WO2012132927A1

WO2012132927A1 - Hub unit for bicycle, electrically assisted bicycle using hub unit for bicycle, and electric two-wheeled vehicle using hub unit for bicycle

Info

Publication number: WO2012132927A1
Application number: PCT/JP2012/056683
Authority: WO
Inventors: 大場　浩量; 潔洋伊藤
Original assignee: Ntn株式会社
Priority date: 2011-03-29
Filing date: 2012-03-15
Publication date: 2012-10-04

Abstract

A device configured so that the device is compact and the drag torque of a motor is reduced. A transmission mechanism section (30), a speed reduction mechanism section (40), and a drive motor (18) are provided within a hub (10) so as to be arranged side-by-side along an axle (15). The transmission mechanism section (30) transmits the drive force of human power to a hub case (11), and the speed reduction mechanism section (40) transmits the drive force of the drive motor (18) to the hub case (11). The transmission mechanism section (30) is provided with a sun gear (30a) for a transmission, planetary gears (30b) for a transmission, and a planetary carrier (30c) for a transmission, and the planetary carrier (30c) for a transmission serves as an output member for providing an output to the hub case (11). The speed reduction mechanism section (40) is provided with a sun gear (40a) for a speed reducer, planetary gears (40b) for a speed reducer, and an outer ring gear (40d) for a speed reducer. The planetary gears (40b) for a speed reducer are meshed with the outer ring gear (40d) for a speed reducer. The planetary carrier (30c) for a transmission, the planetary carrier (30c) holding the planetary gears (40b) for a speed reducer, serves as an output member for providing an output to the hub case (11). A switching clutch (20) is provided between the outer ring gear (40d) for a speed reducer or a planetary carrier (40c) for a speed reducer and the motor housing (18b) of the drive motor (18).

Description

Bicycle hub unit, and battery-assisted bicycle and electric motorcycle using the same

The present invention relates to an electrically assisted bicycle or an electric motorcycle that adds an assisting force to a human power drive system by an electric motor, a bicycle hub unit used in the electrically assisted bicycle or an electric motorcycle, and an electrically assisted bicycle and an electric motor using the same. It relates to motorcycles.

There are various types of bicycle transmissions. Under such circumstances, generally, a multi-stage sprocket is provided on the same axis of either the crankshaft or the rear axle, or both, and the speed is changed by moving the chain between the sprockets by a derailleur (exterior gear shifting). And a system (internal transmission) that changes gears by switching gears provided in the rear hub of the rear wheel that is a driving wheel.

The exterior transmission has a simple structure and is lightweight, but it may cause the sprocket and chain to wear and cause the chain to come off. On the other hand, internal transmissions are often used in city cycles because they have excellent dust and water resistance and are maintenance-free.

By the way, in an electrically assisted bicycle or an electric motorcycle (hereinafter collectively referred to as an electrically assisted bicycle) in which an assisting force is applied to a human power drive system by an electric motor, a driving wheel is installed in a rear hub of a rear wheel that is a drive wheel of the electrically assisted bicycle. Some have a motor, a speed reduction mechanism, and a speed change mechanism.

A so-called rear hub motor type battery-assisted bicycle provided with a motor at the rear hub can use either an exterior transmission or an interior transmission when combined with a transmission mechanism.
However, when the exterior transmission is used, the structure of the hub is mainly composed of the drive motor and the speed reduction mechanism, and thus becomes simple. However, there is a problem in maintenance due to the exterior transmission as described above. On the other hand, when an internal transmission is used, the hub structure is composed of a motor, a speed reduction mechanism, and a transmission mechanism, so the structure of the hub itself is complicated. This is advantageous.

At present, battery-assisted bicycles are developed mainly in the city cycle, and most of them adopt an internal transmission. Therefore, it is considered that it is desirable to use an internal transmission even in a rear hub motor type battery-assisted bicycle.
Examples of the structure of a battery-assisted bicycle provided with this type of internal transmission include those described in

Patent Documents

1 and 2, for example.

In these structures, a drive motor (electric motor), a speed reduction mechanism, and a speed change mechanism are arranged in the rear hub. As a drive mechanism using a motor, a drive motor and a power system speed reduction mechanism for reducing the rotational speed of the drive motor are incorporated. As a human power input mechanism, an input sprocket is provided on the axle of the drive wheel, and a speed change mechanism and a speed reduction mechanism are arranged in this order from the axle toward the outer periphery.
The rear hub includes a rotating casing and a fixed casing. The human-powered input mechanism is disposed on the rotating casing side, and the driving mechanism using the driving motor is mainly disposed on the fixed casing side.

The human power given by the pedal is transmitted to the sprocket of the driving wheel by the chain, is shifted by the speed change mechanism, and rotates the driving wheel through the rotating casing. In addition, the driving force by the motor is decelerated by the speed reduction mechanism portion of the power system provided separately from the above-described transmission mechanism portion of the human power system, and then the human power driving force and the electric driving force are combined in the rotating casing, It is transmitted to the drive wheel.
At this time, the driving force by the human power converted into the electric signal and the electric signal of the running speed from the speed sensor are input to the control unit included in the battery-assisted bicycle, and the control unit is based on a predetermined condition. Then, a drive signal is output to control the motor.

However, in these structures, the motor is arranged at a position eccentric from the axle center of the axle or at a position far away from the axle to the outer diameter side. For this reason, there exists a problem that the outer diameter of a hub becomes large. If the outer diameter of the hub is large, the weight balance tends to deteriorate.

In this regard, according to the structure described in

Patent Documents

3 and 4, the reduction mechanism, the drive motor, and the transmission mechanism are arranged along the axis of the axle. Can be suppressed.

JP-A-9-58568 JP 2000-043780 A JP 2002-293285 A JP 2003-160089 A

However, in Patent Document 3, in consideration of the assembling property, the work of assembling the drive motor and the speed reduction mechanism is separate from the work of assembling the internal transmission in the lid that closes the end surface of the hub case. It is crowded. That is, the speed reduction mechanism portion and the speed change mechanism portion are completely configured as separate units. Since the space in the axial direction in the hub case is limited, in such a configuration, it is difficult to secure a space for arranging the speed change mechanism portion, and it is difficult to increase the number of speed steps.

In Patent Document 4, the drive motor is arranged between the speed reduction mechanism and the speed change mechanism. In such a configuration, it is difficult to arrange the power supply and control wiring of the motor, and the structure is complicated. Furthermore, the speed reduction mechanism portion and the speed change mechanism portion are configured independently of each other, and it is difficult to increase the number of speed steps as in Patent Document 3.
In addition, motor-assisted bicycles have a range of speeds that can be assisted by motor driving. If the auxiliary motor does not operate due to speeds exceeding this range or due to battery exhaustion, etc., the motor is dragged by the speed reduction mechanism. There is a problem that the torque increases and the running resistance increases.

In view of this, the present invention has a configuration in which the three mechanisms of the speed reduction mechanism, the drive motor, and the speed change mechanism are provided in parallel along the axis of the axle, and the device is compact and the auxiliary motor does not operate. It is an object to suppress the drag torque of the motor.

In order to solve the above problems, the present invention provides a bicycle hub unit in which a speed change mechanism, a speed reduction mechanism, and a drive motor are arranged in parallel in the axial direction of an axle inside the hub. Has a function of transmitting the driving force due to human power input to the input means to the hub case, and the speed reduction mechanism portion has a function of transmitting the driving force input from the driving motor to the hub case, The speed change mechanism portion is constituted by a planetary gear mechanism having two or more speed stages, and at least one transmission sun gear, a transmission planetary gear meshing with the transmission sun gear, and the transmission A planetary gear carrier for transmission that holds the planetary gear, and the at least one transmission sun gear is turned around the axle or not rotatable with respect to the driving force from the input means. A speed change control mechanism for performing speed change, wherein the speed reduction mechanism is configured by a planetary gear mechanism and rotates integrally with a motor shaft of the drive motor; and a gear for the speed reducer A reduction gear planetary gear meshing with the sun gear, and a switchable outer ring gear for reduction gear meshing with the planetary gear for reduction gear and a motor housing holding the drive motor, which can be switched to be relatively rotatable or relatively non-rotatable. The transmission planetary carrier is held by the transmission planetary carrier, which is an output member to the hub case of the transmission mechanism unit, so that the planetary carrier for transmission is connected to the hub case of the reduction mechanism unit. A bicycle hub unit is used, which is characterized by being an output member.

According to this configuration, the planetary gear mechanism is employed in each of the transmission mechanism unit and the reduction mechanism unit, and the planetary gear for reduction device is held by the planetary carrier for transmission which is an output member to the hub case of the transmission mechanism unit. Since the planetary carrier for transmission is used as an output member to the hub case of the speed reduction mechanism, it is possible to make the structure compact in the axle direction by using the common member.

In addition, since a switching clutch is provided between the outer ring gear for the reduction gear that meshes with the planetary gear for the reduction gear and the motor housing that holds the drive motor, the drag torque of the motor when the auxiliary motor does not operate is suppressed. be able to.

Here, for example, the structure of the speed change mechanism portion can be a reduction type including a direct connection state from the input member to the hub case. Further, the structure of the speed change mechanism portion may be a reduction type including a direct connection state from the input member to the hub case and a reduction state of two or more stages.

As a configuration of the shift control mechanism unit that switches two or more shift stages of the planetary gear mechanism, for example, a clutch member is provided between the sun gear for transmission and the axle, and this clutch member (first one-way clutch for transmission) The transmission sun gear can be shifted by switching between a state in which the transmission sun gear can rotate in one direction around the axle and a state in which the transmission sun gear cannot rotate.

In addition, for example, another clutch member is provided between the outer ring gear for transmission that is connected to the input means and meshes with the planetary gear for transmission, and the planetary carrier for transmission that holds the planetary gear for transmission. The transmission control mechanism switches the outer ring gear for transmission to a state in which it cannot rotate in one direction around the axis with respect to the planetary carrier for transmission, so that the constant speed (direct connection) state from the input means to the planetary carrier for transmission It is possible to change the speed.
Normally, a battery-assisted bicycle often travels with a top gear having the largest gear ratio (for example, the state of the third speed in the case of a three-speed shift). High stability and significant improvement in durability. In addition, by increasing the number of stages of the planetary gear and further providing the same number of sun gears according to the number of stages of the planetary gear, it is possible to increase the number of transmissions to 4, 5, and 6.

Further, in each of these configurations, if the axle is a single member that is fixed to both ends of the bicycle frame, the rigidity of the entire rear hub unit is secured by the axle being completely fixed to the frame by supporting both ends. The drive motor can be stably rotated by being completely fixed to the axle.

Furthermore, in each of these configurations, for example, a configuration in which the switching clutch is a two-way clutch can be employed. Further, as the switching clutch, for example, a roller clutch, a sprag clutch, or a clutch provided with a ratchet mechanism (a ratchet clutch) can be employed. By using a roller clutch or a sprag clutch for this two-way clutch, it becomes possible to reduce the amount of play, and by using a ratchet mechanism, the structure can be simplified.

In each of these configurations, the switching clutch can always be engaged with the rotation of the planetary carrier for the speed reducer with respect to the motor housing when the bicycle moves forward by the input of the driving force from the driving motor. For the rotation in the opposite direction, it is possible to adopt a configuration that can be switched between an engageable state and an unengageable state by an input for instructing switching transmitted from the outside.

That is, when the driving force from the driving motor is applied, the outer ring gear for the speed reducer of the speed reduction mechanism unit is always made non-rotatable with respect to the motor housing by the two-way clutch (reverse torque). It will idle during operation). Since the drive motor is rotationally fixed with respect to the axle, the reduction gear outer ring gear is also rotationally fixed. Accordingly, the driving force is transmitted from the drive motor to the output member (transmission planetary carrier) via the reduction gear sun gear and the reduction gear planetary gear, and the output member and the hub case are coupled so as to be integrally rotatable. Torque is transmitted to the drive wheels. Thereby, driving | running | working by auxiliary force is attained.

Also, when the auxiliary force from the drive motor is unnecessary or cannot be obtained, such as when the battery is dead, the outer ring gear for the speed reducer is driven from the drive motor to the motor housing by the drive force of human power. It rotates in the opposite direction to when moving forward with force. In this state, the reduction gear outer ring gear of the reduction mechanism portion is made rotatable with respect to the motor housing, that is, the reduction gear planetary outer gear rotates idly with respect to the motor housing. As a result, comfortable driving without drag resistance of the drive motor is possible.

Furthermore, for reverse input from the drive wheels when the bicycle travels by inertia, similarly, the outer ring gear for the speed reducer is in the opposite direction to that when moving forward with the drive force from the drive motor with respect to the motor housing. Rotate. In this state, the two-way clutch is engaged by an input transmitted from the outside, and the outer ring gear for the speed reducer of the speed reduction mechanism is made incapable of rotating relative to the motor housing. Thereby, the reverse input from the drive wheel is transmitted to the drive motor via the speed reduction mechanism, and regenerative charging is possible.

Therefore, it is only necessary to switch the switching clutch from the engageable state to the disengageable state only when regeneration is necessary, and the internal structure of the hub can be simplified. The switching clutch can be switched by, for example, an external electric signal input, but can also be switched by a mechanical operation (input) such as advancing / retreating operation or rotating operation of the member. is there.

In any case, it is possible to regenerate only during braking by linking the switching with the brake operation. At this time, the input from the outside can be transmitted by the switching clutch control mechanism that operates in conjunction with the brake operation. As a configuration of the switching clutch control mechanism unit, for example, the switching can be performed by utilizing the advance / retreat operation of a wire or the like interlocking with the brake operation and the rotation operation (input) of the members configuring the link mechanism.

Furthermore, a configuration is adopted in which the switching clutch is switched based on a plurality of elements (the presence / absence of a brake operation, the number of revolutions, and the numerical value of the pedal torque) when the plurality of elements satisfy a predetermined requirement. be able to. By using a plurality of elements as a reference for switching, it becomes possible to obtain more comfortable traveling.

For example, when a clutch provided with a ratchet mechanism is employed as the switching clutch, the ratchet mechanism includes a first ratchet portion that engages in only one direction around the axis of the planetary carrier for the reducer with respect to the motor housing. The second ratchet portion can be configured to engage only in the rotation in the direction opposite to the engagement direction of the first ratchet portion.

At this time, the first ratchet portion is always in an engageable state with respect to the rotation of the planetary carrier for the speed reducer with respect to the motor housing when the bicycle is advanced by the input of the driving force from the driving motor, The second ratchet portion can be configured to be able to switch between an engageable state and an unengageable state by an input transmitted from the outside when no driving force is input from the drive motor.

In each of these configurations, the motor housing can be configured to be held on a bicycle frame or axle so as not to be relatively rotatable.

Further, in each of these configurations, the input means is provided on one end side of the axle, the drive motor is provided on the other end side of the axle, and the speed change mechanism portion and the speed reduction mechanism portion are provided on the input means and the drive side. A configuration provided between the motor and the motor can be employed.
If the speed change mechanism portion and the speed reduction mechanism portion are provided between the sprocket on one end of the axle and the drive motor on the other end, the planetary carrier for transmission and the planetary carrier for reduction gear are close to each other. Can be further simplified. The drive motor is completely fixed to the axle that is supported on both ends of the bicycle, thereby ensuring high rigidity of the entire hub unit.

Further, in each of these configurations, the transmission mechanism portion includes an outer ring gear for transmission that rotates integrally with a drive body that transmits the driving force from the input means, and the planetary gear for transmission is engaged with the transmission planetary gear. Torque is joined from the outer periphery of the planet carrier to the inner diameter of the hub case, and the driving force from the input means is transmitted from the driver to the hub case through the transmission planetary gear, the transmission planet carrier, etc. It is possible to adopt a decelerating configuration that is transmitted at a lower speed.

At this time, the drive body and the outer ring gear for transmission can be formed as an integral member, but the drive body and the outer ring gear for transmission are separate members, and the drive of the separate member is performed. The body and the outer ring gear for transmission can be held by a joint that can rotate integrally.

When the driving body and the transmission outer ring gear are separate members, the driving body and the transmission outer ring gear can be configured to be held so as to be relatively movable in the radial direction. If the drive body and the outer ring gear for transmission can be moved relative to each other in the radial direction, manufacturing errors and assembly errors that can occur in the drive body and the outer ring gear for transmission can be absorbed by the relative movement. A good balance can be maintained between the gears engaged with each other in the gear mechanism.
Although it is desirable that the planetary gear is ideally driven concentrically, in reality, each gear includes a manufacturing error. Due to manufacturing errors, an excessive load may be applied to a specific gear, which may reduce durability. Therefore, the above-described configuration that can absorb these manufacturing errors is preferable.

That is, here, the drive body to which the input member is coupled and the outer ring gear for the transmission are made separate members, each having a degree of freedom in the radial direction while being able to rotate integrally. In addition, since the driving body is rotatably supported on the axle by a bearing, the outer ring gear of the transmission moves in the radial direction, so that the planetary gear mechanism can have a load balanced arrangement.

Further, in each of these configurations, the reduction mechanism portion includes a first outer gear portion provided on the reduction gear planetary gear meshes with the reduction gear sun gear, and is provided on the reduction gear planetary gear. A configuration in which a second outer gear portion having a smaller number of teeth than the one outer gear portion meshes with the outer ring gear for a reduction gear can be employed.
Thus, by using the planetary gears for two speed reducers with different numbers of teeth for the planetary gear mechanism of the speed reduction mechanism unit, it is possible to achieve a high reduction ratio with a compact structure.

Further, in each of these configurations, if the number of the planetary gears for transmission is the same as the number of the planetary gears for reduction gears, the periphery of the axle in the transmission mechanism unit that mainly transmits the driving force by human power from the input means This is desirable because the load balance around the axle is close to the load balance around the axle in the speed reduction mechanism that mainly transmits the driving force from the drive motor.

For example, if the number of planetary gears for transmission is three, the load balance around the axle when the driving force is transmitted becomes the best. At this time, it is desirable that the number of planetary gears for reduction gears is also the same number.

Further, in each of these configurations, the shift control mechanism section relatively rotates the first one-way clutch for transmission that can make the at least one transmission sun gear unrotatable in one direction around the axle. It is possible to adopt a configuration that can be switched so that it can be rotated or cannot be relatively rotated.

Furthermore, a bicycle hub unit composed of each of these components can be incorporated, and an auxiliary force can be added to the human-powered drive system by an electric motor, and an electrically assisted bicycle or an electric motorcycle equipped with a regeneration mechanism can be obtained.

In order to solve the above-described problems, the present invention provides a bicycle hub unit in which a speed change mechanism, a speed reduction mechanism, and a drive motor are arranged in parallel in the axial direction of an axle inside the hub. The mechanism portion has a function of transmitting a driving force by human power input to the input means to the hub case, and the speed reduction mechanism portion has a function of transmitting the driving force input from the driving motor to the hub case. The transmission mechanism portion is constituted by a planetary gear mechanism having two or more speed stages, and at least one transmission sun gear, the transmission planetary gear meshed with the transmission sun gear, and the speed change thereof A planetary gear carrier for transmission that holds a planetary gear for a machine, and the at least one transmission sun gear can be rotated around the axle or not rotatable with respect to the driving force from the input means. A speed change control mechanism that changes gears, and the speed reduction mechanism is configured by a planetary gear mechanism and is configured with at least one speed reducer sun gear and a speed reducer planetary gear that meshes with the speed reducer sun gear. The reduction gear planetary gear is engaged with the reduction gear outer ring gear provided on the transmission planet carrier or a member that rotates integrally with the transmission planet carrier, and the reduction gear sun gear. And a switching clutch capable of switching between a motor housing holding the drive motor and a member fixed to the motor housing so as to be relatively rotatable or not relatively rotatable. A hub unit for rotation was adopted.

According to this configuration, a planetary gear mechanism is employed in each of the speed change mechanism portion and the speed reduction mechanism portion, and the speed reducer provided on a transmission planet carrier for the speed change mechanism portion or a member that rotates integrally with the planet carrier for the transmission. Since the planetary gear for the speed reducer of the speed reduction mechanism is meshed with the outer ring gear for use, it is possible to make the structure compact in the axle direction by sharing the members.

In addition, the drag torque of the motor when the auxiliary motor does not operate can be suppressed by providing a switching clutch between the outer ring gear for the speed reducer meshing with the planetary gear for the speed reducer and the motor housing holding the drive motor. Can do.

Note that, as a configuration of the shift control mechanism unit that switches two or more shift stages of the planetary gear mechanism, a clutch member is provided between the transmission sun gear and the axle, and this clutch member (first one-way for transmission) is provided. It is possible to adopt a configuration in which the transmission sun gear can be shifted by switching between a state in which the sun gear for transmission can rotate in one direction around the axle and a state in which it cannot rotate. *

In addition, another clutch member is provided between the outer ring gear for transmission that is connected to the input means and meshes with the planet gear for transmission, and the planet carrier for transmission that holds the planet gear for transmission. The control mechanism switches the outer ring gear for transmission to a state where it cannot rotate in one direction around the axis with respect to the planetary carrier for transmission, thereby shifting from the input means to the planetary carrier for transmission at a constant speed (direct connection) state. can do.

In this configuration, for example, a configuration in which the switching clutch is a two-way clutch can be employed. Further, as the switching clutch, for example, a roller clutch, a sprag clutch, or a clutch provided with a ratchet mechanism (a ratchet clutch) can be employed.

In each of these configurations, the switching clutch is always involved in the rotation of the reduction gear planet carrier or the reduction gear outer ring gear with respect to the motor housing when the bicycle moves forward by the input of the driving force from the driving motor. It is possible to switch between an engageable state and a non-engageable state by an input for instructing a switch transmitted from the outside for rotation in the opposite direction. it can.

That is, when the driving force from the driving motor is applied, the planetary carrier for the speed reducer or the outer ring gear for the speed reducer of the speed reduction mechanism is always in a state in which it cannot rotate with respect to the motor housing by the two-way clutch. Deploy. Thereby, driving | running | working by auxiliary force is attained.

In addition, when the auxiliary force from the drive motor is unnecessary or cannot be obtained, such as when the battery runs out, the planetary carrier for the speed reducer or the outer ring gear for the speed reducer is applied to the motor housing by the driving force of human power. It rotates in the opposite direction to when moving forward with the driving force from the drive motor. In this state, the planetary carrier for the speed reducer or the outer ring gear for the speed reducer of the speed reduction mechanism is made rotatable with respect to the motor housing, that is, the planetary carrier for the speed reducer or the outer ring gear for the speed reducer is set to the motor housing. Idle. As a result, comfortable driving without drag resistance of the drive motor is possible.

Further, for reverse input from the drive wheel when the bicycle travels by inertia, the planetary carrier for the speed reducer or the outer ring gear for the speed reducer advances similarly to the motor housing by the driving force from the drive motor. It rotates in the opposite direction. In this state, the two-way clutch is engaged by an input transmitted from the outside, and the planetary carrier for the speed reducer or the outer ring gear for the speed reducer of the speed reduction mechanism is made non-rotatable with respect to the motor housing. Thereby, the reverse input from the drive wheel is transmitted to the drive motor via the speed reduction mechanism, and regenerative charging is possible.

In any case, it is possible to regenerate only during braking by linking the switching with the brake operation. At this time, the input from the outside can be transmitted by the switching clutch control mechanism that operates in conjunction with the brake operation. As a configuration of the switching clutch control mechanism, for example, it is configured to make use of a forward / backward movement of a wire or the like interlocking with a brake operation and a rotation operation (input) of a member constituting the link mechanism to perform the switching. Can do.

When a clutch provided with a ratchet mechanism is employed as the switching clutch, the ratchet mechanism is engaged only in one direction around the axis of the planetary carrier for reducer or the outer ring gear for reducer with respect to the motor housing. One ratchet portion and a second ratchet portion that engages only in rotation in a direction opposite to the engagement direction of the first ratchet portion can be configured.

At this time, the first ratchet portion can always be engaged with the rotation of the reduction gear planetary carrier or the reduction gear outer ring gear with respect to the motor housing when the bicycle advances by the input of the driving force from the driving motor. The second ratchet portion can be switched between an engageable state and a non-engageable state by an input transmitted from the outside when the driving force is not input from the drive motor. can do.

Also, in each of these configurations, the input means is provided on one end side of the axle, the drive motor is provided on the other end side of the axle, and the speed change mechanism portion and the speed reduction mechanism are provided on the input means and the drive side. A configuration provided between the motor and the motor can be employed.
If the speed change mechanism and the speed reduction mechanism are provided between the sprocket on one end of the axle and the drive motor on the other end, the planetary mechanism for transmission and the planetary mechanism for speed reducer are close to each other. The structure for standardizing can be further simplified. The drive motor is completely fixed to the axle that is supported on both ends of the bicycle, thereby ensuring high rigidity of the entire hub unit.

Further, in each of these configurations, the transmission mechanism portion includes an outer ring gear for transmission that rotates integrally with a drive body that transmits the driving force from the input means, and the planetary gear for transmission is engaged with the transmission planetary gear. An outer diameter gear portion provided on the outer periphery of the planet carrier meshes with an inner diameter gear portion provided in the hub case, and the driving force from the input means is transmitted from the drive body to the planetary gear for transmission and the planetary gear for transmission. It is possible to adopt a decelerating configuration that is transmitted to the hub case through the carrier at a constant speed or less.

When the drive body and the transmission outer ring gear are separate members, the drive body and the transmission outer ring gear can be configured to be relatively movable in the radial direction. If the drive body and the outer ring gear for transmission can be moved relative to each other in the radial direction, manufacturing errors and assembly errors that can occur in the drive body and the outer ring gear for transmission can be absorbed by the relative movement. A good balance can be maintained between the gears engaged with each other in the gear mechanism.

Further, in each of these configurations, the reduction mechanism portion includes a first outer gear portion provided on the reduction gear planetary gear meshes with the reduction gear sun gear, and is provided on the reduction gear planetary gear. A second outer gear portion having a smaller number of teeth than the one outer gear portion meshes with an inner gear portion provided on the planetary carrier for transmission, and the speed reduction mechanism portion drives the sun gear for speed reducer. It is possible to adopt a configuration in which the transmission planetary carrier is used as an output member to the hub case as an input member for driving force from the motor for use.

According to this configuration, the planetary carrier for transmission of the speed change mechanism unit also serves as the member of the outer ring gear of the speed reduction mechanism unit or the planetary carrier for speed reducer, so that the hub can be further downsized in the axial direction.
Further, by using a two-stage gear having two gear portions having different numbers of teeth for the planetary gear for reduction gear, a high reduction ratio can be achieved.

The present invention employs a planetary gear mechanism in each of the speed change mechanism part and the speed reduction mechanism part in a configuration in which three mechanisms of a speed reduction mechanism part, a drive motor, and a speed change mechanism part are provided in parallel along the axis of the axle. Since the planetary gear for reduction gear is held by the planetary gear for transmission with the planetary carrier for transmission that is the output member to the hub case of the transmission mechanism unit, the planetary carrier for transmission is used as the output member to the hub case of the reduction mechanism unit. It becomes possible to make it a compact structure in the direction of the axle by common use.

Further, according to the present invention, a planetary gear mechanism is provided in each of the speed change mechanism portion and the speed reduction mechanism portion in a configuration in which the speed reduction mechanism portion, the drive motor, and the speed change mechanism portion are provided in parallel along the axis of the axle. Adopting, by meshing the planetary gear for reduction gear provided on the planetary gear carrier for transmission of the transmission mechanism portion or the planetary carrier for transmission gearbox with the planetary gear for reduction gear of the reduction mechanism portion, By sharing the members, it is possible to make the structure compact in the axle direction.

A longitudinal sectional view showing an embodiment of the present invention 1A is a cross-sectional view taken along the line AA in FIG. 1, FIG. 1B is a cross-sectional view taken along the line BB in FIG. 1, and FIG. 1 is an enlarged view of the main part of FIG. Longitudinal sectional view showing the first gear of the same embodiment 4A is a cross-sectional view taken along line AA in FIG. 4, FIG. 4B is a cross-sectional view taken along line BB in FIG. 4, and FIG. 4C is a cross-sectional view taken along line CC in FIG. Longitudinal sectional view showing the second gear stage of the same embodiment 6A is a cross-sectional view taken along the line AA in FIG. 6, FIG. 6B is a cross-sectional view taken along the line BB in FIG. 6, and FIG. Longitudinal sectional view showing the third gear stage of the same embodiment 8A is a sectional view taken along line AA in FIG. 8, FIG. 8B is a sectional view taken along line BB in FIG. 8, and FIG. 8C is a sectional view taken along line CC in FIG. XX sectional view of FIG. Sectional drawing which shows other embodiment of FIG. (A) is a clutch control mechanism for switching, (b) is an enlarged view of the main part showing a modification of (a). A longitudinal sectional view showing still another embodiment of the present invention (A) is a cross-sectional view taken along the line AA in FIG. 13, (b) is a cross-sectional view taken along the line BB in FIG. 13, and (c) is a cross-sectional view taken along the line CC in FIG. 13 is an enlarged view of the main part of FIG. Longitudinal sectional view showing the first gear of the same embodiment (A) is a cross-sectional view taken along the line AA in FIG. 16, (b) is a cross-sectional view taken along the line BB in FIG. 16, and (c) is a cross-sectional view taken along the line CC in FIG. Longitudinal sectional view showing the second gear stage of the same embodiment 18A is a sectional view taken along line AA in FIG. 18, FIG. 18B is a sectional view taken along line BB in FIG. 18, and FIG. 18C is a sectional view taken along line CC in FIG. Longitudinal sectional view showing the third gear stage of the same embodiment 20A is a sectional view taken along line AA in FIG. 20, FIG. 20B is a sectional view taken along line BB in FIG. 20, and FIG. 20C is a sectional view taken along line CC in FIG. XX sectional view of FIG. Sectional drawing which shows other embodiment of FIG. (A) (b) is sectional drawing which shows the example of a sprag clutch, respectively, (c) is sectional drawing which shows the example of a roller clutch. Overall view of a power-assisted bicycle or electric motorcycle

An embodiment of the present invention will be described with reference to FIGS. 1 to 12 and FIGS. 24 and 25. FIG. The battery-assisted bicycle of this embodiment is a battery-assisted bicycle of the rear hub motor type in which a drive motor 18 is provided inside a hub 10 (hereinafter referred to as “rear hub 10”) as a rear wheel. FIG. 25 shows an overall view of the battery-assisted bicycle.

It should be noted that the electric assist bicycle and the electric motorcycle are set so that the assisting ratio of the driving force by the driving motor is different from the driving force by human power, and the main structure of the driving force transmission mechanism is the same. Therefore, in the following embodiments, the configuration of the present invention that can be applied to both the battery-assisted bicycle and the electric motorcycle will be described by collectively referring to the battery-assisted bicycle and the electric motorcycle as the battery-assisted bicycle.

In this battery-assisted bicycle, when driving, that is, when a pedaling force transmitted from the crankshaft through the pedal 3 is input, the sprocket 9 of the rear wheel 2 that is a driving wheel (hereinafter referred to as “rear sprocket 9”). A driving force can be transmitted to the rear wheel 2 via a power transmission element 4 such as a chain connecting the two and the transmission mechanism 30 (see FIGS. 25 and 1). The rear sprocket 9 functions as input means for driving force by human power to the rear wheel 2.

Note that the rear hub 10 is provided with a speed change control mechanism 35 that switches the speed of the speed change mechanism 30. The shift control mechanism 35 is manually or electrically input from a shift change switch attached to the outside of the rear hub 10, for example, the handle 5 or the frame 6, and the shift stage can be switched by the input.

Further, the driving force generated by the output of the driving motor 18 as an auxiliary force is transmitted to the hub case 11 via the speed reduction mechanism 40 in the rear hub 10 and can be transmitted to the rear wheel 2.

In addition, when the bicycle is traveling forward with inertia, the reverse input from the rear wheel 2 is transmitted to the drive motor 18 via the speed reduction mechanism 40 (in the case of reverse input, the speed is increased), and the rear wheel 2 A regenerative mechanism is provided for reducing the regenerative electric power generated by the reverse input from the secondary battery 7 to the secondary battery 7 attached to the frame 6 or the like outside the rear hub 10.

As shown in FIG. 1, the rear hub 10 includes a speed change mechanism 30, a speed reduction mechanism 40, and a drive motor 18 from one end of the rear sprocket 9 in a hub case 11 provided coaxially with the axle 15 of the rear wheel 2. In order. Both ends of the axle 15 are fixed to the frame 6 of the battery-assisted bicycle, and are in a so-called both-end fixed state.

Further, the driving motor 18 is fixed to the axle 15 with no freedom by screwing or the like. The axle 15 is inserted through the central portion of the motor shaft 18 a of the drive motor 18, and the motor shaft 18 a rotates around the axle 15. The axle 15 and the motor shaft 18a are rotatably supported by a bearing 18c.

The transmission mechanism 30 is composed of a planetary gear mechanism that can change gears in a total of three stages including direct connection and two-stage deceleration. The transmission mechanism 30 includes a transmission sun gear 30a provided on the outer periphery of the axle 15 via a transmission first one-way clutch 30e. In this embodiment, the transmission sun gear 30a includes two sun gears, that is, a first sun gear 30a-1 and a second sun gear 30a-2. The first sun gear 30a-1 and the second sun gear 30a-2 are respectively connected to the outer periphery of the axle 15 via the first clutch portion 30e-1 and the second clutch portion 30e-2 of the first one-way clutch 30e for transmission. It is connected to the.

The first clutch portion 30e-1 and the second clutch portion 30e-2 are swingably provided on a shift clutch holding portion 34 that is completely fixed (fixed immovably) on the outer periphery of the axle 15, respectively. In this embodiment, the structure in which the axle 15 and the transmission clutch holding portion 34 are fixed so as not to rotate is realized by press-fitting the axle 15 having a hexagonal cross section into a hole provided in the transmission clutch holding portion 34. . Further, the transmission clutch holding portion 34 is fixed in the axial direction of the axle 15 using a retaining ring or the like.

The transmission mechanism 30 includes a transmission planetary gear 30b having two gear portions respectively meshed with the first sun gear 30a-1 and the second sun gear 30a-2, and the transmission planetary gear 30b as a planet carrier. And a planetary carrier 30c for transmission that is held via a shaft 30i. The two gear portions of the planetary gear 30b for transmission are set so that their outer diameters are different from each other and the number of teeth is different.

Furthermore, the speed change mechanism unit 30 includes a drive body 32 that rotates integrally with the rear sprocket 9 and transmits a driving force from the rear sprocket 9. An auxiliary drive body 33 having an outer ring gear 30d for transmission that meshes with the gear portion having the smaller number of teeth of the planetary gear 30b for transmission is connected to the drive body 32 so as to rotate integrally. The transmission outer ring gear 30d may be meshed with the gear portion having the larger number of teeth of the transmission planetary gear 30b.

Further, the transmission planetary carrier 30c is joined to the inner diameter portion of the hub case 11 so that torque can be transmitted.

Further, the drive body 32 and the planetary carrier 30c for transmission are connected via a second one-way clutch 31 for transmission.

In this embodiment, the driving body 32 and the auxiliary driving body 33 (transmission outer ring gear 30d) are separate members, and the driving body 32 and the auxiliary driving body 33, which are separate members, rotate together via a shaft 32a. Is held by possible bonds. Thus, if the driving body 32 and the auxiliary driving body 33 are formed as separate members, the driving body 32 that does not require relatively strong strength is an aluminum material, and an outer ring gear for a transmission that requires a hardened layer by heat treatment. The auxiliary drive body 33 provided with 30d and the clutch cam surface can be made of a different material such as a steel material, and the weight can be reduced.

Moreover, in this embodiment, the drive body 32 and the auxiliary drive body 33 are floatingly supported in a radial direction (a state in which the drive body 32 is supported with a degree of freedom in radial movement) so that the arrangement of the gears can achieve a load balance. By shifting to the position, the entire load balance can be easily obtained. Note that the driving body 32 and the auxiliary driving body 33 may be formed as an integral member.

Further, it is attached to the end face of the drive motor 18 and the ring member 17 that closes the end face of the hub case 11, between the drive body 32 and the shift control mechanism 35 provided on the outer periphery of the axle 15, between the drive body 32 and the hub case 11. Between the lid 16,

bearings

12, 13, and 14 are provided, respectively. The

bearings

12, 13, and 14 support the respective members so as to be relatively rotatable.

Also, a bearing portion 26 is provided between the motor housing 18b that holds the drive motor 18 and the outer ring gear 40d for reduction gear. The motor housing 18b and the reduction gear outer ring gear 40d are supported by the bearing portion 26 so as to be relatively rotatable. In the bearing portion 26, a plurality of rollers 26a held by a cage 26b are arranged along the circumferential direction.

By operating the transmission control mechanism unit 35, the first clutch unit 30e-1, the second clutch unit 30e-2, and the transmission second one-way clutch 31 can be switched. As a result of the switching, the first sun gear 30a-1 and the second sun gear 30a-2 rotate in one direction around the axis and the drive body 32 rotates relative to the axle 15 and the planetary carrier 30c for transmission. It is switched to an impossible state.

FIG. 1 and FIG. 2 show the state of each clutch at the third gear position (at the third speed). As shown in FIGS. 2A, 2B, and 2C, at the third speed, all the clutches are engaged with the clutch cam surface. That is, at the third speed, there is no restriction for laying down each clutch, and all the above-described three clutches are in mesh with the clutch cam surface.

In this embodiment, a ratchet clutch that is relatively inexpensive as compared with other clutch mechanisms is used for the first clutch portion 30e-1, the second clutch portion 30e-2, and the second one-way clutch 31 for transmission. Adopted. However, the types of these clutches are not limited, and other different clutches such as a roller clutch or a sprag clutch having a high backlash reduction effect (rattle prevention effect) may be used.

As shown in FIG. 2 (a), the first clutch portion 30e-1 of the first one-way clutch for transmission 30e is a first one-way clutch pawl 30f for transmission that can swing on the outer periphery of the axle 15. Claw portion 30f-1). The first clutch pawl portion 30f-1 is a first one-way clutch cam surface 30g for transmission (first cam surface portion 30g-1) provided on the inner peripheral surface of the first sun gear 30a-1 by an elastic member (not shown). It is urged in the direction of meshing. Since the first clutch pawl portion 30f-1 meshes with the first cam surface 30g-1, the first sun gear 30a-1 can be made non-rotatable only with respect to the axle 15 in one direction around the axis. Note that the first sun gear 30a-1 is always rotatable about the axle 15 (idling state) with respect to rotation in the other direction around the axis.

Similarly, as shown in FIG. 2 (b), the second clutch portion 30e-2 of the transmission first one-way clutch 30e has a first first-way clutch pawl 30f for transmission that can swing on the outer periphery of the axle 15. A second clutch pawl portion 30f-2). The second clutch pawl portion 30f-2 is a first one-way clutch cam surface 30g for transmission (second cam surface 30g-2) provided on the inner peripheral surface of the second sun gear 30a-2 by an elastic member (not shown). It is urged in the direction of meshing. Since the second clutch pawl portion 30f-2 meshes with the second cam surface 30g-2, the second sun gear 30a-2 can be made non-rotatable only with respect to the axle 15 in one direction around the axis. Note that the second sun gear 30a-2 is always rotatable about the axle 15 (idling state) with respect to rotation in the other direction around the axis.

The second clutch pawl portion 30f-2 of the second clutch portion 30e-2 can be switched ON / OFF by the rotation operation of the clutch switching member 37 provided in the transmission control mechanism portion 35. That is, if the switching state is turned OFF, the second clutch pawl portion 30f-2 of the second clutch portion 30e-2 is in a state where it cannot be engaged with the second cam surface 30g-2 (a state where it cannot be engaged). The second sun gear 30a-2 can be rotated with respect to the axle 15 with respect to rotation around the axis.

If the switching state is ON, the second clutch pawl portion 30f-2 of the second clutch portion 30e-2 is in a state (engageable state) that can be engaged with the second cam surface 30g-2, The second sun gear 30a-2 cannot rotate with respect to the axle 15 with respect to rotation in one direction around the axis.
As described above, the second sun gear 30a-2 can be switched between rotation and non-rotation with respect to rotation in one direction around the axis with respect to the axle 15.

The second one-way clutch 31 for transmission is provided so that the second one-way clutch pawl 31f for transmission can swing around a planet carrier shaft 30i that supports the planetary gear 30b for transmission on the planet carrier 30c for transmission. It has been.
The transmission second one-way clutch pawl 31f is disposed on the planetary carrier 30c for transmission toward the outer periphery, and is provided on the inner peripheral surface of the drive body 32 (auxiliary drive body 33) by an elastic member (not shown). The second one-way clutch cam surface 31g for the machine is biased in the direction of meshing. Thus, it is desirable to provide the second one-way clutch cam surface 31g for transmission on the inner peripheral surface of the drive body 32 (auxiliary drive body 33) rather than the outer peripheral surface of the planetary carrier 30c for transmission.

The second one-way clutch pawl 31f for transmission meshes with the second one-way clutch cam surface 31g for transmission, so that the planetary carrier 30c for transmission is unidirectional around the axis with respect to the drive body 32 (auxiliary drive body 33). It can be made non-rotatable only with respect to rotation. It should be noted that the transmission planet carrier 30c is always rotatable to the drive body 32 (auxiliary drive body 33) (idling state) with respect to rotation in the other direction around the axis.

In this embodiment, the second one-way clutch pawl 31f for transmission is configured to be attached to the planet carrier shaft 30i in order to improve its assemblability, but this is attached to another shaft provided on the planet carrier 30c for transmission. It is also possible to install.

As described above, when another shaft is used to support the transmission second one-way clutch pawl 31f, the transmission second one-way clutch pawl 31f includes the number of transmission planetary gears 30b (3 in this embodiment). For example, it is possible to set the number to four or more.
However, the number of the second one-way clutch pawls 31f for the transmission is two or one, so that the device can be simplified. When considering the load balance, two or more are suitable at equal intervals.

FIG. 3 shows a detailed view of the shift control mechanism unit 35. The shift control mechanism 35 includes a clutch switching member 39, a clutch switching control member 37, a clutch switching guide member 38, and a shift switching rod (shift operating unit) 36 that transmits an external signal into the rear hub unit. The end portion 36a of the shift switching rod 36 is pushed in by a signal input manually or electrically from a hand switch or the like.

The axle 15 is provided with a shift guide groove 35b. The speed change guide groove 35b has a shape twisted at a certain angle with respect to the axial direction. By pushing the speed change switch rod 36, the pin 35c held in the speed change guide groove 35b moves in the axial direction of the axle 15 while rotating around the axis of the axle 15. By the operation of the pin 35c, the clutch switching control member 37 rotates about the axis of the axle 15 by the same angle. The pin 35c receives a reaction force in the direction opposite to the pushing direction by the elastic force of the elastic member 35d disposed in the shaft hole 15a inside the axle 15. For this reason, the pin 35c is stably disposed between the shift switching rod 36 and the elastic member 35d.

Further, by the rotation operation of the clutch switching control member 37, the first one-way clutch switching portion 37a for transmission provided in the clutch switching control member 37 becomes the first clutch portion 30e-1 of the first one-way clutch 30e for transmission. , The state is switched between the state of contact with the first clutch pawl 30f-1 and the state of separation. By the switching, the swing of the first clutch pawl portion 30f-1 is controlled, and the first sun gear 30a-1 can be rotated relative to the rotation of the axle 15 in one direction or in a state where the relative rotation is impossible. Switch to

Further, the clutch switching member 39 is pressed by the transmission second one-way clutch switching portion 37b having an inclined surface provided in the clutch switching control member 37, and is movable along the axial direction of the axle 15. The clutch switching member 39 is switched between a state in which the second one-way clutch pawl 31f of the transmission is in contact with the second one-way clutch pawl 31f and a state in which the second one-way clutch 31 is separated. By the switching, the swing of the second one-way clutch pawl 31f for transmission is controlled, and the outer ring gear 30d (drive body 32, auxiliary drive body 33) for transmission and the planet carrier 30c for transmission are It switches to a state in which relative rotation is possible or relative rotation is impossible with respect to rotation in one direction.

The portions where the first one-way clutch switching unit 37a for transmission and the second one-way clutch switching unit 37b for transmission abut on each clutch pawl are tapered surfaces 39c that gradually approach the inner diameter side in one axial direction. Therefore, the force at the time of releasing the engagement can be increased from the state in which each clutch pawl is engaged with the cam surface.

Further, the clutch switching member 39 includes an elastic member 35e between the clutch switching guide member 38 provided on the outer periphery of the axle 15 or a separate member. Is released, the transmission second one-way clutch switching portion 37b is automatically disengaged from the position of the transmission second one-way clutch pawl 31f.

Next, the speed reduction mechanism unit 40 will be described. The reduction mechanism unit 40 is constituted by a planetary gear mechanism, and a reduction gear sun gear 40a provided on the outer periphery of the motor shaft 18a of the drive motor 18, and a reduction gear planetary gear engaged with the reduction gear sun gear 40a. 40b, and a reduction gear outer ring gear 40d that meshes with the reduction gear planetary gear 40b.

The motor shaft 18a and the reduction gear sun gear 40a are the same member, or the reduction gear sun gear 40a is held by a member that rotates integrally with the motor shaft 18a. Moreover, the planetary gear 40b for reduction gears implement | achieves a high reduction ratio by providing the 2-stage gear part from which the number of teeth differs.

That is, in the speed reduction mechanism section 40, the first outer diameter gear section 40e provided on the reduction gear planetary gear 40b meshes with the reduction gear sun gear 40a, and the first outer diameter gear section 40e provided on the reduction gear planetary gear 40b. The second outer diameter gear portion 40f having a smaller diameter with fewer teeth meshes with the transmission outer ring gear 40d.

As described above, the planetary carrier for transmission 30c and the hub case 11 are joined to the inner diameter portion of the hub case 11 from the outer periphery of the planetary carrier for transmission 30c so that torque can be transmitted.

Furthermore, the planetary gear 40b for reduction gear and the planet carrier 30c for transmission are connected via a planet carrier shaft 40i. That is, the carrier holding the reduction gear planetary gear 40b is the transmission planetary carrier 30c, and the transmission planetary gear 30b and the reduction gear planetary gear 40b are held by a common carrier. In this way, a compact structure is realized by holding the transmission planetary gear 30b and the reduction planetary gear 40b with a common carrier. Further, the axial dimension of the hub can be shortened, and the assembly can be simplified as compared with the case where the hub case 11 is meshed independently.

Further, since the planetary gear 40b for reduction gear is held by the planetary carrier 30c for transmission, the planetary carrier 30c for transmission has the hub case 11 in both the driving force by human power and the driving force by the driving motor 18. Functions as a common output member. In other words, the transmission mechanism 30 uses the rear sprocket 9 and the drive body 32 as input members for driving force by human power, and the planetary carrier 30c for transmission as an output member to the hub case 11. Further, the speed reduction mechanism unit 40 uses the reduction gear sun gear 40 a as an input member for driving force from the driving motor 18, and uses the transmission planetary carrier 30 c as an output member to the hub case 11.

In addition, a switching clutch 20 is provided that can switch between a reduction gear outer ring gear 40d that meshes with the reduction gear planetary gear 40b and a motor housing 18b that holds the drive motor 18 so as to be relatively rotatable or not relatively rotatable.
The reduction gear outer ring gear 40d is rotationally fixed (non-rotatably fixed) to the motor housing 18b by the switching clutch 20, so that the driving force from the driving motor 18 is output from the reduction gear sun gear 40a as an output member. The transmission planetary carrier 30 c is decelerated and output, and the driving force is transmitted to the rear wheel 2 through the hub case 11.

The rotation support of the reduction gear outer ring gear 40d to the motor housing 18b is performed by the bearing 26, and the two-way clutch provided between the motor housing 18b and the reduction gear outer ring gear 40c arranged in parallel with the bearing 26. The rotation fixed state can be set by engagement of a switching clutch 20 (hereinafter referred to as “two-way clutch 20”). The motor housing 18 b is held together with the motor 18 on the bicycle frame 6 or the axle 15 so as not to rotate relative thereto.

The two-way clutch 20 is always engaged with the retainer 24 by an elastic member (not shown) when the motor is driven (when the driving force from the driving motor 18 acts and the battery-assisted bicycle moves forward). Load is applied in the direction of matching. For this reason, the reduction gear outer ring gear 40d is rotationally fixed to the motor housing 18b.

Further, when the motor is not driven (when the battery-assisted bicycle moves forward only by driving force by human power), the cage 24 is rotated by an elastic member toward the direction of rotation together with the outer ring gear 40d for reduction gear. Therefore, the reduction gear outer ring gear 40d rotates in the direction of idling with respect to the motor housing 18b, that is, in the direction opposite to the direction in which the driving force from the driving motor 18 acts. For this reason, torque is not transmitted to the motor shaft 18a, that is, the drag torque of the drive motor 18 can be cut off.

When the battery-assisted bicycle travels inertially on a downhill or the like and is reversely input from the rear wheel 2 (hub case 11) and regenerative charging is performed by the rotational force, the two-way clutch 20 is input from the switching clutch control mechanism unit 25. Switching is made possible by (external input signal). As a result, the reverse input from the hub case 11 is transmitted to the drive motor 18 via the speed reduction mechanism 40 and can be regenerated.

The two-way clutch 20 can be switched between an engageable state and an unengageable state by a manual or electric external signal (input) transmitted to the switching clutch control mechanism unit 25. The external input is transmitted to the two-way clutch 20 by the switching clutch control mechanism 25 in conjunction with the brake operation.

In this embodiment, as shown in FIG. 12 (a), as the switching clutch control mechanism unit 25, an advancing / retreating operation of a wire or the like interlocking with a brake operation is input to the input mechanism 25a. The action member 25b is pushed to the outer diameter side against the urging force of the elastic member 25c, so that the cage 24 is loaded with an external force in the rotation direction or resistance to the rotation. When the load of the external force or resistance is equal to or greater than the biasing force of the elastic member of the cage 24, the cage 24 is delayed from the rotation of the outer ring gear 40d for the speed reducer, and the two-way clutch 20 can be switched. .

Further, for example, as shown in FIG. 12B, an electromagnetic clutch 25d or a solenoid valve 25d as the switching clutch control mechanism unit 25 arranged in the rear hub unit may be employed. An electric signal is transmitted to the electromagnetic clutch 25d and the solenoid valve 25d, and the electromagnetic clutch 25d or the solenoid valve 25d is turned on / off by the electric signal, and an external force in the rotating direction or resistance to the rotation is applied to the cage 24 of the two-way clutch 20. , The two-way clutch 20 can be controlled.

In addition, by setting the same number of

planetary gears

30b and 40b in the speed change mechanism 30 and the speed reduction mechanism 40, the inside of the speed change mechanism 30 by the driving force from the driving motor 18 and the driving force of human power. The driving force can be balanced. Further, in order to utilize a limited space, it is desirable to set the number of both

planetary gears

30b and 40b by three.

The operation of each member will be described with reference to FIG.
4 and 5 show the arrangement of the rear hub unit at the first shift (at the first speed). In this embodiment, the rear sprocket 9 is attached to the drive body 32 of the speed change mechanism unit 30, and the driving force by human power from the pedal 3 is transmitted to the drive body 32.

In the first gear stage, the first clutch portion 30e-1 of the first one-way clutch for transmission 30e is in a state that can be engaged with the driving force by the first clutch pawl portion 30f-1, One end of the second clutch portion 30e-2 is restrained by the first first-way clutch switching portion 37a for transmission of the clutch switching control member 37 and cannot be engaged.

Further, the second one-way clutch 31 for transmission is connected at its one end by a clutch switching member 39 in which the second one-way clutch pawl 31f for transmission operates through the second one-way clutch switching portion 37b for transmission of the clutch switching control member 37. It is restrained and cannot be engaged.

Therefore, the driving force by human power is input to the transmission planetary gear 30b through the driving body 32 and the auxiliary driving body 33. At this time, the first sun gear 30a-1 is driven by the first clutch portion 30e-1. Since it is engaged in the direction, the driving force is transmitted to the hub case 11 via the transmission planetary carrier 30c.

In this state, the driving force from the rear sprocket 9 is expressed as a speed ratio, where a1 is the number of teeth of the first sun gear 30a-1 and d1 is the number of teeth of the outer ring gear 30d for transmission.
d1 / (a1 + d1)
Is transmitted to the hub case 11.

FIGS. 6 and 7 show the arrangement of the rear hub unit at the second gear position (at the second speed). Similar to the first gear stage, the rear sprocket 9 is attached to the drive body 32 of the transmission mechanism unit 30, and the driving force by human power from the pedal 3 is transmitted to the drive body 32.
When the speed change rod 36 is pushed, the pin 35c is also pushed into the hub, and the pin 35c and the clutch switching control member 37 rotate around the axis. At the second gear stage, the first clutch portion 30e-1 of the first one-way clutch for transmission 30e is in a state in which the first clutch pawl portion 30f-1 can be engaged, as in the first speed. In addition, the second clutch portion 30e-2 is released from the restriction at one end by the first one-way clutch switching portion 37a for transmission by the rotational movement of the clutch switching control member 37. It is possible to match.

Also, the second one-way clutch 31 for transmission is in a state in which one end of the second one-way clutch pawl 31f for transmission is restricted by the clutch switching control member 37 and cannot be engaged. At this time, the first sun gear 30a-1 is in a state in which the first clutch pawl 30f-1 can be engaged in one direction around the axis. Since it rotates in the reverse direction, it can idle. Therefore, only the second sun gear 30a-2 is engaged in the driving force direction.

Therefore, the driving force by human power is input to the transmission planetary gear 30b through the driving body 32 and the auxiliary driving body 33, and the second sun gear 30a-2 is engaged in the driving force direction by the second clutch portion 30e-2. Therefore, the driving force is transmitted to the hub case 11 via the transmission planetary carrier 30c.

At this time, the transmission planetary gear 30b has two stages of gear portions (gears) having different numbers of teeth, and the gear portion on the side having the smaller number of teeth of the planetary gear 30b for transmission includes the outer ring gear 30d for transmission, The gear portion having the larger number of teeth meshes with the second sun gear 30a-2.
In this state, the driving force from the rear sprocket 9 is such that the number of teeth of the second sun gear 30a-2 is a2, the number of teeth of the outer ring gear 30d for transmission is d1, and the number of teeth of the planetary gear 30b for transmission is smaller. If the number of teeth of the gear part is b1, and the number of teeth of the gear part on the side with the larger number of teeth is b2, the speed ratio,
(B2 × d1) / [(a2 × b1) + (b2 × d1)]
Is transmitted to the hub case 11.

8 and 9 show the arrangement of the rear hub unit at the third gear position (at the third speed). The rear sprocket 9 is attached to the drive body 32 of the speed change mechanism 30 as in the first and second speed changes, and the driving force generated by human power from the pedal 3 is transmitted to the drive body 32.

The pin 35c is also pushed into the hub when the speed change rod 36 is pushed to the farthest side, and the pin 35c and the clutch switching control member 37 further rotate around the axis. At the third speed change stage, the first clutch portion 30e-1 of the first one-way clutch 30e for transmission is driven in the driving direction of the first sun gear 30a-1 at the first speed by the first clutch pawl portion 30f-1. It can be engaged only with respect to the rotation. Further, the second clutch portion 30e-2 is engaged with the second clutch pawl portion 30f-2 by releasing the restriction at one end by the first one-way clutch switching portion 37a for transmission by the rotational movement of the clutch switching control member 37. It is possible.

Further, the transmission second one-way clutch 31 is configured such that the transmission second one-way clutch pawl 31 f is rotated by the clutch switching control member 37, and the transmission second one-way clutch switching unit 37 b is the shaft of the clutch switching member 39. Release the direction movement constraint. As a result of this release, the clutch switching member 39 is moved to the left in FIG. 8 by the elastic force of the elastic member 35e, so that the restriction at one end of the second one-way clutch pawl 31f for transmission is released, and the second one-way for transmission is released. The clutch 31 can be engaged.

At this time, the first sun gear 30a-1 is in a state where the first clutch pawl portion 30f-1 can be engaged in one direction around the axis. Can rotate idly because it rotates in the reverse direction, and the second sun gear 30a-2 is in a state in which the second clutch pawl 30f-2 can be engaged in one direction around the axis. When this acts, it rotates idly because it rotates in the direction opposite to the engageable direction. Therefore, the outer ring gear 30d for transmission and the planet carrier 30c for transmission cannot be rotated relative to the driving force direction.

Therefore, the driving force is transmitted from the driving body 32 and the outer ring gear 30d for transmission to the planetary carrier 30c for transmission via the second one-way clutch 31 for transmission, and is transmitted to the hub case 11 in a directly connected state. In this highest speed gear stage, since no gear is used for torque transmission, the durability of the hub is remarkably improved.

In addition, when the motor is driven, when the driving force from the driving motor 18 is applied regardless of the gear position, the motor shaft 18a is held integrally or rotatably with the reduction gear sun gear 40a. ing. A two-way clutch 20 is disposed between the outer ring gear for reduction gear 40d and the motor housing 18b. Further, as shown in FIG. 10, the two-way clutch 20 is loaded in a direction in which the roller 23 as an engaging element is engaged with the forward cam surface 21 b on one side in the circumferential direction with respect to the driving force by the driving motor 18. Is given. This addition is given from an elastic member (not shown) via a cage 24. For this reason, the two-way clutch 20 can always transmit power by the driving force of the driving motor 18.

For this reason, the driving force from the driving motor 18 is transmitted to the planetary carrier 30c for transmission which is an output member to the hub case 11 through the planetary gear 40b for reduction gear. At this time, the carrier holding the reduction gear planetary gear 40b is shared with the transmission planetary carrier 30c holding the transmission planetary gear 30b. In other words, the reduction gear planetary gear 40b is held by the transmission planet carrier 30c or a member that rotates integrally with the transmission planet carrier 30c, thereby reducing the size of the apparatus.

Further, the reduction gear planetary gear 40b has two stages of gear portions (gears) having different numbers of teeth, and the gear portion on the side having the smaller number of teeth of the reduction gear planetary gear 40b (the second outer diameter gear portion 40f) is provided. The reduction gear outer ring gear 40d and the gear portion having the larger number of teeth (the first outer diameter gear portion 40e) mesh with the reduction gear sun gear 40a. As described above, the reduction gear planetary gear 40b has two stages, so that a high reduction ratio can be realized.

In this state, the driving force from the drive motor 18 is such that the number of teeth of the reduction gear sun gear 40a is a3, the number of teeth of the reduction gear outer ring gear 40d is d2, and the number of teeth of the reduction gear planetary gear 40b is smaller. When the number of teeth of the gear part is b3 and the number of teeth of the gear part on the side with the larger number of teeth is b4, the speed ratio to the motor rotation speed,
(A3 × b3) / [(a3 × b3) + (b4 × d2)]
Is transmitted to the hub case 11.

Further, when the motor is not driven, for example, when the speed range set to perform the motor assist is exceeded, or when the driving force from the driving motor 18 is not loaded due to a reason such as battery exhaustion, the hub case Torque is transmitted from 11 to the drive motor 18 via the planetary gear 40b for reduction gear. This torque is a torque in the direction opposite to that when the motor is driven. At this time, a rotational load is applied to the cage 24 of the two-way clutch 20 by an elastic member in a direction in which the cage 24 rotates together with the reduction gear outer ring gear 40d. For this reason, the reduction gear outer ring gear 40d rotates in the idling direction with respect to the motor housing 18b, and torque is not transmitted to the motor shaft 18a, that is, the drag torque of the motor can be cut off.

Further, when a reverse input is made from the rear wheel 2 (hub case 11) on a downhill or the like and regenerative charging is performed by the rotational force, the two-way clutch 20 is switched to the two-way by an external input signal through the switching clutch control mechanism unit 25. Resistance is applied to the retainer 24 of the clutch 20, and the retainer 24 and the roller 23 are moved in a direction to engage with the regeneration side cam surface 21 a in a rotation direction different from that during forward movement, thereby switching to an engageable state. As a result, the reverse input from the hub case 11 is input from the transmission planetary carrier 30c and transmitted to the reduction gear sun gear 40a (motor shaft 18a) via the reduction gear mechanism 40, to the outside of the rear hub unit. Rechargeable charging is possible for the provided secondary battery 7.

In this embodiment, as the two-way clutch 20, a roller type as shown in FIG. 10 is shown, but instead of this, for example, as shown in FIG. 11, a clutch provided with a ratchet mechanism may be adopted. it can.

In this case, the first ratchet portion 20a of the two-way clutch 20 is arranged such that the ratchet pawl 23a, which is the engagement element 23, can always be engaged with the driving force of the driving motor 18. Further, the ratchet pawl 23a of the second ratchet portion 20b can be switched between an engageable state and an unengageable state by an external input signal through the switching clutch control mechanism portion 25. By this switching, it is possible to make the state capable of regenerating as described above or the state in which the motor drag torque can be interrupted.

As the two-way clutch 20, as shown in FIG. 24 (a), a sprag is disposed as an engagement element 23 between the inner ring on the motor housing 18b side and the outer ring on the outer ring gear 40d side for the speed reducer. A sprag clutch held by the cage 24 can also be employed.

In this embodiment, the number of stages of the planetary gear 30b for transmission is two, but the number of stages of the planetary gear 30b for transmission can be three or four or more.

Further, in these embodiments, in the first one-way clutch 30e for transmission and the second one-way clutch 31 composed of a ratchet clutch, the engagement of each clutch pawl of the ratchet clutch with the clutch cam surface is rotated. Although the clutch switching control member 37 that moves and the clutch switching member 39 that moves in the axial direction in conjunction with the clutch switching member 39 are switched between the engageable state and the disengageable state, the axle 15 and the transmission are used. Other configurations may be adopted as means for switching the sun gear 30a, the transmission outer ring gear 30d (driving body 32), and the transmission planetary carrier 30c between relative rotation and non-rotation.

In this embodiment, the first one-way clutch for transmission 30e and the second one-way clutch for transmission 31 each employ a ratchet clutch. For example, a sprag clutch as shown in FIG. You may employ | adopt the one-way clutch which consists of other structures, such as a roller clutch as shown in FIG.24 (c).

Still another embodiment of the present invention will be described with reference to FIGS. 13 to 23 and FIGS. 24 and 25. FIG. Since the main configuration of the battery-assisted bicycle is the same as that of the above-described embodiment, the following description will focus on differences from the above-described embodiment.

As shown in FIG. 13, the speed change mechanism unit 30 is constituted by a planetary gear mechanism that can change gears in three stages including direct connection and two-stage reduction. The transmission mechanism 30 includes a transmission sun gear 30a provided on the outer periphery of the axle 15 via a transmission first one-way clutch 30e. In this embodiment, the transmission sun gear 30a includes two sun gears, that is, a first sun gear 30a-1 and a second sun gear 30a-2. The first sun gear 30a-1 and the second sun gear 30a-2 are respectively connected to the outer periphery of the axle 15 via the first clutch portion 30e-1 and the second clutch portion 30e-2 of the first one-way clutch 30e for transmission. It is connected to the.

The transmission mechanism 30 includes a transmission planetary gear 30b having two gear portions respectively engaged with the first sun gear 30a-1 and the second sun gear 30a-2, and the transmission planetary gear 30b as a planet carrier shaft. And a planetary carrier 30c for transmission that is held via 30i. The two gear portions of the planetary gear 30b for transmission are set so that their outer diameters are different from each other and the number of teeth is different.

Furthermore, the speed change mechanism unit 30 includes a drive body 32 that rotates integrally with the rear sprocket 9 and transmits a driving force from the rear sprocket 9. The drive body 32 is provided with a transmission outer ring gear 30d that meshes with a gear portion having a smaller number of teeth of the transmission planetary gear 30b as a member that rotates integrally or integrally. The transmission outer ring gear 30d may be meshed with the gear portion having the larger number of teeth of the transmission planetary gear 30b.

Furthermore, the outer diameter gear part 40g provided on the outer periphery of the planetary carrier 30c for transmission is engaged with the inner diameter gear part 40h provided in the hub case 11.

In this embodiment, the drive body 32 and the transmission outer ring gear 30d are formed as an integral member, but the drive body 32 and the transmission outer ring gear 30d are formed as separate members. The separate drive body 32 and the transmission outer ring gear 30d may be held by a joint that can rotate integrally. At this time, the drive body 32 and the transmission outer ring gear 30d are supported in a floating manner in a radial direction (a state in which the gear 32 is supported with a degree of freedom in radial movement) so that the arrangement of the gears is at a position where a load balance can be obtained. Misalignment makes it easy to balance the entire load.

Further, if the driving body 32 and the transmission outer ring gear 30d are formed as separate members, the driving body 32 that does not require relatively strong strength is made of an aluminum material and a hardened layer by heat treatment. It is possible to select different materials such as 30d steel, which realizes weight reduction.

Further, it is attached between the drive body 32 and the shift control mechanism 55 provided on the outer periphery of the axle 15, between the drive body 32 and the hub case 11, and on the ring member 17 that closes the end surface of the hub case 11 and the end surface of the drive motor 18. Between the lid 16,

bearings

12, 13, and 14 are provided, respectively. The

bearings

12, 13, and 14 support the respective members so as to be relatively rotatable.

A bearing 26 is also provided between the motor housing 18b that holds the driving motor 18 and the speed reducer carrier 40c. The motor housing 18b and the speed reducer carrier 40c are supported by the bearing 26 so as to be relatively rotatable. In the bearing portion 26, a plurality of rollers 26a held by a cage 26b are arranged along the circumferential direction.

By operating the transmission control mechanism unit 55, the first clutch unit 30e-1, the second clutch unit 30e-2, and the second one-way clutch 31 for transmission can be switched. As a result of the switching, the first sun gear 30a-1 and the second sun gear 30a-2 rotate in one direction around the axis and the drive body 32 rotates relative to the axle 15 and the planetary carrier 30c for transmission. It is switched to an impossible state.

FIGS. 20 and 21 show the state of each clutch at the third gear position (at the third speed). As shown in FIGS. 21 (a), 21 (b) and 21 (c), at the third speed, all the clutches are engaged with the clutch cam surface.

In this embodiment, a ratchet clutch that is relatively inexpensive as compared with other clutch mechanisms is used for the first clutch portion 30e-1, the second clutch portion 30e-2, and the second one-way clutch 31 for transmission. Adopted. However, the types of these clutches are not limited, and other clutches such as a roller clutch or a sprag clutch having a high backlash effect (rattle prevention effect) may be used as in the above-described embodiment.

As shown in FIG. 21 (a), the first clutch portion 30e-1 of the transmission first one-way clutch 30e includes a transmission first one-way clutch pawl 30f (first clutch) that can swing on the outer periphery of the axle 15. Claw portion 30f-1). The first clutch pawl portion 30f-1 is a first one-way clutch cam surface 30g for transmission (first cam surface portion 30g-1) provided on the inner peripheral surface of the first sun gear 30a-1 by an elastic member (not shown). It is urged in the direction of meshing. Since the first clutch pawl portion 30f-1 meshes with the first cam surface 30g-1, the first sun gear 30a-1 can be made non-rotatable only with respect to the axle 15 in one direction around the axis. Note that the first sun gear 30a-1 is always rotatable about the axle 15 (idling state) with respect to rotation in the other direction around the axis.

Similarly, the second clutch portion 30e-2 of the transmission first one-way clutch 30e has a transmission first one-way clutch pawl 30f (second clutch pawl portion 30f-2) swingable on the outer periphery of the axle 15. Prepare. The second clutch pawl portion 30f-2 is a first one-way clutch cam surface 30g for transmission (second cam surface 30g-2) provided on the inner peripheral surface of the second sun gear 30a-1 by an elastic member (not shown). It is urged in the direction of meshing. Since the second clutch pawl portion 30f-2 meshes with the second cam surface 30g-2, the second sun gear 30a-2 can be made non-rotatable only with respect to the axle 15 in one direction around the axis. Note that the second sun gear 30a-2 is always rotatable about the axle 15 (idling state) with respect to rotation in the other direction around the axis.

The second clutch pawl portion 30f-2 of the second clutch portion 30e-2 can be switched ON / OFF by the rotation operation of the clutch switching member 37 provided in the transmission control mechanism portion 35. That is, if the switching state is turned OFF, the second clutch pawl portion 30f-2 of the second clutch portion 30e-2 is in a state where it cannot be engaged with the second cam surface 30g-2 (a state where it cannot be engaged). The second sun gear 30 a-2 can be rotated with respect to the rotation about the axis with respect to the axle 15.

The second one-way clutch portion 31 for transmission is provided with a second one-way clutch pawl 31f for transmission so as to be swingable around the planet carrier shaft 30i provided on the planet carrier 30c for transmission. The transmission second one-way clutch pawl 31f is arranged on the transmission planet carrier 30c toward the outer peripheral side. The transmission second one-way clutch pawl 31f is urged by an elastic member (not shown) in a direction to mesh with a transmission second one-way clutch cam surface 31g provided on the inner peripheral surface of the drive body 32.
The second one-way clutch cam surface 31g for transmission is desirably provided on the inner peripheral surface of the outer ring gear 30d for transmission.

The second one-way clutch pawl 31f for transmission meshes with the second one-way clutch cam surface 31g for transmission, so that the planetary carrier 30c for transmission has one axis around the outer ring gear 30d for transmission and the drive body 32. It can be made non-rotatable only in the direction of rotation. Note that the planetary carrier 30c for transmission is always rotatable to the outer ring gear 30d for transmission and the drive body 32 (idling state) with respect to rotation in the other direction around the axis.

In this embodiment, the transmission second one-way clutch pawl 31f is swingably attached to the planet carrier shaft 30i that supports the transmission planetary gear 30b. However, this is used for the transmission planetary gear 30b and the transmission. It is also possible to attach to another shaft provided on the planet carrier 30c.

As described above, when another shaft is used to support the transmission second one-way clutch pawl 31f, the transmission second one-way clutch pawl 31f includes the number of transmission planetary gears 30b (3 in this embodiment). For example, it is possible to set the number to four or more. In any case, the number of the second one-way clutch pawls 31f for transmission can be one or two, regardless of which shaft is supported.

FIG. 15 shows a detailed view of the shift control mechanism 55. The shift control mechanism section 55 includes a shift operation section 56 that includes a shift switching input member 56a, a shift switching intermediate member 56b, a first clutch switching member 57, a second clutch switching member 59, a clutch switching control member 56c, and the like.

The shift switching input member 56a is rotated by a signal input manually or electrically from a hand switch or the like. A shift switching intermediate member 56b connected to the shift switching input member 56a inside the rear hub 10 holds a first clutch switching member 57 and a second clutch switching member 59. The clutch switching control member 56c is loaded in the specific rotation direction by the elastic force of the

elastic members

56g and 56h.

When the clutch switching control member 56c rotates around the shaft against the elastic force, the sleeve-shaped first clutch having a C-shaped cross section provided in the second clutch portion 30e-2 of the first one-way clutch 30e for transmission. The switching member 57 (see FIG. 14B) also rotates about the axis in the same direction.

Further, the second clutch switching member 59 is movable in the axial direction by the action of the tapered surface 56d provided on the clutch switching control member 56c. At this time, the second clutch switching member 59 is guided in its axial movement by the guide portion 59b located on the inner diameter side thereof being fitted into the guide hole 56f of the guide member 56e that is rotationally fixed to the axle 15.

When the first clutch switching member 57 is disengaged from the position of the second clutch pawl portion 30f-2 due to the rotation of the first clutch switching member 57 around the axis, the second clutch pawl portion 31f-2 rises in the engaging direction, The transmission sun gear 30a and the axle 15 can be relatively rotated only in one direction around the axis. Further, when the first clutch switching member 57 enters the position of the second clutch pawl portion 30f-2, the second clutch pawl portion 30f-2 is prevented from rising in the engaging direction, and the transmission sun gear 30a. And the axle 15 can rotate relative to each other around the axis. In this way, the transmission sun gear 30a can be switched to be rotatable relative to the axle 15 in one direction around the axis or to be relatively non-rotatable.

When the second clutch switching member 59 moves in the axial direction and the action portion 59a located on the outer diameter side thereof is disengaged from the position of the second one-way clutch pawl 31f for transmission, the second one-way clutch pawl for transmission 31f rises in the engaging direction, and the outer ring gear 30d for transmission and the planetary gear 30b for transmission are in a state of being relatively rotatable in one direction around the axis. Further, when the action portion 39a enters the position of the second one-way clutch pawl 31f for transmission, the rising of the second one-way clutch pawl 31f for transmission in the engaging direction is prevented, and the outer ring gear 30d for transmission The transmission planetary gear 30b is in a state of being relatively rotatable around the axis. In this way, the transmission planetary gear 30b can be switched to be rotatable relative to the outer ring gear 30d and the driving body 32 in one direction around the axis, or to be relatively non-rotatable.

The portion where the action portion 59a contacts the second one-way clutch pawl 31f for transmission is a tapered surface 59c that gradually approaches the inner diameter side in one axial direction, so the second one-way clutch for transmission From the state where the claw 31f is engaged with and engaged with the transmission second clutch cam surface 31g, the force for releasing the engagement can be increased.

Further, since the second clutch switching member 59 is provided with an elastic member 58a between the second clutch switching member 59 and the holding member 58 provided on the outer periphery of the axle 15, the second clutch switching member 59 is moved in the axial direction by the action of the tapered surface 56d of the clutch switching control member 56c. When the pressing is released, the action portion 59a is automatically detached from the position of the second one-way clutch pawl 31f for transmission by the elastic force.

Next, the speed reduction mechanism unit 40 will be described. The reduction mechanism unit 40 is configured by a planetary gear mechanism, and a reduction gear sun gear 40a provided on the outer periphery of the motor shaft 18a of the drive motor 18, and a reduction gear planetary gear that meshes with the reduction gear sun gear 40a. 40b, and a reduction gear planet carrier 40c that holds the reduction gear planet gear 40b via the planet carrier shaft 40i.

The motor shaft 18a and the reduction gear sun gear 40a are held by the same member or a member that rotates integrally, and the reduction gear planetary gear 40b is provided with a two-stage gear portion having a different number of teeth to achieve high reduction. Realize the ratio.

Further, in the speed reduction mechanism section 40, the first outer diameter gear section 40e provided on the reduction gear planetary gear 40b meshes with the reduction gear sun gear 40a, and the first outer diameter gear section 40e provided on the reduction gear planetary gear 40b. A second outer gear portion 40f having a smaller diameter with a smaller number of teeth meshes with the outer ring gear (inner gear portion) 40d provided integrally with the planetary carrier 30c for transmission.

Further, the outer ring gear 40d for the speed reducer, that is, the outer gear portion 40g provided on the planetary carrier 30c for transmission, meshes with the inner gear portion 40h provided on the hub case 11.
For this reason, the planetary carrier 30 c for transmission is a common output member to the hub case 11 for both the driving force by human power and the driving force by the driving motor 18.

That is, the transmission mechanism 30 uses the rear sprocket 9 and the driving body 32 as input members for driving force by human power, and the planetary carrier for transmission 30c as an output member to the hub case 11.

The reduction mechanism 40 uses the reduction gear sun gear 40 a as an input member for driving force from the drive motor 18 and the transmission planetary carrier 30 c as an output member to the hub case 11.

As described above, the reduction gear outer ring gear 40d is formed of the same member as the transmission planetary carrier 30c, which is a carrier member of the transmission mechanism 30, or a member that rotates integrally therewith. It is possible to shorten the assembly, and the assembly can be simplified as compared with the case where the hub cases 11 are engaged with each other independently.

Further, the planetary gear mechanism of the reduction mechanism unit 40 is configured such that the planetary carrier 40c for reduction gears can be rotationally fixed. Therefore, the reduction gear sun gear 40 a that is an input member is decelerated and output to the reduction gear outer ring gear 40 d, and the driving force is transmitted to the rear wheel 2 via the hub case 11.

The reduction planetary carrier 40c is rotationally supported by the bearing 26, and a two-way clutch 20 (switching clutch 20) provided between the motor housing 18b and the reduction planetary carrier 40c arranged in parallel with the bearing 26. The rotation fixed state can be set by engagement. The motor housing 18b is held on the bicycle frame or axle 15 so as not to rotate relative thereto.

The two-way clutch 20 is driven by the elastic member 20c with respect to the planetary carrier 40c for the speed reducer in the direction in which the two-way clutch 20 is always engaged when the driving force from the driving motor 18 acts and the battery-assisted bicycle moves forward. A load is applied to 20 cages 24.

Further, when not driving (when the battery-assisted bicycle moves forward only by driving force by human power), the planetary carrier 40c for reduction gear is idle with respect to the motor housing 18b, that is, the driving force from the driving motor 18 is low. It rotates in the opposite direction to the case where it acts. For this reason, torque is not transmitted to the motor shaft 18a, that is, the drag torque of the drive motor 18 can be cut off.

Further, when the battery-assisted bicycle travels by inertia and is reversely input from the rear wheel 2 and the hub case 11 to perform regenerative charging by the rotational force, the two-way clutch 20 is input from the switching clutch control mechanism unit 25 (external input signal). ) To enable engagement. As a result, the reverse input from the hub case 11 is transmitted to the drive motor 18 via the speed reduction mechanism 40 and can be regenerated.

These switching clutch control mechanisms 25 are operated manually or electrically, and can be regenerated by interlocking with a brake, for example.

In this embodiment, as shown in FIG. 13, as the switching clutch control mechanism unit 25, an advance / retreat operation of a wire or the like interlocking with a brake operation is input to the input mechanism 25a, and the input mechanism 25a is actuated by the input by the input member 25b. Is pushed against the urging force of the elastic member 25c toward the outer diameter side, so that the cage 24 or the elastic member 20c is loaded with an external force in the rotation direction or resistance to the rotation. When the load of the external force or resistance is equal to or greater than the urging force of the elastic member 20c, the cage 24 is delayed from the rotation of the planetary carrier 30c for reduction gear, and the two-way clutch 20 can be switched.

In addition, by setting the same number of

planetary gears

30b and 40b by three.

The operation of each member will be described with reference to FIG.
The arrangement of the rear hub unit at the first shift (at the first speed) is shown in FIGS. In this embodiment, the rear sprocket 9 is attached to the drive body 32 of the speed change mechanism unit 30, and the driving force by human power from the pedal 3 is transmitted to the drive body 32.

In the first gear stage, the first clutch portion 30e-1 of the first one-way clutch for transmission 30e is in a state that can be engaged with the driving force by the first clutch pawl portion 30f-1, One end of the second clutch pawl 30f-2 is restrained by the first clutch switching member 37 so that the two clutch portion 30e-2 cannot be engaged.

Also, the second one-way clutch 31 for transmission is in a state where one end of the second one-way clutch pawl 31f for transmission is restricted by the second clutch switching member 39 and cannot be engaged.

For this reason, the driving force by human power is input to the transmission planetary gear 30b from the transmission outer ring gear 30d. At this time, the first sun gear 30a-1 is moved in the driving force direction by the first clutch portion 30e-1. Because of the engagement, the driving force is transmitted to the hub case 11 via the transmission planetary carrier 30c.

FIG. 18 and FIG. 19 show the arrangement of the rear hub unit at the second gear stage (at the second speed). Similar to the first gear stage, the rear sprocket 9 is attached to the drive body 32 of the transmission mechanism unit 30, and the driving force by human power from the pedal 3 is transmitted to the drive body 32.

In the second speed step, the first clutch portion 30e-1 of the first one-way clutch for transmission 30e is in a state in which the first clutch pawl portion 30f-1 can be engaged, and the second clutch portion 30e- 2, the second clutch pawl portion 30f-2 is released from the restraint at one end thereof by the rotational movement of the clutch switching member 57 and is in an engageable state.

Also, the second one-way clutch 31 for transmission is in a state where one end of the second one-way clutch pawl 31f for transmission is restricted by the second clutch switching member 59 and cannot be engaged. At this time, the first sun gear 30a-1 is in a state in which the first clutch pawl 30f-1 can be engaged in one direction around the axis. Since it rotates in the reverse direction, it can idle. Therefore, only the second sun gear 30a-2 is engaged in the driving force direction.

For this reason, the driving force by human power is input to the transmission planetary gear 30b from the transmission outer ring gear 30d, and the second sun gear 30a-2 is engaged in the driving force direction by the second clutch portion 30e-2. Therefore, the driving force is transmitted to the hub case 11 via the transmission planetary carrier 30c.

Fig. 20 and Fig. 21 show the arrangement of the rear hub unit at the third gear position (at the third speed). The rear sprocket 9 is attached to the drive body 32 of the speed change mechanism 30 as in the first and second speed changes, and the driving force generated by human power from the pedal 3 is transmitted to the drive body 32.

At the third gear position, the first clutch portion 30e-1 of the first one-way clutch for transmission 30e is in a state in which the first clutch pawl portion 30f-1 can be engaged, and the second clutch portion 30e- 2, the second clutch pawl portion 30f-2 is released from the restraint at one end thereof by the rotational movement of the clutch switching member 57 and is in an engageable state.

Also, the second one-way clutch 31 for transmission is in a state where the second one-way clutch pawl 31f for transmission is released from the restraint at one end by the axial movement of the second clutch switching member 59 and can be engaged. .

Therefore, the driving force is transmitted from the outer ring gear 30d for transmission to the planetary carrier 30c for transmission via the second one-way clutch 31 for transmission, and is transmitted to the hub case 11 in a directly connected state. In this highest speed gear stage, since no gear is used for torque transmission, the durability of the hub is remarkably improved.

In addition, regardless of the gear position, when the driving force from the driving motor 18 is applied, the motor shaft 18a is held integrally with the reduction gear sun gear 40a or rotatably. Further, a two-way clutch 20 is disposed between the planetary carrier 40c for speed reducer and the motor housing 18b, and as shown in FIG. The cage 24 is loaded by the elastic force of the elastic member 20c in a direction to engage with the forward cam surface 21b on one circumferential side. For this reason, the two-way clutch 20 can always transmit power by the driving force of the driving motor 18.

The driving force from the drive motor 18 is transmitted to the reduction gear outer ring gear 40d via the reduction gear planetary gear 40b. At this time, the outer ring gear 40d for reduction gears is held so as to be integrally rotatable with the speed change planetary carrier 30c or integrally rotatable.

Further, the reduction gear planetary gear 40b has two stages of gear portions (gears) having different numbers of teeth, and the gear portion on the side having the smaller number of teeth of the reduction gear planetary gear 40b (the second outer diameter gear portion 40f) is provided. The reduction gear outer ring gear 40d and the gear portion having the larger number of teeth (the first outer diameter gear portion 40e) mesh with the reduction gear sun gear 40a. The reduction gear outer ring gear 40 d, that is, the outer gear portion 40 g provided on the transmission planetary carrier 30 c meshes with the inner gear portion 40 h provided on the hub case 11. As described above, the reduction gear planetary gear 40b has two stages, so that a high reduction ratio can be realized.

In this state, the driving force from the drive motor 18 is such that the number of teeth of the reduction gear sun gear 40a is a3, the number of teeth of the reduction gear outer ring gear 40d is d2, and the number of teeth of the reduction gear planetary gear 40b is smaller. When the number of teeth of the gear part is b3 and the number of teeth of the gear part on the side with the larger number of teeth is b4, the speed ratio,
(A3 × b3) / (b4 × d2)
Is transmitted to the hub case 11.

Further, when the driving force from the driving motor 18 is not loaded, torque is transmitted from the hub case 11 via the outer ring gear 40d for reduction gears, and the planetary carrier 40c for reduction gears rotates in the opposite direction to that when the motor driving is performed. To do. For this reason, the planetary carrier for speed reducer 40c of the speed reduction mechanism section 40 and the motor housing 18b cannot be engaged and idle.
Therefore, the motor shaft 18a does not rotate, does not generate a drag torque of the motor, and can travel comfortably.

When regenerative charging is performed, the switching clutch control mechanism unit 25 is operated to provide resistance to the retainer 24 of the two-way clutch 20 and to engage with the regenerative cam surface 21a in a rotational direction different from the forward direction. The retainer 24 and the roller 23 are moved, and the planetary carrier 40c for the speed reducer of the speed reduction mechanism 40 and the motor housing 18b can be engaged.
As a result, the driving force from the hub case 11 is transmitted to the motor shaft 18a via the speed reduction mechanism 40, and the secondary battery 7 provided outside the rear motor unit can be recharged.

Further, in this embodiment, as the two-way clutch 20, a roller type as shown in FIG. 22 is shown, but instead of this, for example, as shown in FIG. 23, a clutch provided with a ratchet mechanism may be adopted. it can.

In this case, the first ratchet portion 20a of the two-way clutch 20 is arranged such that the ratchet pawl 23a, which is the engagement element 23, can always be engaged with the driving force by the driving motor 18, and the second ratchet By switching the ratchet pawl 23a of the part 20b between the state in which the first clutch switching member 37 can be engaged and the state in which the ratchet claw 23a cannot be engaged, the above-described regenerative state or the state in which the motor drag torque can be interrupted is achieved. It becomes possible.
As the two-way clutch 20, as shown in FIG. 24A, a sprag is disposed as an engaging member 23 between the inner ring on the motor housing 18 b side and the planetary carrier 40 c for reduction gear, and the sprag is placed in the cage 24. It is also possible to employ a sprag clutch held in the above.

Further, in these embodiments, in the first one-way clutch 30e for transmission and the second one-way clutch 31 composed of a ratchet clutch, the engagement of each clutch pawl of the ratchet clutch with the clutch cam surface is rotated. The first clutch switching member 37 that moves and the second clutch switching member 59 that moves in the axial direction employ a method of switching between an engageable state and a disengageable state, but the axle 15 and the transmission sun gear. Other means may be adopted as means for switching the outer ring gear 30d for transmission 30d (driving body 32) and the planetary carrier 30c for transmission between relative rotation and non-rotation.

In this embodiment, the first one-way clutch 30e-1 for transmission and the second one-way clutch 31 for transmission each employ a ratchet clutch. However, as in the previous embodiment, a roller clutch, a sprag clutch For example, a one-way clutch having another configuration may be adopted.

1 Electric assist bicycle 2 Drive wheel (rear wheel)
3 Pedal 4 Power transmission element (chain)
5 Handle 6 Frame 7 Secondary battery 8 Hub flange 9 Input means (rear sprocket)
10 Hub (rear hub)
11

Hub case

12, 13, 14, 18c, 26 Bearing 15 Axle 15a Shaft hole 16 Lid 17 Ring member 18 Driving motor 18a Motor shaft 18b Motor housing 19 Holding member 20 Switching clutch (two-way clutch)
20a First ratchet portion 20b Second ratchet portion 21 Cam surface 21a Regeneration side cam surface 21b Advance side cam surface 22 Outer diameter surface 23 Engagement element 23a Regeneration ratchet pawl 23b Advance side ratchet pawl 24 Cage 25 Switching clutch control mechanism

25a Input mechanism

25b Action member

25c Elastic member 25d Electromagnetic clutch (solenoid valve)
30 Transmission mechanism 30a Transmission sun gear 30a-1 First sun gear 30a-2 Second sun gear 30b Transmission planetary gear 30c Transmission planetary carrier 30d Transmission outer ring gear 30e Transmission first one-way clutch 30e-1 first clutch portion 30e-2 second clutch portion 30f first one-way clutch pawl 30f-1 for transmission first clutch pawl portion 30f-2 second clutch pawl portion 30g first one-way clutch cam surface 30g for transmission -1 first cam surface portion 30g-2 second cam surface portion 30i planet carrier shaft 31 second one-way clutch 31f for transmission second one-way clutch pawl 31g for transmission second one-way clutch cam surface 32 for transmission driver 32a shaft 33 Auxiliary drive 34 Transmission clutch holding section 35 Transmission control mechanism section 35b Transmission guide groove 35c Pin 36 Speed control unit (speed change rod)
36a End 37 First clutch switching control member 37a Transmission first one-way clutch switching unit 37b Transmission second one-way clutch switching unit 38 Clutch switching guide member 39 Clutch switching member 40 Deceleration mechanism unit 40a Reduction gear sun gear 40b Planetary gear for reducer
40c planetary carrier for reduction gear 40d outer ring gear for reduction gear 40e first outer diameter gear portion 40f second outer diameter gear portion 40g outer diameter gear portion 40h inner diameter gear portion 40i planetary carrier shaft 55 transmission control mechanism portion 56 transmission operation portion 56a speed change Switching input member 56b Shifting switching intermediate member 56c Clutch switching control member 56d Tapered surface 56e Guide member

56f Guide holes

56g, 56h Elastic member 57 First clutch switching member 58 Holding member 58a Elastic member 59 Second clutch switching member

59a Acting portion

59b Guide Part 59c taper surface

Claims

A bicycle hub unit in which a transmission mechanism (30), a speed reduction mechanism (40), and a drive motor (18) are arranged in parallel in the axial direction of the axle (15) inside the hub (10).
The speed change mechanism portion (30) has a function of transmitting a driving force generated by human power input to the input means (9) to the hub case (11), and the speed reduction mechanism portion (40) is provided with the drive motor (18). ) Is transmitted to the hub case (11), and the speed change mechanism (30) is constituted by a planetary gear mechanism having two or more speeds, and at least one speed change. A transmission sun gear (30a), a transmission planetary gear (30b) meshing with the transmission sun gear (30a), and a transmission planetary carrier (30c) holding the transmission planetary gear (30b) For changing the speed by switching the at least one sun gear for transmission (30a) to be rotatable or non-rotatable around the axle (15) with respect to the driving force from the input means (9). control The speed reduction mechanism (40) includes a planetary gear mechanism, and the speed reduction mechanism (40) is a planetary gear mechanism that rotates integrally with the motor shaft (18a) of the drive motor (18). 40a) and a reduction gear planetary gear (40b) meshing with the reduction gear sun gear (40a), and the reduction gear outer ring gear (40d) meshing with the reduction gear planetary gear (40b) and the driving gear A switching clutch (20) that can be switched relative to or not relative to the motor housing (18b) that holds the motor (18) is provided, and the output of the transmission mechanism (30) to the hub case (11) The planetary gear for reduction gear (40b) is held by the planetary carrier for transmission (30c), which is a member, so that the planetary gear for transmission (30c) can be connected to the center of the reduction mechanism section (40). A bicycle hub unit, characterized in that the output member to the case (11).
The bicycle hub unit according to claim 1, wherein the speed change mechanism portion (30) is a speed reduction type including a direct connection state from the input means (9) to the hub case (11).
The bicycle hub according to claim 1, wherein the speed change mechanism portion (30) is a speed reduction type including a direct connection state from the input means (9) to the hub case (11) and a speed reduction state of two or more stages. unit.
The bicycle hub unit according to any one of claims 1 to 3, wherein the axle (15) is a single member fixed to both ends of a bicycle frame (6).
The bicycle hub unit according to any one of claims 1 to 4, wherein the switching clutch (20) is a two-way clutch.
The bicycle hub unit according to claim 5, wherein the switching clutch (20) is a roller clutch or a sprag clutch.
The switching clutch (20) is always involved in the rotation of the reduction gear outer ring gear (40d) with respect to the motor housing (18b) when the bicycle moves forward by the input of driving force from the driving motor (18). The bicycle according to claim 5 or 6, wherein the bicycle can be switched to an engageable state and an unengageable state by an input transmitted from the outside, in a rotation in the opposite direction. Hub unit.
The switching clutch (20) is a clutch provided with a ratchet mechanism, and the ratchet mechanism engages only in one direction around the axis of the outer ring gear (40d) for the speed reducer with respect to the motor housing (18b). 8. The ratchet portion (20a) and a second ratchet portion (20b) that engages only in rotation in a direction opposite to the engagement direction of the first ratchet portion (20a). The bicycle hub unit described.
The first ratchet portion (20a) is always in rotation with respect to the motor housing (18b) of the outer ring gear (40d) for the speed reducer when the bicycle moves forward by the input of driving force from the driving motor (18). The second ratchet portion (20b) is in an engageable state, and when the driving force is not input from the drive motor (18), the second ratchet portion (20b) can be engaged and input by an input transmitted from the outside. The bicycle hub unit according to claim 8, wherein the bicycle hub unit can be switched to an impossible state.
The transmission mechanism (30) includes a transmission outer ring gear (30d) that rotates integrally with a driving body (32) that transmits a driving force from the input means (9), and the transmission planetary gear (30b). The transmission planetary carrier (30c) is joined to the inner diameter of the hub case (11) so that torque can be transmitted, and the driving force from the input means (9) is the driving body (32). The transmission planetary gear (30b) and the transmission planetary carrier (30c) are transmitted to the hub case (11) at a constant speed or less from the transmission planetary gear (30b). The bicycle hub unit described.
In the speed reduction mechanism (40), a first outer gear (40e) provided on the planetary gear (40b) for the speed reducer meshes with the sun gear (40a) for the speed reducer, and the planetary gear for the speed reducer ( 40b), a second outer gear portion (40f) having a smaller number of teeth than the first outer gear portion (40e) meshes with the outer ring gear (40d) for the reduction gear. Item 11. The bicycle hub unit according to any one of Items 1 to 10.
The transmission control mechanism (35) includes a transmission first one-way clutch (30e), which is configured to prevent the at least one transmission sun gear (30a) from rotating in one direction around the axle (15). The bicycle hub unit according to any one of claims 1 to 11, wherein the bicycle hub unit can be switched so as to be relatively rotatable or non-rotatable in a direction.
In the bicycle hub unit in which the transmission mechanism (30), the speed reduction mechanism (40), and the drive motor (18) are arranged in parallel in the axial direction of the axle (15) inside the hub (10),
The speed change mechanism portion (30) has a function of transmitting a driving force generated by human power input to the input means (9) to the hub case (11), and the speed reduction mechanism portion (40) is provided with the drive motor (18). ) Is transmitted to the hub case (11), and the speed change mechanism (30) is constituted by a planetary gear mechanism having two or more speeds, and at least one speed change. A transmission sun gear (30a), a transmission planetary gear (30b) meshing with the transmission sun gear (30a), and a transmission planetary carrier (30c) holding the transmission planetary gear (30b) For changing the speed of the at least one transmission sun gear (30a) to be rotatable or non-rotatable around the axle (15) with respect to the driving force from the input means (9). Controller The speed reduction mechanism (40) is configured by a planetary gear mechanism and meshes with at least one speed reducer sun gear (40a) and the speed reducer sun gear (40a). A planetary gear for reduction gear (40b), and the planetary gear for reduction gear (40b) is provided on the planetary carrier for transmission (30c) or a member that rotates integrally with the planetary carrier for transmission (30c). A reduction gear planet carrier (40c) that holds the reduction gear sun gear (40a) and a motor housing (18b) that holds the drive motor (18). A rotating hub unit comprising a switching clutch (20) capable of switching between a member fixed to the motor housing (18b) so as to be relatively rotatable or not rotatable. .
The transmission control mechanism (55) includes a transmission first one-way clutch (30e), which is configured to make the at least one transmission sun gear (30a) non-rotatable in one direction around the axle (15). The bicycle hub unit according to claim 13, wherein the hub unit can be switched so as to be relatively rotatable or not rotatable relative to the direction.
The bicycle hub unit according to claim 13 or 14, wherein the switching clutch (20) is a two-way clutch.
The bicycle hub unit according to claim 15, wherein the switching clutch (20) is a roller clutch or a sprag clutch.
The switching clutch (20) is always involved in the rotation of the reduction gear planet carrier (40c) with respect to the motor housing (18b) when the bicycle moves forward by the input of driving force from the driving motor (18). 17. The switchable state can be switched between an engageable state and a disengageable state by an input transmitted from the outside in the opposite direction of rotation. Bicycle hub unit described in 1.
The switching clutch (20) is a clutch provided with a ratchet mechanism, and the ratchet mechanism engages only in one direction around the axis of the planetary carrier for speed reducer (40c) with respect to the motor housing (18b). The ratchet part (20a) and the second ratchet part (20b) that engages only in rotation in a direction opposite to the engagement direction of the first ratchet part (20a). 14. The bicycle hub unit according to 14.
The first ratchet portion (20a) is always in rotation with respect to the motor housing (18b) of the planetary carrier for speed reducer (40c) when the bicycle moves forward by input of driving force from the driving motor (18). The second ratchet portion (20b) is in an engageable state, and when the driving force is not input from the drive motor (18), the second ratchet portion (20b) can be engaged and input by an input transmitted from the outside. 19. The bicycle hub unit according to claim 18, wherein the bicycle hub unit can be switched to an impossible state.
The transmission mechanism (30) includes a transmission outer ring gear (30d) that rotates integrally with a driving body (32) that transmits a driving force from the input means (9), and the transmission planetary gear (30b). The outer diameter gear portion (40g) provided on the outer periphery of the transmission planet carrier (30c) is engaged with the inner diameter gear portion (40h) provided in the hub case (11), and the input means (9) Is transmitted from the drive body (32) to the hub case (11) at a constant speed or less through the transmission planetary gear (30b) and the transmission planetary carrier (30c). The bicycle hub unit according to any one of claims 13 to 19.
In the speed reduction mechanism (40), a first outer gear (40e) provided on the planetary gear (40b) for the speed reducer meshes with the sun gear (40a) for the speed reducer, and the planetary gear for the speed reducer ( 40b) has a second outer diameter gear portion (40f) having a smaller number of teeth than the first outer diameter gear portion (40e) in an inner diameter gear portion (40h) provided on the planetary carrier for transmission (30c). The reduction mechanism (40) is engaged with the reduction gear sun gear (40a) as a driving force input member from the drive motor (18), and the transmission planet carrier (30c) is used as the transmission gear carrier (30c). 21. The bicycle hub unit according to claim 13, wherein the bicycle hub unit is an output member to the hub case.
20. The bicycle hub unit according to claim 7, 9, 17 or 19, wherein the external input is transmitted by a switching clutch control mechanism section (25) that operates in conjunction with a brake operation.
The bicycle hub unit according to any one of claims 1 to 22, wherein the motor housing (18b) is held so as not to rotate relative to a bicycle frame or an axle (15).
The input means (9) is provided on one end side of the axle (15) and the drive motor (18) is provided on the other end side of the axle (15), and the transmission mechanism (30) and the speed reduction mechanism (40) are provided. 24. The bicycle hub unit according to any one of claims 1 to 23, wherein the hub unit is provided between the input means (9) and the drive motor (18).
The drive body (32) and the transmission outer ring gear (30d) are separate members, and the drive body (32) and the transmission outer ring gear (30d), which are separate members, can be integrally rotated. The bicycle hub unit according to any one of claims 1 to 24, wherein the hub unit is for a bicycle.
The bicycle hub unit according to claim 25, wherein the drive body (32) and the transmission outer ring gear (30d) are held so as to be relatively movable in a radial direction.
27. The bicycle hub unit according to claim 1, wherein the number of planetary gears for transmission (30b) is the same as the number of planetary gears for reduction gears (40b). .
The bicycle hub unit according to any one of claims 1 to 27, wherein the number of planetary gears (30b) for transmission is three.
An electrically assisted bicycle and an electric motorcycle using the bicycle hub unit according to any one of claims 1 to 28.