axial direction by an external operation from the outside of the axle 5, the reverse input sleeve 9b is also moved in the axial direction, and the notch portion 9d is It moves to both positions of the first clutch pawl 2c-1 for reverse input or the second clutch pawl 2c-2 for reverse input.

  Then, the reverse input first clutch pawl 2c-1 and the reverse input second clutch pawl 2c-2 facing the notch 9d are released from the restraint by the reverse input sleeve 9b, and one end thereof is for reverse input. It rises to the first clutch cam surface 2b-1 and the reverse input second clutch cam surface 2b-2 side, and is in a state where it can engage with the reverse input. For example, in FIGS. 2A and 2B, both the first clutch pawl 2c-1 for reverse input and the second clutch pawl 2c-2 for reverse input are restrained and cannot be engaged. 8 (a) and 8 (b), both the first clutch pawl 2c-1 for reverse input and the second clutch pawl 2c-2 for reverse input are both raised and engaged. Is shown.

  A tapered surface 9e is provided at one axial end of the notch 9d. The taper surface 9e is formed by the reverse input first clutch pawl 2c-1 and the reverse input second clutch pawl 2c-2, while the reverse input first clutch cam surface 2b-1 and the reverse input second clutch cam surface 2b-. 2, when the engagement is to be released from the engaged state, the taper surface 9e is in contact with one end of each of the clutch claws 2c-1 and 2c-2, thereby smoothly releasing the engagement. Yes. That is, by the inclined surface of the tapered surface 9e, it is possible to increase the force for removing the clutch claws 2c-1 and 2c-2 from the clutch cam surfaces 2b-1 and 2b-2.

  The reverse input operation unit 9a has a shaft shape, is inserted in a shaft hole 5a provided in the axle 5 so as to be able to advance and retreat, and is urged outward in the axial direction by an elastic member 9g. For this reason, when the reverse input operation portion 9a is pushed into the hub 1, the reverse input operation portion 9a is moved against the biasing force of the elastic member 9g to release the pushing force. Then, the reverse input operation unit 9a automatically returns to the original state by the biasing force.

  Further, the reverse input sleeve 9 b is fixed to the axle 5 by a pin 9 f inserted in a lateral hole 9 c provided in the axle 5. The reverse input sleeve 9b can be moved in the axial direction by moving the pin 9f in the axial direction in the horizontal hole 9c by the speed change operation portion 9a.

  This clutch switching device 9 switches the reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 to a state in which they can be engaged with the reverse input in conjunction with the brake operation. It has become. That is, if the brake is operated (when the brake is in effect), the reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 can be engaged with the reverse input. When the brake operation is released (the brake is not effective), the reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 are engaged with the reverse input. It becomes impossible to match.

  For this reason, the reverse switching first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 are reversely input by the function of the clutch switching device 9 when the brake is applied, especially when the forward drive is not driven. By switching to a state in which engagement is possible, reverse input from the hub case 7 can be transmitted to the driving force transmission element (chain 23) through the rear sprocket 4.

  As described above, in this embodiment, the first sun gear 3a-1 meshed with the first planetary gear 3b-1 is the first first-way clutch 3e-1 for shifting and the first one-way for reverse input with respect to the axle 5. It is supported via the clutch 2a-1. Further, the second sun gear 3a-2 meshing with the second planetary gear 3b-2 is supported with respect to the axle 5 through the second one-way clutch 3e-2 for shifting and the second one-way clutch 2a-2 for reverse input. Has been.

Here, in this embodiment, the first planetary gear mechanism 3p-1 and the second planetary gear mechanism 3p-2 are configured by the same planetary gear mechanism. That is, by using the sun gear 3a and the planetary gear 3b having the same gear specifications, it is possible to share the parts of the planetary gear mechanisms 3p-1 and 3p-2, thereby realizing cost reduction. .
When the first outer ring gear 3d-1 and the second outer ring gear 3d-2 are formed separately from the second planet carrier 3c-2 and the hub case 7, respectively, the first outer ring gear 3d-1, The two outer ring gears 3d-2 are also made of the same gear specifications, so that parts can be shared.

  Further, in this embodiment, the bidirectional first clutch cam portion 3h-1 that exhibits the functions of both the first clutch cam surface 3g-1 for shifting and the first clutch cam surface 2b-1 for reverse input is used as the first sun. It is formed on the inner surface of the gear 3a-1. Further, the bidirectional second clutch cam portion 3h-2 that exhibits the functions of both the second clutch cam surface 3g-2 for shifting and the second clutch cam surface 2b-2 for reverse input is connected to the second sun gear 3a-2. It is formed on the inner surface.

  Accordingly, the unevenness of the bidirectional first clutch cam portion 3h-1 also functions as the first clutch cam surface 3g-1 for shifting, and also functions as the first clutch cam surface 2b-1 for reverse input. The unevenness of the bidirectional second clutch cam portion 3h-2 also functions as the second clutch cam surface 3g-2 for shifting, and also functions as the second clutch cam surface 2b-2 for reverse input.

For this reason, the shift first one-way clutch 3e-1 and the reverse input first one-way clutch 2a-1 and the shift second one-way clutch 3e-2 and the reverse input second one-way clutch 2a-2 are respectively connected to the shaft. It is arranged at the same position in the direction.
At this time, the shift first clutch pawl 3f-1 and the reverse input first clutch pawl 2c-1, and the shift second clutch pawl 3f-2 and the reverse input second clutch pawl 2c-2 are also respectively It is arranged at the same position in the direction.

  The length of the transmission mechanism 3 in the axial direction of the axle 5 has to be as short as possible because there is a limitation in the space in the rear hub 1, and thus the reverse input one-way clutch 2 and the transmission one-way By configuring the clutch 3e as a ratchet clutch and disposing them at the same position in the axial direction of the axle 5, the length of the sun gear 3a in the axial direction can be shortened.

  The state of the first gear stage is shown in FIGS. In the first shift, the first clutch pawl 3f-1 for shifting and the second clutch pawl 3f-2 for shifting are both restrained by the shifting sleeve 10b, as shown in FIGS. ing.

  For this reason, the first sun gear 3a-1 and the second sun gear 3a-2 are rotatable relative to the axle 5 with respect to the driving force.

  At this time, the reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 are both the reverse input first clutch pawl 2c-1 and the reverse input second clutch pawl 2c-. 2 is constrained by the reverse input sleeve 9b, so that it cannot engage with the reverse input.

  In this case, the driving force from the rear sprocket 4 is directly connected (constant speed) in the order of the first planet carrier 3c-1, the first one-way clutch 3k, the second planet carrier 3c-2, the second one-way clutch 3m, and the hub case 7. Communicated.

  The state of the second gear stage is shown in FIGS. When the shift operation unit 10a of the shift control mechanism 10 is pushed to a certain position in the axial direction in the direction of the arrow shown in FIG. 3 from the state of the first shift, the shift first clutch pawl 3f-1 is Although it is restrained by the speed change sleeve 10b, the notch 10d of the speed change sleeve 10b is moved to the position of the speed change second clutch pawl 3f-2. In this state, as shown in FIGS. 4A and 4B, the second clutch pawl 3f-2 for shifting is released, and the second clutch pawl 3f-2 for shifting is attached to an elastic member (not shown). It swings by the force and engages with the bi-directional second clutch cam portion 3h-2.

  For this reason, with respect to the driving force, the first sun gear 3a-1 can be relatively rotated around the axle 5, and the second sun gear 3a-2 cannot be relatively rotated.

  At this time, the reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 are both the reverse input first clutch pawl 2c-1 and the reverse input second clutch pawl 2c-. 2 is constrained by the reverse input sleeve 9b, so that it cannot engage with the reverse input.

  In this case, the driving force from the rear sprocket 4 is the first planet carrier 3c-1, the first one-way clutch 3k, the second planet carrier 3c-2, the second planet gear 3b-2, the second outer ring gear 3d-2, The speed is increased and transmitted in the order of the hub case 7.

The speed increase ratio is as follows. The number of teeth of the second sun gear 3a-2 is b, and the number of teeth of the second outer ring gear 3d-2 is d.
(B + d) / d
It becomes.

  The state of the third speed change is shown in FIGS. When the shift operation unit 10a of the shift control mechanism 10 is further pushed to the position in the axial direction in the direction of the arrow shown in FIG. 5 from the state of the second shift, the shift first clutch pawl 3f-1 And the notch 10d of the shift sleeve 10b moves to the position of the shift second clutch pawl 3f-2. Thereby, the restraint of the first clutch pawl 3f-1 for shifting and the second clutch pawl 3f-2 for shifting is released, and the first clutch pawl 3f-1 for shifting and the second clutch pawl 3f-2 for shifting are It swings by an urging force of an elastic member (not shown) and engages with the bidirectional first clutch cam portion 3h-1 and the bidirectional second clutch cam portion 3h-2.

  At this time, relative to the driving force, the first sun gear 3a-1 and the second sun gear 3a-2 are not relatively rotatable.

  At this time, the reverse input first one-way clutch 2a-1 and the reverse input second one-way clutch 2a-2 are both the reverse input first clutch pawl 2c-1 and the reverse input second clutch pawl 2c-. 2 is constrained by the reverse input sleeve 9b, so that it cannot engage with the reverse input.

  In this case, the driving force from the rear sprocket 4 is the first planetary carrier 3c-1, the first planetary gear 3b-1, the first outer ring gear 3d-1, the second planetary carrier 3c-2, and the second planetary gear 3b-. 2, the second outer ring gear 3d-2 and the hub case 7 are accelerated and transmitted in this order.

The speed increase ratio is such that the number of teeth of the first sun gear is a, the number of teeth of the second sun gear 3a-2 is b, the number of teeth of the first outer ring gear 3d-1 is c, and the number of teeth of the second outer ring gear 3d-2 is If the number of teeth is d,
{(A + c) × (b + d)} / (c × d)
It becomes.

  When returning from the third speed to the second speed, or returning from the second speed to the first speed, the elastic force of the elastic member 10g and the elastic member 9g can be achieved by releasing the force in the direction of pushing in the speed change operation unit 10a. As a result, the speed change operation unit 10a and the speed change sleeve 10b are pushed back, so that the speed change operation can be performed only by releasing or loosening the force in the pressing direction.

  At this time, the shift first clutch pawl 3f engaged with the bidirectional first clutch cam portion 3h-1 and the bidirectional second clutch cam portion 3h-2 by the tapered surface 10e provided in the axial direction of the notch portion 10d. -1 and the second clutch pawl 3f-2 for shifting are increased, and the shifting sleeve 10b is easily returned, so that smooth switching is possible.

  7 and 8 show the state when the forward drive is not driven. When the reverse input operation portion 9a of the clutch switching device 9 is pushed to the position in the axial direction in the direction indicated by the arrow in FIG. 7 in conjunction with the brake operation, the reverse input first clutch pawl 2c-1 and the reverse input second The notch 9d of the reverse input sleeve 9b moves to the position of the two clutch pawl 2c-2. Thereby, the restraint of the first clutch pawl 2c-1 for reverse input and the second clutch pawl 2c-2 for reverse input is released, and the first clutch pawl 2c-1 for reverse input and the second clutch pawl 2c for reverse input are released. -2 is swung by an urging force of an elastic member (not shown), and engages with the bidirectional first clutch cam portion 3h-1 and the bidirectional second clutch cam portion 3h-2.

  At this time, the first sun gear 3 a-1 and the second sun gear 3 a-2 cannot rotate relative to the axle 5 with respect to the reverse input.

  In this case, the reverse input from the hub case 7 is the second outer ring gear 3d-2, the second planetary gear 3b-2, the second planet carrier 3c-2, the first outer ring gear 3d-1, and the first planetary gear 3b-1. The first planetary carrier 3c-1 and the rear sprocket 4 are decelerated and transmitted in this order, and are transmitted to the motor via the chain 23 as a power transmission element, thereby enabling regenerative power generation.

The reduction ratio is such that the number of teeth of the first sun gear 3a-1 is a, the number of teeth of the second sun gear 3a-2 is b, the number of teeth of the first outer ring gear 3d-1 is c, and the second outer ring gear 3d- If the number of teeth of 2 is d,
{(A + c) × (b + d)} / (c × d)
It becomes.

  When the bicycle is pushed back by hand (during reverse), the reverse input first clutch pawl 2c-1 and the reverse input second clutch pawl 2c-2 are bidirectional first clutch cam portions unless the brake is operated. 3h-1 and the two-way second clutch cam portion 3h-2 are not engageable. Therefore, the function does not interfere with the first one-way clutch 3k and the second one-way clutch 3m, and the vehicle can move backward.

Further, as a modified example of the speed change control mechanism 10 and the clutch switching device 9, for example, a speed change sleeve 10b or a reverse input sleeve 9b may be operated to rotate around the axis of the axle 5. That is, by rotating the speed change sleeve 10b and the reverse input sleeve 9b in the direction around the axle 5, the notches 10d and 9d are positioned at the positions of the speed change clutch pawl 3f and the reverse input clutch pawl 2c, The reverse input one-way clutch 2 and the shift one-way clutch 3e are respectively switched by moving between the shift clutch pawl 3f and the reverse input clutch pawl 2c.
At this time, the rotation around the shaft of the speed change sleeve 10b and the reverse input sleeve 9b can be operated in conjunction with the axial movement of the speed change operation portion 10a and the reverse input operation portion 9a. Further, the shift operation unit 10a and the reverse input operation unit 9a can be operated in conjunction with the rotational movement around the axis.

  In these embodiments, in the one-way clutch 3e for shifting and the one-way clutch 2 for reverse input constituted by a ratchet clutch, the clutch pawls 3f and 2c of the ratchet clutch are engaged with the clutch cam surfaces 3g and 2b. Although a method of switching between a state that can be engaged by the shift sleeve 10b and the reverse input sleeve 9b and a state that cannot be engaged is adopted, the one-way clutch between the axle 5 and the sun gear 3a can be relatively rotated and cannot be relatively rotated. As the means for switching to, other configurations other than the speed change sleeve 10b and the reverse input sleeve 9b may be employed.

  In this embodiment, the shift one-way clutch 3e, the first one-way clutch 3k, and the second one-way clutch 3m are constituted by ratchet clutches, but one-way clutches having other configurations such as a roller clutch and a sprag clutch are used. It can also be adopted.

1 Rear hub (hub)
2 Reverse input one-way clutch 2a-1 Reverse input first one-way clutch 2a-2 Reverse input second one-way clutch 2b-1 Reverse input first clutch cam surface 2b-2 Reverse input second clutch cam surface 2c- 1 First clutch claw for reverse input 2c-2 Second clutch claw for reverse input 2d Oscillating shaft (clutch claw shaft)
3 Transmission mechanism 3a Sun gear 3a-1 First sun gear 3a-2 Second sun gear 3b Planetary gear 3b-1 First planetary gear 3b-2 Second planetary gear 3c Planetary carrier 3c-1 First planetary carrier 3c-2 Second planetary carrier 3d Outer ring gear 3d-1 First outer ring gear 3d-2 Second outer ring gear 3e Shifting one-way clutch 3e-1 Shifting first one-way clutch 3e-2 Shifting second one-way clutch 3f Shifting clutch cam pawl 3f-1 Shifting first clutch pawl 3f-2 Shifting second clutch pawl 3g Shifting clutch cam surface 3g-1 Shifting first clutch cam surface 3g-2 Shifting second clutch cam surface 3h-1 First in both directions Clutch cam portion 3h-2 Bidirectional second clutch cam portion 3i Oscillating shaft (clutch pawl shaft)
3k First one-way clutch 3m Second one-way clutch 3n First clutch cam surface 3q First clutch pawl 3r Second clutch pawl 3s Second clutch cam surface 4 Rear sprocket (sprocket)
5 Axle 5a, 5b Shaft hole 6 Hub flange 7 Hub case 9 Clutch switching device 9a Reverse input operation portion 9b Reverse input sleeve 9c Horizontal hole 9d Notch 9e Tapered surface 9f Pin 9g Elastic member 10 Shift control mechanism 10a Shift operation portion 10b For shift Sleeve 10c Horizontal hole 10d Notch 10e Tapered surface 10f Pin 10g Elastic member 13, 14 Bearing part

Claims (12)

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 generated by the output of the motor can be transmitted to the driving wheel via the driving force transmitting element. In the battery-assisted bicycle provided with a regenerative mechanism for reducing regenerative power generated by reverse input from the drive wheel to the output shaft of the motor to the secondary battery during forward non-drive,
A hub (1) provided on the drive wheel is provided with a speed change mechanism (3), a reverse input one-way clutch (2), and a clutch switching device (9). The speed change mechanism (3) is connected to the axle (5). It is provided with at least two planetary gear mechanisms (3p) arranged in parallel along the axial direction, and the first planetary gear mechanism (3p-1) as one of the planetary gear mechanisms (3P) is arranged around the axle (5). The first sun gear (3a-1) provided, the first planetary gear (3b-1) meshing with the first sun gear (3a-1), and the first planetary gear (3b-1) are held. The second planetary gear mechanism (3p-2), which has the first planet carrier (3c-1) and is another planetary gear mechanism (3p), is provided with a second sun gear ( 3a-2) and the second planetary gear (3b-2) meshing with the second sun gear (3a-2) And a second planet carrier (3c-2) that holds the second planetary gear (3b-2), and the speed change mechanism (3) has the first sun gear (3a-1) and The shifting one-way clutch (3e) capable of switching the second sun gear (3a-2) to be relatively rotatable or non-rotatable around the axle (5) and the switching one-way clutch (3e). The second planet carrier (3c-2) rotates integrally with the first outer ring gear (3d-1) meshing with the first planetary gear (3b-1). The hub case (7) rotates integrally with the second outer ring gear (3d-2) meshing with the second planetary gear (3b-2),
The shift control mechanism (10) makes one of the first sun gear (3a-1) and the second sun gear (3a-2) non-rotatable with respect to the driving force relative to the axle (5), and the other is the axle ( 5) By making the relative rotation possible, the driving force is changed from the first planetary carrier (3c-1) to the first planetary gear mechanism (3p-1) or the second planetary gear mechanism (3p-2). Drives both the first sun gear (3a-1) and the second sun gear (3a-2), the first speed-increasing state that is accelerated through either of them and transmitted to the hub case (7) By making the axle (5) non-rotatable relative to the force, the driving force is transferred from the first planetary gear mechanism (3c-1) to the first planetary gear mechanism (3p-1) and the second planetary gear mechanism ( 3p-2) is transmitted through the second speed increase through the hub case (7). The reverse input one-way clutch (2) is configured such that, in each of the planetary gear mechanisms (3p-1, 3p-2), the first sun gear (3a-1) and the second sun gear (2a) It is provided between the sun gear (3a-2) and the axle (5). By operating the clutch switching device (9) during forward non-drive, the reverse input from the drive wheel By making the at least one sun gear (3a) non-rotatable around the axle (5), a reverse input from the driving wheel can be transmitted from the hub case (7) to the driving force transmitting element (1). ) With a battery-assisted bicycle.   The electric clutch according to claim 1, wherein the clutch switching device (9) switches the reverse input one-way clutch (2) to a state in which the reverse input can be engaged with the reverse input in conjunction with a brake operation. Auxiliary bicycle. A first one-way clutch (3k) is provided between the first planet carrier (3c-1) and the second planet carrier (3c-2), and the second planet carrier (3c-2) and the hub case (7) With a second one-way clutch (3m)
The shift control mechanism (10) drives the first sun gear (3a-1) and the second sun gear (3a-2) relative to the driving force relative to the axle (5). The speed can be changed to a low speed state in which the force is transmitted directly from the first planet carrier (3c-1) to the hub case (7) via the first one-way clutch (3k) and the second one-way clutch (3m). The battery-assisted bicycle according to claim 1 or 2, characterized by the above.   The reverse input one-way clutch (2) includes a reverse input first one-way clutch (2a-1) provided between the first sun gear (3a-1) and the axle (5); The second one-way clutch for reverse input (2a-2) provided between the sun gear (3a-2) and the axle (5). When the forward drive is not driven, the clutch switching device (9) By switching the first one-way clutch for reverse input (2a-1) and the second one-way clutch for reverse input (2a-2) to be engageable with the reverse input, the reverse from the hub case (7) is achieved. The battery-assisted bicycle according to claim 3, wherein an input can be transmitted to the driving force transmitting element.   The said 1st planetary gear mechanism (3p-1) and said 2nd planetary gear mechanism (3p-2) were comprised by the same planetary gear mechanism in any one of Claims 1 thru | or 4 characterized by the above-mentioned. The motor-assisted bicycle described. The battery-assisted bicycle according to any one of claims 1 to 5, wherein the first one-way clutch (3k) and the second one-way clutch (3m) are constituted by a ratchet clutch. The battery-assisted bicycle according to any one of claims 1 to 5, wherein the first one-way clutch (3k) and the second one-way clutch (3m) are constituted by a roller clutch or a sprag clutch.   The shift one-way clutch (3e) includes a shift first one-way clutch (3e-1) provided between the first sun gear (3a-1) and the axle (5), and the second sun gear. (3a-2) and the second shift one-way clutch (3e-2) provided between the axle (5) and the first shift one-way clutch (3e-1) and the second shift-use clutch. The battery-assisted bicycle according to any one of claims 1 to 7, wherein the two-way clutch (3e-2) is a ratchet clutch.   The shift control mechanism (10) has a shift operation part (10a) drawn out through the axle (5), and by moving the shift operation part (10a) in the axial direction, The battery-assisted bicycle according to claim 8, wherein the first one-way clutch for shifting (3e-1) and the second one-way clutch for shifting (3e-2) are switched.   The shift first one-way clutch (3e-1) has a swingable first clutch pawl (3f-1) on the outer surface of the axle (5). ) Meshing with the first clutch cam surface (3g-1) for shifting is provided on the inner surface of the first sun gear (3a-1), and the second one-way clutch for shifting (3e-2) is swung. A second clutch claw surface (3g-2) for shifting, in which the second clutch pawl (3f-2) for shifting freely engages the outer surface of the axle (5) and the second clutch pawl (3f-2) for shifting. The battery-assisted bicycle according to claim 8 or 9, wherein the battery-assisted bicycle is provided on an inner surface of the second sun gear (3a-2).   The first clutch pawl (3f-1) for shifting and the second clutch pawl (3f-2) for shifting are each elastically connected to the first clutch cam surface (3g-1) for shifting or the shifting gear. The second clutch cam surface (3g-2) is urged in the direction of rising, and the other end can come into contact with the speed change sleeve (10b) provided on the outer periphery of the axle (5). The notch (10d) provided in the shifting sleeve (10b) is moved by the shifting operation portion (10a) in the axial direction so that the shifting first clutch pawl (3f-1) and the shifting gear By moving between the position of the second clutch pawl (3f-2) and the position retracted from the first clutch pawl (3f-1) for shifting and the second clutch pawl (3f-2) for shifting The first for shifting Eikuratchi (3e-1) and motor-assisted bicycle according to claim 10, wherein the second one-way clutch (3e-2) that is switched for the shift.   The shift sleeve (10b) moves in the axial direction of the axle (5), so that the notch (10d) is moved, and the axial end of the notch (10d) is axially moved. The battery-assisted bicycle according to claim 11, further comprising a tapered surface (10e) that approaches the outer diameter side toward the outside.

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