JP2010274900A - Electric auxiliary bicycle including regeneration mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To attain regenerative charging without complicating a device as much as possible in a center motor type electric auxiliary bicycle including an internally provided transmission. <P>SOLUTION: In the electric auxiliary bicycle, a secondary battery and a motor for auxiliary driving are mounted to a frame for connecting a front wheel and a rear wheel, stepping force transmitted from a crankshaft or drive force by an output of the motor can be transmitted to a drive wheel. The bicycle includes a regenerative mechanism for reducing regenerative electric power generated by reverse input from the drive wheel to an output shaft of the motor to the secondary battery at non-driving. A speed-change mechanism 5 and a first one way clutch 2 are provided at the inside of a hub 1 provided on the drive wheel, and the speed-change mechanism 5 has function for transmitting the stepping force or the drive force by the output of the motor to the drive wheel through a sprocket 7. The first one way clutch 2 is idled at drive by the stepping force or the output of the motor and has function capable of transmitting reverse input from the drive wheel to the sprocket 7. <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 speed change 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 the 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 in a center motor-type battery-assisted bicycle equipped with an internal transmission, without complicating the device as much as possible.

  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 can transmit to the drive wheel and, when not driven, regenerative power generated by reverse input from the drive wheel to the output shaft of the motor to the secondary battery, the drive wheel A transmission mechanism and a first one-way clutch inside the hub provided in the first transmission mechanism, wherein the transmission mechanism has a function of transmitting a driving force generated by the pedaling force or the output of the motor to the driving wheel through a sprocket. The clutch is idle when driven by the pedaling force or the output of the motor, and can transmit a reverse input from the driving wheel to the sprocket when not driven. Employing the configuration of the motor-assisted bicycle provided with a regenerative mechanism characterized in that it comprises.

  With the above configuration, when driving forward, the driving force is transmitted from the sprocket of the driving wheel to the hub, and the bicycle moves forward. During non-drive forward, the first one-way clutch is locked to transmit the reverse input from the hub to the sprocket, and further, torque is transmitted from the sprocket to the motor-driven sprocket through the power transmission element, thereby enabling regenerative power generation. .

  In this configuration, the speed change mechanism includes a sun gear provided on the outer periphery of the axle, a planetary gear that meshes with the sun gear, a planet carrier that holds the planetary gear, and an outer ring gear that meshes with the planetary gear. Sometimes, the sun gear is a fixed member, the outer ring gear is an input member, the planet carrier is an output member, and at the constant speed, it is composed of a two-stage planetary gear reducer using the outer ring gear as an input / output member. can do.

  For changing the speed of the speed change mechanism, known means that can change the meshing of the gears between the input member and the output member can be employed. For example, a slide member that is movable in the axial direction with respect to the axle of the drive wheel may be provided, and the shift switching of the speed change mechanism may be performed by moving the slide member in the axial direction. In this way, since the slide member can be pulled out through the axle, the shifting operation from the outside can be easily realized through the slide member.

  Further, the transmission mechanism includes a plurality of sun gears, and any one of the plurality of sun gears is a fixing member, the outer ring gear is an input member, and the planetary carrier is an output member. It is possible to employ a configuration that includes a speed reducer that includes a plurality of gear combinations, and that includes a speed change control mechanism that has a function of selecting any one of the plurality of sun gears as the fixed member.

  Further, the transmission mechanism includes a plurality of the sun gears, and any one of the plurality of sun gears is a fixing member, the planetary carrier is an input member, and the outer ring gear is an output member. It is possible to adopt a configuration including a speed change mechanism including a gearbox having a plurality of gear combinations, and having a function of selecting any one of the plurality of sun gears as the fixed member.

  In the configuration including these shift control mechanisms, any one of the plurality of sun gears rotatably supported around the axle is rotated around the axle with respect to both the driving force and the reverse input from the tire. It is possible to adopt a configuration having a function of performing a shift by switching between possible and non-rotatable.

  Further, the shift control mechanism includes a snap key, and the shift switching of the shift mechanism is performed by moving the snap key in the axial direction from outside through the axle, and any of the sun gears with which the snap key meshes. It is possible to employ a configuration in which rotation around the axle is impossible with respect to both the driving force and the reverse input from the tire.

  It should be noted that locking (engagement) and release of the first one-way clutch can be interlocked with a brake operation. When the reverse drive is not driven, the first one-way clutch is not locked, and the reverse input can be cut off as in the forward drive.

  As the first one-way clutch, a well-known one-way clutch can be employed. For example, a roller clutch or a sprag clutch can be employed.

  In the center unit, it is possible to transmit the driving force and the torque in both directions of the reverse input by directly connecting the motor output shaft and the motor drive sprocket.

  In addition, by incorporating a center one-way clutch that transmits only the driving force between the crankshaft and the crank sprocket (human-powered sprocket) and idles during reverse input, the pedal can be forced to rotate by reverse input. Can be prevented.

  As the center one-way clutch, a well-known one-way clutch can be employed. For example, a roller clutch, a sprag clutch, or a ratchet clutch 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. If the operation of the first one-way clutch for reverse input transmission is linked with the brake operation, the braking force can be increased.

  Since the speed change mechanism is built in the hub of the drive wheel, it is highly durable and maintenance-free. That is, regenerative charging can be realized without complicating the device as much as possible in a center motor-type battery-assisted bicycle equipped with an internal transmission.

The direct connection state of 1st embodiment is shown, (a) is front sectional drawing, (b) is a side view. The deceleration state of 1st embodiment is shown, (a) is front sectional drawing, (b) is a side view. The direct connection state of 2nd embodiment is shown, (a) is front sectional drawing, (b) is a side view. The deceleration state of 2nd embodiment is shown, (a) is front sectional drawing, (b) is a side view. Side view showing the third embodiment Side view showing the fourth embodiment Side view showing the fifth embodiment

(First embodiment)
1st Embodiment of this invention is described based on FIG.1 and FIG.2. 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 7. In addition, a regenerative mechanism is provided that, when not driven, regenerates regenerative power generated by reverse input from the rear wheel rear hub 1 to the output shaft of the motor to the secondary battery of the center motor unit.

  As shown in FIG. 1, the rear hub 1 includes a speed change mechanism 5 and a first one-way clutch 2 in a hub case 12 that is provided coaxially with the rear axle 11.

  As shown in FIG. 1A, the configuration of the first one-way clutch 2 is such that an inner ring 2c and an outer ring 2b arranged on the same axis can relatively rotate about an axis, and an outer peripheral surface of the inner ring 2c and an outer ring 2b The roller 2a is disposed in a wedge space extending between the groove 2f and extending in the circumferential direction. The roller 2a is held in the circumferential direction by an annular cage 2d, and is urged by the elastic member 2e through the cage 2d in the direction in which the wedge space expands. A bearing portion 15 is provided between the cage 2d and the inner ring 2c and can be rotated relative to each other.

The inner ring 2c is supported so as to be rotatable integrally with the rear sprocket 7. The outer ring 2b is rotatably provided integrally with the hub case 12.
Bearing portions 13 are provided between the inner ring 2c and the axle 11 and between the hub case 12 and the axle 11, and are supported so as to be rotatable relative to each other. A bearing portion 14 is also provided between the inner ring 2c and the hub case 12 so as to be relatively rotatable.

In the first one-way clutch 2, when the rear sprocket 7 and the inner ring 2c rotate in the backward direction with respect to the outer ring 2b, the roller 2a moves in the groove 2f in the direction in which the wedge space is narrowed, and the inner ring 2c and the outer ring 2b are moved. Combine and lock. Further, when the rear sprocket 7 and the inner ring 2c rotate in the forward direction with respect to the outer ring 2b, the coupling is released and the lock is released.
As a result, the forward torque input to the rear sprocket 7 is not transmitted, but the reverse torque (including the reverse input torque during forward non-drive) is transmitted.

  However, in a normal state (a state where no external force is applied to the cage 2d), the cage 2d urged by the elastic body 2e presses the roller 2a in the direction in which the wedge space expands. Never lock. However, when a force is applied to the cage 2d from the outside and the cage 2d overcomes the bias of the elastic body 2e and rotates relative to the outer ring 2b in the backward direction, the roller 2a is in a shallow position in the wedge space of the outer ring 2b. It becomes a standby state. At this time, if there is a reverse input from the tire side, the roller 2a is wedge-engaged between the inner ring 2c and the groove 2f of the outer ring 2b, and the inner ring 2c and the outer ring 2b of the first one-way clutch 2 are coupled and locked. .

  That is, the first one-way clutch 2 can idle during forward drive, and can transmit reverse input torque from the tire to the rear sprocket 7 when not forward driven.

  The transmission mechanism 5 includes a sun gear 5a that rotates integrally with the axle 11, a planetary gear 5b that meshes with the sun gear 5a, a planet carrier 5c that holds the planetary gear 5b, and an outer ring that meshes with the planetary gear 5b. And a gear 5d.

  Further, in the speed change mechanism 5, the second one-way clutch 3 is incorporated between the outer ring gear 5 d and the hub case 12. A third one-way clutch 4 is incorporated between the inner ring 2c and the outer ring gear 5d. In this embodiment, a ratchet clutch is employed as the structure of the second one-way clutch 3 and the third one-way clutch 4, but a one-way clutch having another structure such as a roller clutch or a sprag clutch may be employed.

  By providing the second one-way clutch 3 and the third one-way clutch 4, the transmission mechanism 5 allows the forward torque input to the sprocket 7 to be transmitted from the sprocket 7 side to the tire side via the third one-way clutch 4. However, it functions so that the torque in the reverse direction is not transmitted from the sprocket 7 side to the tire side.

  Next, the speed change function of the speed change mechanism 5 will be described. Switching between speed reduction and direct connection (constant speed) of the speed change mechanism 5 is performed by the slide member 8 provided on the axle 11 moving (sliding) in the axial direction. Done. A shaft hole 11 a is formed in the axle 11, and the slide member 8 can be moved along the axial direction of the axle 11 by an operation member (not shown) inserted from the opening of the shaft hole 11 a. I can do it.

  When the slide member 8 is pushed inward from the state shown in FIG. 1B to the state shown in FIG. 2B by the operating member, the ratchet pawl 4a held by the inner ring 2c of the third one-way clutch 4 However, from the state shown in FIG. 1A to the state shown in FIG. 2A, the rear sprocket 7 and the inner ring 2c and the hub case 12 are directly connected to each other by being engaged with a groove provided on the inner periphery of the hub case 12. Torque can be transmitted (directly connected (constant speed) state).

At this time, rotation is transmitted to the planetary gear 5b and the planet carrier 5c from the outer ring gear 5d integrated with the rear sprocket 7 and the inner ring 2c, but the rotation speed of the hub case 12 is higher than the rotation speed of the planet carrier 5c. Therefore, the second ratchet clutch 3 is idled so that torque transmission from the planet carrier 5c to the hub case 12 does not occur.

  Further, when the force that pushes the slide member 8 inward from the operation member is released, the slide member 8 is changed from the state shown in FIG. 2B to the state shown in FIG. And pushed back.

At this time, the ratchet pawl 4a of the third one-way clutch 4 is pressed along the tapered portion 8a of the slide member 8, and the circumferential direction from the state shown in FIG. 2A to the state shown in FIG. Fall into. When the ratchet pawl 4a falls down, the ratchet pawl 4a is released from the groove provided in the inner periphery of the case 12 that has been bitten, so that the third one-way clutch 4 rotates idle.
For this reason, the rotational torque input from the rear sprocket 7 is transmitted from the outer ring gear 5d to the planetary gear 5b and the planetary carrier 5c through the inner ring 2c, and the second one-way clutch 3 is locked, and finally the hub case 12 Reportedly. At this time, the rotational speed is decelerated while being transmitted from the outer ring gear 5d to the planet carrier 5c (decelerated state).

  That is, the speed change mechanism 5 uses the sun gear 5a as a fixed member, the outer ring gear 5d as an input member, and the planet carrier 5c as an output member in the deceleration state, and the outer ring gear 5d as an input / output member in the direct connection state. It is a functioned two-speed planetary gear reducer that is directly connected to the reduction gear.

  More specifically, during forward drive in the deceleration state (the state shown in FIG. 1), the forward drive torque input from the rear sprocket 7 causes the inner ring 2c and the outer ring gear 5d integrated with the rear sprocket 7 to move. Rotate in the forward direction. In the speed change mechanism 5, the sun gear 5a is fixed to the axle 11, and the planetary gear 5b revolves while rotating in the forward direction of the outer ring gear 5d to guide the planetary gear 5b. 5c also rotates in synchronization with the revolution of the planetary gear 5b.

  At this time, if the number of teeth of the sun gear 5a is a and the number of teeth of the outer ring gear 5d is d, the reduction ratio of the reduction gear is (a + d) / d. The second one-way clutch 3 is incorporated between the planet carrier 5c and the hub case 12, and the rotation of the planet carrier 5c is transmitted to the case 12 at this reduction ratio.

On the other hand, in the first one-way clutch 2 incorporated between the inner ring 2c and the hub case 12, the cage 2d urged by the elastic body 2e causes the roller 2a to move deeper in the groove 2f (in the direction in which the wedge space expands). Since it is pressed, it is usually idle.
If a force is applied from the friction member 10 to the cage 2d by the brake operation performed by the driver, the cage 2d overcomes the bias of the elastic body 2e and rotates relative to the outer ring 2b in the backward direction.
As a result of this relative rotation, even if the roller 2a enters a standby state at a shallow position in the groove 2f of the outer ring 2b, as long as the rotation speed of the inner ring 2c is higher than the rotation speed of the outer ring 2b (the deceleration state), the roller Since 2a deviates from the wedge space formed by the groove 2f of the inner ring 2c and the outer ring 2b, the first one-way clutch 2 is not locked.

  Further, during forward drive in the direct connection (constant speed) state (the state shown in FIG. 2), the forward driving torque input from the rear sprocket 7 is held in the inner ring 2c integrated with the rear sprocket 7. It is transmitted directly to the hub case 12 through the third one-way clutch 4.

  On the other hand, the first one-way clutch 2 incorporated between the inner ring 2c and the hub case 12 is not locked because the cage 2d biased by the elastic body 2e presses the roller 2a toward the deeper side of the groove 2f.

If a force is applied from the friction member 10 to the cage 2d by the brake operation performed by the driver, the cage 2d overcomes the bias of the elastic body 2e and rotates relative to the outer ring 2b in the backward direction.
Even if the roller 2a is in a standby state at a shallow position of the outer ring groove 2f due to this relative rotation, the rotation speed of the inner ring 2c is equal to the rotation speed of the outer ring 2b (the direct connection (constant speed) state), and the roller 2a The one-way clutch 2 is not locked because it does not bite into the wedge formed by the groove 2f of the inner ring 2c and the outer ring 2b.

  Further, when the vehicle is not driven forward (for example, a situation where a bicycle is used to go down a hill without pedaling), a reverse input torque is applied to the rear hub 1 from the tire side. At this time, since the second one-way clutch 3 and the third one-way clutch 4 idle, the reverse input torque cannot be transmitted through the second one-way clutch 3 and the third one-way clutch 4.

  On the other hand, at this time, the first one-way clutch 2 is in a normal state (holding state) because the cage 2d biased by the elastic body 2e presses the roller 2a toward the deeper groove 2f (the direction in which the wedge space spreads). In a state where no external force is applied to the container 2d), the wheel is idling.

However, when force is applied from the friction member 10 to the cage 2d by the brake operation performed by the driver, the cage 2d overcomes the bias of the elastic body 2e and rotates relative to the outer ring 2b in the backward direction.
When the roller 2a is in a standby state at a shallow position of the outer ring groove 2f due to this relative rotation, the rotation speed of the outer ring 2b is higher than the rotation speed of the inner ring 2c (non-driven state). The first one-way clutch 2 is locked in the wedge space formed by the groove 2f of 2b, and the hub case 12 and the rear sprocket 7 are directly connected.

  As a result, the reverse input torque from the tire of the rear wheel that is the drive wheel is transmitted from the rear sprocket 7 to the motor shaft through a power transmission element such as a chain, and the regenerative charging is enabled.

  Although not shown, a center one-way clutch is provided between the crankshaft and the crank sprocket that locks in the direction in which the driving force is transmitted and idles with respect to the reverse input. For this reason, the driving force is not transmitted to the crankshaft, the pedal, and the like by reverse input. As this center one-way clutch, a well-known one-way clutch such as a roller clutch, a sprag clutch or a ratchet clutch can be adopted.

  In this embodiment, it is assumed that an external force is applied from the friction member 10 to the cage 2d by a brake operation performed by the driver as an external force applied to the cage 2d. However, the external force is not limited to the brake operation. You may assume the external force by an element.

  It should be noted that the absolute rotation direction is reversed when the vehicle is not driven backward (when the bicycle is pulled down and pulled backward), but the relative rotation relationship between the rear sprocket 7 and the hub case 12 is the same as that during forward drive. The same.

  That is, according to the axial position of the slide member 8, the second one-way clutch 3 is locked in the deceleration state, and the third one-way clutch 4 is locked in the direct connection state. On the other hand, the first one-way clutch 2 is always idling.

  As described above, the speed change mechanism 5 has a function of transmitting the stepping force or the driving force generated by the motor output to the hub case 12, that is, the rear wheel that is the driving wheel, through the rear sprocket 7, and the first one-way. The clutch 2 has a function of idling when driven by the pedaling force or the output of the motor and transmitting a reverse input from the rear wheel to the rear sprocket 7 when not driven.

(Second embodiment)
A second embodiment of the present invention is shown in FIGS. In the second embodiment, the difference from the first embodiment will be mainly described. First, the speed change mechanism 5 is constituted by a planetary gear mechanism that switches between three speeds.

  Further, the first one-way clutch 2 for reverse input transmission is constituted by a roller clutch disposed between the inner ring 2c meshing with the outer ring gear 5d and the hub case 12.

  The speed change mechanism 5 includes three sun gears 5f, 5g, and 5h that are coaxially and rotatably supported on the outer periphery of the axle 11. Further, a planetary gear 5e having a three-stage gear meshing with each of the sun gears 5f, 5g, and 5h, a planet carrier 5c holding the planetary gear 5e, and an outer ring gear 5d meshing with the planetary gear 5e are provided.

  Further, a second one-way clutch 3 is incorporated between the outer ring gear 5d and the hub case 12. The inner ring 2c and the outer ring gear 5d are engaged with each other by a spline or the like.

  Any one of the sun gears 5f, 5g, and 5h can be selectively made non-rotatable with respect to the axle 11 by the speed change control device 30, and the speed change mechanism 5 has the sun gears 5f, 5g, The speed can be changed by selecting 5h.

For example, when the sun gear 5h cannot be rotated with respect to the axle 11, assuming that the number of teeth of the sun gear 5h is a and the number of teeth of the outer ring gear 5d is d, the speed increasing ratio from the planet carrier 5c to the outer ring gear 5d is (A + d) / d.
At this time, the sun gears 5f and 5g are idle, and the sun gears 5f and 5g are not involved in torque transmission.

  That is, the sun gears 5f, 5g, and 5h have different numbers of teeth, and by making any one non-rotatable with respect to the axle 11, the speed increase ratio can be changed.

  On the other hand, the first one-way clutch 2 incorporated between the inner ring 2c and the hub case 12 is held by the elastic body 2e as in FIGS. 1 (a) and 2 (a) showing the above-described embodiment. Since the container 2d presses the roller 2a toward the deeper side of the groove 2f (the direction in which the wedge space expands), it is normally in an idle state.

When driving force is input to the rear sprocket 7 during forward drive (the state shown in FIG. 3), torque is transmitted in the order of the planet carrier 5c, the planetary gear 5e, the outer ring gear 5d, the second one-way clutch 3, and the hub case 12. The
At this time, the first one-way clutch 2 is idling. In a normal state (a state where no external force is applied to the cage 2d), the cage 2d biased by the elastic body 2e presses the roller 2a toward the deeper side of the groove 2f (the direction in which the wedge space expands). This is because the first one-way clutch 2 is not locked against rotational input in both directions.

  Further, when the vehicle is not driven forward (for example, a situation where the bicycle is lowered on a hill without stroking the pedal / the state shown in FIG. 4), reverse input torque is applied to the rear hub 1 from the tire side. At this time, since the second one-way clutch 3 runs idle, the reverse input torque cannot be transmitted through the second one-way clutch 3.

  On the other hand, at this time, the first one-way clutch 2 is in a normal state (holding state) because the cage 2d biased by the elastic body 2e presses the roller 2a toward the deeper groove 2f (the direction in which the wedge space spreads). In a state where no external force is applied to the container 2d), the wheel is idling.

However, when force is applied from the friction member 10 to the cage 2d by the brake operation performed by the driver, the cage 2d overcomes the bias of the elastic body 2e and rotates relative to the outer ring 2b in the backward direction.
When the roller 2a is in a standby state at a shallow position of the outer ring groove 2f due to this relative rotation, the rotation speed of the outer ring 2b is higher than the rotation speed of the inner ring 2c (non-driven state). The first one-way clutch 2 is locked in the wedge space formed by the groove 2f of 2b, and the hub case 12 and the rear sprocket 7 are directly connected.

  As a result, the reverse input torque from the tire of the rear wheel that is the drive wheel is transmitted from the rear sprocket 7 to the motor shaft through a power transmission element such as a chain, and the regenerative charging is enabled.

  In addition, the structure of the said speed change control apparatus 30 employ | adopts the following structure in this embodiment. That is, as shown in FIGS. 3 (a) and 3 (b), the speed change control device 30 has a shaft member 30b inserted through a shaft hole 11a provided in the axle 11 so as to be able to advance and retreat in the axial direction. A snap key 30a protruding in the radial direction is provided. An elastic member 30b is accommodated in the inner part of the shaft hole 11a. In this embodiment, a coil spring is employed as the elastic member 30c.

  Further, a plurality of grooves 5i as shown in FIGS. 3A and 4A are formed in the inner diameter portions of the sun gears 5f, 5g, and 5h, respectively, along the circumferential direction. The snap key 30a can selectively engage with any one of the sun gears through the groove 5i, and any one of the sun gears 5f, 5g, 5h cannot rotate with respect to the axle 11. And

As described above, FIG. 3A shows the state when the driving force is transmitted from the rear sprocket 7, while FIG. 4A shows the case where the reverse input from the tire is transmitted. Shows the state.
Since the direction of the torque applied to the sun gear is reversed when the driving force and the reverse input are applied, the grooves 5i of the sun gears 5f, 5g, and 5h and the snap key 30a are configured to lock against the torque in both directions. .

  When the first one-way clutch 2 is locked during forward non-drive, the reverse input from the tire is transmitted in the order of the hub case 12, the first one-way clutch 2, the inner ring 2c, the outer ring gear 5d, the planetary gear 5e, the planetary carrier 5c, and the rear sprocket 7. Then, it is transmitted to the motor shaft through a power transmission element such as a chain, and regenerative charging is possible.

  The selection of the sun gears 5f, 5g, and 5h with which the planetary gear 5e is engaged is performed by moving the shaft member 30b and the snap key 30a in the axial direction relative to the axle 11 through the shaft hole 11a of the axle 11 from the outside. By changing the sun gears 5f, 5g, and 5h with which the snap key 30a is engaged, can be performed.

(Third embodiment)
A third embodiment is shown in FIG. In this embodiment, the outer ring gear 5d and the inner ring 2c of the first one-way clutch 2 are formed as an integral member. The basic operation is the same as in the second embodiment.

(Fourth embodiment)
A fourth embodiment is shown in FIG. In this embodiment, the speed change mechanism 5 is constituted by a planetary gear mechanism that switches between three speed reductions, and the first one-way clutch 2 for reverse input transmission is constituted by a roller clutch between the hub case 12 and the inner ring 2c. .

  The inner ring 2c meshes with the planet carrier 5c through a spline. In this case, the driving force from the pedal is decelerated and transmitted from the rear sprocket 7 of the rear hub 1 in the order of the outer ring gear 5d, the planetary gear 5e, the planet carrier 5c, the second one-way clutch 3, and the hub case 12. Other basic operations are the same as those in the second embodiment.

(Fifth embodiment)
A fifth embodiment of the present invention is shown in FIG. In the fifth embodiment, as in the fourth embodiment, the speed change mechanism 5 is constituted by a planetary gear mechanism that switches between three speeds. Further, the first one-way clutch 2 for transmitting reverse input is constituted by a roller clutch between the hub case 12 and the outer ring gear 5d. Other basic operations are the same as those in the second embodiment.

DESCRIPTION OF SYMBOLS 1 Rear hub 2 1st one-way clutch 2a Roller 2b Outer ring 2c Inner ring 2d Cage 2e Elastic body 2f Groove 3 Second one-way clutch (Ratchet clutch)
4 Third one-way clutch (Ratchet clutch)
5 Transmission mechanism 5a, 5f, 5g, 5h Sun gear 5b, 5e Planetary gear 5c Planet carrier 5d Outer gear 6 Elastic member 7 Rear sprocket 8 Slide member 9 Seal 10 Friction member 11 Axle 11a Shaft hole 12 Hub cases 13, 14, 15 Bearing Part 30 Transmission control mechanism 30a Snap key

Claims (14)

A secondary battery and an auxiliary drive motor are attached to the frame connecting the front wheel and the rear wheel, so that 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. In the battery-assisted bicycle provided with a regeneration mechanism that returns the regenerative power generated by the reverse input from the wheel to the output shaft of the motor to the secondary battery,
A hub (1) provided on the drive wheel is provided with a speed change mechanism (5) and a first one-way clutch (2). The speed change mechanism (5) generates a driving force generated by the pedaling force or the output of the motor using a sprocket ( 7) has a function of transmitting to the driving wheel through the first one-way clutch (2) idles when driven by the pedaling force or the output of the motor, and reverse input from the driving wheel when not driven. A battery-assisted bicycle equipped with a regenerative mechanism characterized by having a function of transmitting to the sprocket (7).   The transmission mechanism (5) includes a sun gear (5a) provided on the outer periphery of the axle (11), a planetary gear (5b) meshing with the sun gear (5a), and a planet carrier that holds the planetary gear (5b). (5c) and an outer ring gear (5d) meshing with the planetary gear (5b), and at the time of deceleration, the sun gear (5a) is a fixed member, the outer ring gear (5d) is an input member, and the planet carrier (5c). 2 is a two-stage planetary gear reducer using the outer ring gear (5d) as an input / output member at constant speed. bicycle.   A slide member (8) that is movable in the axial direction with respect to the axle (11) of the drive wheel is provided, and the speed change mechanism (5) is switched by moving the slide member (8) in the axial direction. An electrically assisted bicycle comprising the regeneration mechanism according to claim 2.   The transmission mechanism (5) includes a plurality of the sun gears (5a; 5f, 5g, 5h), and any one of the plurality of sun gears (5a; 5f, 5g, 5h) is a fixed member, and the outer ring gear ( 5d) is an input member, and the planet carrier (5c) is an output member, thereby comprising a reduction gear including a combination of gears having a plurality of gear ratios, and a plurality of the sun gears (5a; 5f, 5. The battery-assisted bicycle with a regenerative mechanism according to claim 1, further comprising a shift control mechanism (30) having a function of selecting any one of 5 g and 5 h) as the fixing member.   The transmission mechanism (5) includes a plurality of the sun gears (5a; 5f, 5g, 5h), and any one of the plurality of sun gears (5a; 5f, 5g, 5h) is fixed to the planet carrier ( 5c) is an input member, and the outer ring gear (5d) is an output member, thereby comprising a gearbox having a combination of gears having a plurality of gear ratios, and a plurality of sun gears (5a; 5f). , 5g, 5h). The battery-assisted bicycle provided with the regeneration mechanism according to claim 1, further comprising a shift control mechanism (30) having a function of selecting any one of the fixing members as the fixing member.   The shift control mechanism (30) is configured to reversely input any one of the plurality of sun gears (5a; 5f, 5g, 5h) rotatably supported around the axle (11) from a driving force and a tire. 6. The electric motor equipped with a regenerative mechanism according to claim 4, wherein the motor has a function of switching gears so as to be rotatable or non-rotatable around the axle (11). Auxiliary bicycle.   The shift control mechanism (30) includes a snap key (30a), and shifts the shift of the shift mechanism (5) through the axle (11) to move the snap key (30a) in the axial direction from the outside. Any of the sun gears (5a; 5f, 5g, 5h) with which the snap key (30a) meshes cannot rotate around the axle (11) with respect to both the driving force and the reverse input from the tire. The battery-assisted bicycle provided with the regeneration mechanism according to claim 6.   The battery-assisted bicycle with a regenerative mechanism according to any one of claims 1 to 7, wherein the first one-way clutch (2) is engaged in conjunction with a brake operation.   The battery-assisted bicycle with a regeneration mechanism according to any one of claims 1 to 8, wherein the first one-way clutch (2) is a roller clutch.   The battery-assisted bicycle with a regeneration mechanism according to any one of claims 1 to 8, wherein the first one-way clutch (2) is a sprag clutch.   A center one-way clutch is provided between the crankshaft and the crank sprocket, the center one-way clutch locking in a direction in which a driving force is transmitted to the driving wheel and idling in response to a reverse input from the driving wheel. A battery-assisted bicycle comprising the regeneration mechanism according to any one of 10 above.   The battery-assisted bicycle with a regenerative mechanism according to claim 11, wherein the center one-way clutch is a roller clutch.   12. The battery-assisted bicycle with a regenerative mechanism according to claim 11, wherein the center one-way clutch is a sprag clutch.   12. The battery-assisted bicycle with a regenerative mechanism according to claim 11, wherein the center one-way clutch is a ratchet clutch.

Images