JP2012121407A - Power-assisted bicycle and motorcycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To make a device compact by arranging a reduction gear, an electric motor and a transmission mechanism in parallel along the axle.SOLUTION: Inside a rear hub 1 of a power-assisted bicycle or motorcycle, a transmission mechanism 11, a speed reducer 10 and a driving motor 8 are arranged in parallel in the axial direction of an axle 14. The transmission mechanism 11 includes a sun gear 11a for transmission, a planetary gear 11b for transmission and a planetary carrier 11c for transmission to transmit a leg power to a driving wheel. The speed reducer 10 includes a sun gear 10a for transmission and a planetary gear 10b for transmission to transmit a driving force from a motor output shaft 8a of the driving motor 8 to a driving wheel. The planetary gear 10b for transmission is retained on the planetary carrier 11c for transmission. A shift control mechanism 15 implements shift speed change so as to change a sun gear 11a for transmission to be rotatable or non-rotatable around the axle 14 through a clutch member 16a provided between the sun gear 11a for transmission and the axle 14. Both ends of the axle 14 in the axial direction are supported by a frame 6.

Description

  The present invention relates to a battery-assisted bicycle and an electric motorcycle in which an auxiliary force is applied to a human-powered drive system by an electric motor.

  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 drive wheel axle, or both, and the speed is changed by moving the chain between the sprockets by a derailleur ( There is a system (internal transmission) that shifts gears by changing gears provided inside the hub of the drive wheel.

  The exterior transmission has a simple structure and is lightweight, but it causes wear of the sprocket and the chain, and also causes 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 some electrically assisted bicycles and electric motorcycles that add an auxiliary force to the human power drive system by an electric motor, a motor, a speed reducer, and a speed change mechanism are provided in the hub of the drive wheel of the bicycle.
In addition, although the name of a motor-assisted bicycle and a motor-driven motorcycle is distinguished by law according to requirements such as an assist ratio, the following will be collectively referred to as a motor-assisted bicycle.

  A so-called hub motor type battery-assisted bicycle provided with a driving motor in the hub can use either the exterior transmission or the internal transmission when this is combined with a transmission.

  However, when an exterior transmission is used, the structure of the hub is mainly composed of a motor and a speed reducer, so that the structure is simple. However, there is a problem in maintenance due to the exterior transmission as described above. On the other hand, in the case of using an internal transmission, the structure of the hub is composed of a motor, a speed reducer, and a transmission mechanism, so the structure of the hub itself is complicated, but there are advantages due to the internal transmission as described above. 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 mechanism even in a hub motor type battery-assisted bicycle.

  As a structure of a battery-assisted bicycle provided with this type of internal transmission mechanism, for example, there are those described in Patent Documents 1 and 2.

  In these structures, an electric motor (drive motor), a speed reduction mechanism, and a speed change mechanism are arranged in the hub. As a drive mechanism using an electric motor, a driving electric motor and a power system speed reducing mechanism for reducing the rotational speed of the electric 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 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 electric 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, and after being shifted by the speed change mechanism, is transmitted to the speed reducing mechanism of the human power system to rotate the driving wheel through the rotating casing. In addition, the driving force by the electric motor is decelerated by a power-system decelerating mechanism provided separately from the above-described human-powered decelerating mechanism, and then the manpower driving force and the electric driving force are combined in the rotating casing, and the driving wheel Is transmitted to.

  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. The drive signal is output to control the electric motor.

  However, in these structures, the electric motor is arranged at a position eccentric from the axis of the axle. 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 structures described in Patent Documents 3 and 4, since the speed reduction mechanism, the electric motor, and the speed change mechanism are provided on the axle, the increase in size of the hub can be suppressed.

  That is, in these structures, the speed reduction mechanism, the electric motor, and the speed change mechanism are arranged in parallel in the vehicle width direction in the hub of the rear wheel, which is the driving wheel, and the human power given by the pedal is transmitted through the chain. After being transmitted to the sprocket of the wheel and shifted by a transmission through a one-way clutch, the driving wheel is rotated through a rotating casing. Further, the driving force by the electric motor is decelerated by a speed reduction mechanism comprising a planetary gear mechanism provided around the axle, and then the human driving force and the electric driving force are combined in the rotating casing and transmitted to the driving wheel. It has become so.

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

  However, according to the structures described in Patent Documents 3 and 4, the output from the electric motor is transmitted to the hub case (rotary casing) via the speed reduction mechanism, and the driving force from the pedal is transmitted to the hub case (rotating casing) via the speed change mechanism. ).

  For this reason, the three mechanisms of the speed reducer, the electric motor, and the speed change mechanism that are arranged in parallel along the axis of the axle have independent structures. That is, the transmission mechanism of the human driving force and the transmission mechanism of the electric driving force are interposed independently by different routes.

Since the space in the axle direction of the drive wheels is limited, in such a structure, the space for the speed change mechanism is reduced, and it is difficult to increase the number of shift stages.
In this structure, since the axle and the motor output shaft are arranged in parallel in the axial direction, a large bending moment acts on the axle when a load acts on the axle and the motor shaft in the vertical direction. For this reason, the axle is required to have high strength, and if the axle and the motor output shaft are supported by a bearing or the like, there is a problem that an excessive load is applied to the support portion.

  In view of this, the present invention has a configuration in which three mechanisms of a speed reduction mechanism, an electric motor, and a speed change mechanism are provided in parallel along the axle of the drive wheel in the hub of the drive wheel. An object is to provide an axle support structure that can withstand.

  In order to solve the above-described problems, the present invention includes a speed change mechanism, a speed reduction mechanism, and a drive motor arranged in parallel in the axial direction of an axle inside a hub of a drive wheel supported by a frame, A planetary gear mechanism and at least one transmission sun gear, a transmission planetary gear meshing with the transmission sun gear, and a transmission planet carrier for holding the transmission planetary gear. The driving force generated by the pedaling force from the pedal is transmitted to the driving wheel, and the speed reduction mechanism is constituted by a planetary gear mechanism and is configured with at least one speed reducer sun gear and the speed reducer planetary gear engaged with the speed reducer sun gear. The planetary gear for the speed reducer is held by the planet carrier for the transmission, and transmits the driving force from the motor output shaft of the driving motor to the driving wheel. A battery-assisted bicycle or an electric two-wheeled vehicle comprising a shift control mechanism for performing a shift by switching a sun gear to be rotatable or non-rotatable around an axis of the axle, and supporting both axial ends of the axle with the frame. Adopted.

  According to this configuration, in the configuration in which the speed change mechanism, the speed reduction mechanism, and the drive motor are arranged in parallel in the axle direction inside the hub of the drive wheel, the speed reducer planetary gear is the speed change planetary carrier or the speed change planetary carrier. And is held by a member that rotates integrally. That is, the carrier for the transmission and the reducer can be made common, and the device in the axle direction can be made compact.

  In addition, since both ends of the axle in the axial direction are supported by the frame, the axle is fixed to the frame with both ends, so that the shaft rigidity can be improved compared to the conventional cantilever state and a large vertical load acting on the hub. Can withstand.

  Further, in this configuration, a driving force generated by a pedaling force from the pedal is input to the speed change mechanism via a sprocket provided on one end side in the axial direction of the axle with respect to the hub, If a configuration in which a speed change mechanism, a speed reduction mechanism, and a drive motor are provided in parallel from one end to the other end in the axial direction is adopted, the speed change mechanism and the speed reduction mechanism are close to each other. The structure for sharing the carrier can be simplified.

  In each of these configurations, a configuration in which the drive motor is supported by the axle can be employed. For example, the drive motor can be fixed to the axle so as not to rotate around the axis by screwing or the like. At this time, the axle may pass through the drive motor from one end side in the axial direction toward the other end side, and both ends in the axial direction of the axle may be supported by the frame.

  Further, the shaft center of the motor output shaft of the drive motor is aligned with the shaft center of the axle, and an axle insertion hole extending in the axial direction is provided in the motor output shaft, and the axle is driven through the axle insertion hole. A configuration in which the motor is drawn from one end side in the axial direction to the other end side can be employed. According to this configuration, the drive motor and the axle can be arranged coaxially, and the configuration with the best weight balance can be obtained.

  At this time, the planetary gear mechanism of the speed change mechanism and the speed reduction mechanism can be rotatably fixed to the axle via a bearing or the like in parallel with the drive motor. That is, the axle is both-ends fixed to the frame of the battery-assisted bicycle or the electric motorcycle, and the load is distributed by the drive motor and the planetary gear mechanism being fixed to the axle independently of each other. It becomes difficult to be influenced by bending with respect to the vertical load from each of the planetary gear mechanisms.

  Further, in each of these configurations, the transmission planetary gear and the reduction planetary gear may be configured to be held on the transmission planet carrier by different planet carrier shafts, respectively. This can be configured to be held by the planetary carrier for transmission by the same planetary carrier shaft. If the planetary gear for transmission and the planetary gear for reduction gear are held on the planetary carrier for transmission by the same planet carrier shaft, the structure for sharing the carrier for transmission and reduction gear is further simplified It can be.

  In each of these configurations, it is desirable that the transmission planetary gear and the reduction gear planetary gear have the same number, and in that case, the planet carrier shaft is used as the transmission planetary gear and the reduction gear. It is desirable to have the same number as the planetary gear. In the case where the number of planetary gears for transmission and the number of planetary gears for reduction gear is the same, the number of planetary carrier shafts is twice the number of planetary gears for transmission and the number of planetary gears for reduction gear. You can also.

  Further, the number of the planetary gears for transmission and the number of planetary gears for reduction gears can be freely set. When these numbers are the same, for example, the planetary gears for transmission and the planetary gears for reduction gears can be used. It is also possible to adopt a configuration in which the number is three each. Of course, regardless of the number, it is desirable that the planetary gear for transmission and the planetary gear for reduction gear are respectively arranged in an equally divided direction around the axis of the axle.

  Furthermore, the planetary gear for transmission and the planetary gear for reduction gear are held on the planetary carrier for transmission by separate planetary carrier shafts, and the axle of the planetary carrier shaft that holds the planetary gear for transmission It is possible to adopt a configuration in which the distance from the center of the shaft is different from the distance from the center of the axle of the planet carrier shaft that holds the planetary gear for reduction gear. By making the radial position (so-called PCD) of the planet carrier shaft holding the planetary gear for transmission and the planet carrier shaft holding the planetary gear for reduction gear different, it is for transmission and reduction gear. The operation of arranging each planetary gear becomes easier.

In each of these configurations, a spacing member is provided between the planetary gear for transmission and the planetary gear for reduction gear, and the spacing material contacts the planetary gear for transmission and the planetary gear for reduction gear. Therefore, it is possible to employ a configuration that functions as a cushioning material.
In particular, since the planetary gear for transmission and the planetary gear for reduction gear held by the same planetary carrier shaft have different rotational speeds, there is a risk that heat generation or wear may occur due to mutual contact. This is because the spacing material can prevent heat generation, wear, or damage caused by direct contact between the two.

  Alternatively, in each of these configurations, a spacing member may be provided between the transmission planetary gear and the reduction planetary gear, and the spacing member may employ a configuration that holds all the planet carrier shafts. it can. Since the spacing member holds the planet carrier shaft, the rigidity of the planet carrier shaft with respect to the vertical load can be increased.

  In addition, this spacing material may adopt a configuration having both a function as a buffer material by contacting the planetary gear for transmission and the planetary gear for reduction gear, and a function of holding all planet carrier shafts. it can.

In each of these configurations, the shift control mechanism may employ a configuration that performs the rotation or non-rotation switching via a clutch member provided between the transmission sun gear and the axle.
That is, according to this configuration, the transmission control mechanism can rotate the transmission sun gear and the axle with respect to the driving force via the clutch member provided between the transmission sun gear and the axle. Alternatively, it can be switched to be non-rotatable, and shifting can be enabled by the switching.

  A regenerative mechanism can also be added to this battery-assisted bicycle or electric motorcycle. That is, the transmission control mechanism can rotate or rotate the transmission sun gear around the axle with respect to the relative rotation in both directions around the transmission sun gear and the axle via the clutch member. By making the transmission sun gear and the axle unrotatable with respect to the reverse input from the drive wheel, the regenerative electric power generated by the reverse input is transmitted through the drive motor. It is the structure provided with the regeneration mechanism which returns to a secondary battery.

In other words, the sun gear for transmission can be switched to be rotatable or non-rotatable around the axle not only for the driving force by the pedaling force from the pedal but also for the reverse input from the driving wheel. If the reverse input from the drive wheel is transmitted to the drive motor in an appropriate state according to the above, regenerative charging is possible.
At this time, the reverse input from the drive wheel is always transmitted to the drive motor and the secondary battery is regeneratively charged. Whether or not to perform the regenerative charge can be controlled, for example, the operation of the brake lever By turning on the regenerative charging switch, it is possible to set so that regenerative charging is performed under optimum conditions only when necessary.

  In addition, because the space inside the hub is limited, the length of the sun gear of the planetary gear mechanism in the axle direction must be shortened. According to this configuration, the clutch member serves as a clutch for shifting and reverse input. By using the same member, the mechanism can be simplified and the axial length of the apparatus can be shortened. As this clutch member, for example, a ball, a key, or a ratchet can be used.

  Further, in each of these configurations, the clutch member is a ball that can move along the axial direction of the axle, and the ball can move or rotate by moving along the axial direction of the axle. It is possible to adopt a configuration for performing the impossible switching.

  In the configuration using the ball as the clutch member, the ball moves along the axial direction of the axle so that the ball faces a cam surface provided on the inner surface of the transmission sun gear, and the position facing the cam surface. If the ball moves to a position where the ball has been separated and the ball is in the facing position, the sun gear for transmission cannot be rotated around the axis of the axle with respect to the driving force, and the ball has been detached. If it exists in a position, the structure which the said sun gear for transmissions can rotate to the surroundings of the axis of the said axle with respect to a driving force is employable.

In each of these configurations, the shift control mechanism includes a control member between the axle and the transmission sun gear, and the control member intersects with the axis direction of the axle in an oblique direction. A longitudinal pocket is provided, the ball is held in the pocket, a ball groove is provided on the outer surface of the axle, and the ball shaft is rotated by the ball groove when the control member is rotated around the axle axis. A configuration that guides movement in a direction can be employed.
Since the longitudinal pocket intersects with the axial direction of the axle in an oblique direction, if the control member is rotated around the axis, the ball in the ball groove can be moved in the axial direction of the axle. .

  The ball groove can be configured to extend in parallel with the axial direction of the axle, for example. The ball groove extends in a direction obliquely intersecting the axial direction of the axle, the intersection direction of the ball groove with respect to the axial direction of the axle, and the intersecting direction of the pocket with respect to the axial direction of the axle. Can adopt a configuration opposite to the axial direction of the axle.

  Further, the pocket and the ball groove extend in a straight line, and if the intersection angle between the pocket and the ball groove is 30 degrees or more, the movement of the ball is smooth.

  In these configurations, it is possible to adopt a configuration in which the ball groove is provided with a relief groove for preventing the ball from interfering with the cam surface at a position separated from the position facing the cam surface. According to this configuration, the ball is prevented from erroneously interfering with the cam surface. In particular, when a plurality of sun gears are juxtaposed in the axial direction of the axle, the use of this relief groove is effective in preventing the adjacent sun gears from being engaged unexpectedly.

  Further, as another configuration of the clutch member, for example, the clutch member is a ball or key member fixed in the axial direction of the axle, and the ball or key member moves in the radial direction of the axle. It is possible to adopt a configuration for switching between rotation and non-rotation.

  The ball or key member moves in the radial direction of the axle so that it can be engaged with a cam surface provided on the inner surface of the transmission sun gear, and a position separated from the engageable position. If the ball or key member is in the engageable position, the transmission sun gear cannot rotate around the axle shaft with respect to the driving force, and the ball or key member If it is in the disengaged position, it is possible to employ a configuration in which the transmission sun gear can rotate around the axis of the axle with respect to the driving force.

  In this configuration, the shift control mechanism includes a control member between the axle and the transmission sun gear, and a hole is provided through the control member in the radial direction of the axle. It is possible to adopt a configuration that moves to the engageable position by entering the hole and moves to the disengaged position when coming out of the hole.

  The shift control mechanism may be configured to perform switching between the rotatable and the non-rotatable by moving the control member in the axial direction of the axle, and rotates the control member around the axle axis. Thereby, it can also be set as the structure which switches the said rotation possible or non-rotatable.

In each of these configurations, the number of the clutch members may be, for example, a configuration in which only one clutch member is disposed around the axle, but it is desirable that at least two clutch members be disposed around the axle shaft. .
Further, at that time, it is desirable that the clutch members are arranged at equal intervals around the axle.

Further, in each of these configurations, the planetary gear of the speed reduction mechanism is a two-stage gear, and an outer ring gear for a speed reducer provided in a motor housing holding a drive motor in one of the gears, a drive motor in the other gear By adopting a configuration in which a reduction gear sun gear provided on the motor output shaft is engaged, a high reduction ratio can be achieved.
Of course, since the number of stages can be arbitrarily set according to the specifications required for the battery-assisted bicycle or the electric motorcycle, for example, it can be one stage or can be three stages or more.

According to the present invention, the apparatus can be made compact in a configuration in which three mechanisms of a speed reducer, an electric motor, and a speed change mechanism are provided in parallel along the axis of the axle.
Further, since both ends in the axial direction of the axle are supported by the frame, the shaft rigidity can be improved as compared with the conventional cantilever state, and it is possible to withstand a large vertical load acting on the hub.

A longitudinal sectional view of a hub according to an embodiment of the present invention The principal part enlarged view which shows the effect | action of the clutch of the embodiment Sectional drawing which shows the effect | action of the clutch in the AA cross section of FIG. The assembled state of the planetary carrier for transmission, the planetary gear for transmission, the planetary gear for reduction gear, and the planetary carrier shaft is shown, (a) is a side view, (b) is a sectional view. Sectional view showing pocket part of planetary carrier for transmission Longitudinal sectional view of a hub according to another embodiment The assembled state of the planetary carrier for transmission, the planetary gear for transmission, the planetary gear for reduction gear, and the planetary carrier shaft is shown, (a) is a side view, (b) is a sectional view. Sectional view showing pocket part of planetary carrier for transmission Overall view of a power-assisted bicycle or electric motorcycle

  Embodiments of the present invention will be described with reference to the drawings. The battery-assisted bicycle of this embodiment is a battery-assisted bicycle of the rear hub motor type in which a drive motor 8 is provided inside a hub 1 (hereinafter referred to as “rear hub 1”) of a rear wheel that is a drive wheel. In addition, since the structure of this embodiment can be employ | adopted also as an electric two-wheeled vehicle and both structures are the same, it demonstrates as a battery-assisted bicycle below.

  As shown in FIG. 1, the driving force by the pedal force is referred to as a rear wheel 2 sprocket 9 (hereinafter referred to as “rear sprocket 9”) provided on one axial end side (left side in the figure) of the axle 14 with respect to the rear hub 1. ) Is input to the speed change mechanism 11. Further, in the hub case 12 provided coaxially with the axle 14 of the rear wheel 2, the speed change mechanism 11, the speed reduction mechanism 10, and the driving motor 8 are arranged from one axial end side to the other end side (right side in the drawing) of the axle 14. They are provided in parallel.

  Both ends of the axle 14 in the axial direction are fixed to the frame 6 of the battery-assisted bicycle. The drive motor 8 is fixed to the axle 14 so as not to rotate by screwing or the like. An axle insertion hole 8c is provided coaxially at the center of the motor output shaft 8a of the drive motor 8, and the axle 14 is inserted into the axle insertion hole 8c. The motor output shaft 8 a is rotatable around the axle 14.

  During driving, when a driving force based on the pedaling force transmitted from the crankshaft is input through the pedal 3 shown in FIG. 9, the power transmission element 4 such as a chain connecting the front sprocket and the rear sprocket 9 and the speed change mechanism 11 are used. Thus, the driving force can be transmitted to the rear wheel 2. The rear sprocket 9 is attached to the planetary carrier 11c for transmission of the transmission mechanism 11 via the one-way clutch 27.

  The shift control mechanism 15 for switching the shift mechanism 11 is manually or electrically operated by a shift change switch (not shown) attached to the handle 5 or the frame 6 of the battery-assisted bicycle outside the rear hub 1. ing.

  The driving force generated by the output of the driving motor 8 as an auxiliary force is transmitted to the transmission planet carrier 11c of the transmission mechanism 11 via the speed reduction mechanism 10 in the rear hub 1, and the transmission planet of the transmission mechanism 11 is transmitted. It is transmitted to the hub case 12 via the gear 11b and can be transmitted to the rear wheel 2.

  Further, during forward non-drive, the reverse input from the rear wheel 2 is increased from the transmission planetary gear 11b of the transmission mechanism 11 and the transmission planetary carrier 11c of the transmission mechanism 11 to the speed reduction mechanism 10 (in the case of reverse input). ) And the like, and a regenerative mechanism for reducing regenerative power generated by reverse input to the secondary battery 13 attached to the frame 6 and the like outside the rear hub 1 is provided.

  The transmission mechanism 11 is composed of a planetary gear mechanism that can increase the speed in three stages. The transmission mechanism 11 includes three transmission sun gears 11 a (11 a-1, 11 a-2, 11 a-3) provided on the outer periphery of the axle 14, and a transmission planetary gear that meshes with the transmission sun gear 11 a. 11b, and a transmission planet carrier 11c that holds the transmission planetary gear 11b.

  In this embodiment, the transmission sun gear 11a includes three sun gears, that is, a first sun gear 11a-1, a second sun gear 11a-2, and a third sun gear 11a-3. The first sun gear 11a-1, the second sun gear 11a-2, and the third sun gear 11a-3 are connected so as to be rotatable around the axle 14 (transmission control mechanism 15).

  The transmission planetary gear 11b has three gears with different numbers of teeth meshing with the first sun gear 11a-1, the second sun gear 11a-2, and the third sun gear 11a-3. The planetary gear 11b is held by a transmission planet carrier 11c. The transmission outer ring gear 11d that meshes with the transmission planetary gear 11b is integrated with the hub case 12.

  In this embodiment, the outer ring gear 11d for transmission is formed integrally with the hub case 12, but the outer ring gear 11d for transmission and the hub case 12 are formed separately and meshed so as to rotate together. Configuration is also conceivable.

  The number of transmission sun gears 11a can be set freely, and may be one, two, three, or four, for example, depending on the required gear. At this time, the number of gears of the planetary gear 11b for transmission is the same as the number of sun gears 11a for transmission.

  In this embodiment, the transmission outer ring gear 11d meshes with the gear having the second number of teeth of the transmission planetary gear 11b. Although it is possible to engage with other gears, this embodiment is desirable because the speed increasing ratio width between the three stages can be most earned.

Further, between the transmission planet carrier 11c and the transmission control mechanism 15, between the transmission control mechanism 15 and the axle 14, between the transmission planet carrier 11c and the hub case 12, and between the hub case 12 and the motor housing 8b. Between the motor housing 8b and the motor output shaft 8a, bearings 21, 26, 22, 23, and 24 are provided, respectively, so that they can rotate relative to each other.

  The speed reduction mechanism 10 includes a planetary gear mechanism, and includes one speed reducer sun gear 10a and a speed reducer planetary gear 10b that meshes with the speed reducer sun gear 10a.

  In this embodiment, the speed reducer planetary gear 10b is a two-stage gear having two-stage gears having different numbers of teeth, and is provided in a motor housing 8b that holds the drive motor 8 on the gear having the smaller number of teeth. The reduction gear outer ring gear 10d is engaged. The reduction gear sun gear 10 a provided on the motor output shaft 8 a of the drive motor 8 is meshed with the gear having the larger number of teeth. That is, the reduction mechanism 10 uses the motor output shaft 8a of the drive motor 8 as the reduction gear sun gear 10a, and the reduction gear planetary gear 10b and the reduction gear outer ring gear 10d that rotates together with the motor housing 8b ( Fixed) and a planetary carrier 11c for transmission that is common to the transmission mechanism 11.

The reduction gear planetary gear 10b is connected to the transmission planetary carrier 11c and the transmission planetary gear 11b by a planetary carrier shaft 11e. In other words, the planetary gear 10b for reduction gear is held by the planet carrier 11c for transmission and can rotate around the axle 14 integrally with the planet carrier 11c for transmission and the planet gear 11b for transmission.
Since the planetary gear 11b for transmission and the planetary gear 10b for reduction gear are supported by the planetary carrier shaft 11e with a common planet carrier shaft 11e, the planetary carrier of the transmission mechanism 11 and the planetary carrier of the reduction mechanism 10 are used. By making it common, the axle direction is made compact.

  As shown in FIG. 4, the planetary carrier 11c for transmission includes a first carrier portion 11g located on the transmission mechanism 11 side, and a connecting portion 11i protruding in the axial direction from the first carrier portion 11g. The tip of the connecting portion 11i (the end on the speed reduction mechanism 10 side) is the second carrier portion 11h.

  The planetary carrier 11c for transmission includes the planet carrier shaft 11e that connects the first carrier portion 11g and the second carrier portion 11h. In this embodiment, the first carrier portion 11g and the second carrier portion 11h are integrally formed, but a configuration in which these are used as separate members and connected by the planet carrier shaft 11e may be employed.

Further, as shown in FIG. 5, the planetary carrier 11c for transmission is formed with a pocket portion 11j for receiving the planetary gear 11b for transmission of the transmission mechanism 11 and the planetary gear 10b for reduction gear of the reduction mechanism 10. ing. In this pocket portion 11j, a planetary gear 11b for transmission and a planetary gear 10b for reduction gear are respectively accommodated, and the planetary gear 11b for transmission and the planetary gear 10b for reduction gear are rotatably supported by a planet carrier shaft 11e. ing.
That is, the planet carrier shaft 11e holds the planetary gear 11b for transmission with a degree of freedom of rotation around the planet carrier shaft 11e. Similarly, for the planetary gear 10b for reduction gear, the planet carrier shaft 11e holds the planetary gear shaft 10b for reduction gear with a degree of freedom of rotation around the planet carrier shaft 11e.

  In this embodiment, the number of transmission planetary gears 11b and the number of reduction gear planetary gears 10b are the same (three). Further, the transmission planetary gear 11b and the reduction planetary gear 10b are held on the transmission planet carrier 11c by the same planet carrier shaft 11e, thereby facilitating the assembly.

  The number of the planet carrier shafts 11e can be freely set. As in this embodiment, the number (three) of the planetary gears 11b for transmission and the planetary gears 10b for reduction gears is easy to allow for manufacturing errors. It is good.

Further, the transmission planetary gear 11b of the transmission mechanism 11 and the pocket portion 11j for receiving the reduction gear planetary gear 10b of the reduction mechanism 10 may be integrated. In this case, the transmission planetary gear 11b Since the rotational speed is different from that of the planetary gear 10b for reduction gear, there is a possibility that a problem of heat generation or wear may occur due to contact with each other.
For this reason, it is good to arrange | position the space | interval material 11f as another member between the planetary gear 11b for transmissions, and the planetary gear 10b for reduction gears.

  In this embodiment, the spacing member 11f is a plate-like member and is made of metal, resin, rubber, or the like.

  6 to 8, the planetary carrier shaft 11e of the planetary gear 11b for transmission and the planetary carrier shaft 10e of the planetary gear 10b for reduction gear are set as different axes, and they are oriented around the axis of the axle 14 (phase). ), The distances (PCD) of the planetary carrier shafts 10e and 11e from the axis of the axle 14 can be made different.

  In this embodiment, the number of planetary gears 11b for transmission and the number of planetary gears 10b for reduction gears is three, but the number of planetary gears 11b for transmission and planetary gears 10b for reduction gears can be set freely. However, it is desirable that the transmission planetary gear 11b and the reduction gear planetary gear 10b have the same number in order to balance the load.

FIG. 7 shows the positional relationship between the planetary carrier 11c for transmission, the planetary gear 11b for transmission, and the planetary gear 10b for reduction gear.
Here, the planetary carrier shaft 11e of the planetary gear 11b for transmission and the planetary carrier shaft 10e of the planetary gear 10b for reduction gear are set to P.P. C. D. By making these different from each other, the degree of freedom of design of each planetary gear mechanism can be increased, and the hub can be downsized (for example, the outer diameter of the hub case 12 can be reduced).

  Further, as shown in FIG. 8, the transmission planet carrier 11 c is formed with a pocket portion 11 j into which the transmission planetary gear 11 b of the transmission mechanism 11 and the planetary gear 10 b of the reduction mechanism 10 enter. This is the same as in the previous embodiment. In this pocket portion 11j, a planetary gear 11b for transmission and a planetary gear 10b for reduction gear are respectively accommodated. It is supported.

  In each of these embodiments, the speed change mechanism 11 includes three transmission sun gears 11a (first sun gear 11a-1, second sun gear 11a-2, and third sun gear 11a provided on the outer periphery of the axle 14. -3), by operating the speed change control mechanism 15, one of the transmission sun gears 11 a is selectively switched to be rotatable or non-rotatable around the axle 14 for each of the driving force and the reverse input. Can be changed.

  The switching is performed via a clutch 16 (clutch member 16a) provided between the transmission sun gear 11a and the axle 14.

  The clutch 16 includes a clutch member 16a made of a ball that can move along the axial direction of the axle 14, and the ball moves along the axial direction of the axle 14 so that the transmission sun gear 11a and the axle 14 are moved. The transmission sun gear 11a is selectively switched to be non-rotatable about the axis of the axle 14 and the others are rotatable.

  In this embodiment, the shift control mechanism 15 moves the clutch member 16a along the axial direction of the axle 14 by rotating a control member 15a provided around the axle 14 around the axle 14. By movement, the transmission sun gear 11a and the axle 14 can be switched to be rotatable or non-rotatable with respect to relative rotation in both directions around the axis.

  The bearing portions 21 and 26 described above are provided between the planetary carrier 11c for transmission and the control member 15a of the transmission control mechanism 15, and between the control member 15a of the transmission control mechanism 15 and the axle 14.

  Next, the operation of the speed change mechanism 11 will be described. For example, when the first sun gear 11a-1 is not rotatable with respect to the axle 14, the rotational speed from the rear sprocket 9 increases from the planetary carrier 11c for transmission. The speed is transmitted to the hub case 12 (transmission outer ring gear 11d).

At this time, the number of teeth of the first sun gear 11a-1 is a1, the number of teeth of the transmission planetary gear 11b meshed with the first sun gear 11a-1 is b1, and the transmission planetary gear meshed with the outer ring gear 11d for transmission. When the number of teeth of the gear 11b is b2 and the number of teeth of the outer ring gear 11d for transmission is d1, the speed increasing ratio from the planetary carrier 11c for transmission to the outer ring gear 11d for transmission is [(a1 × b2) / (b1 × d1)] + 1
It becomes. At this time, the second sun gear 11a-2 and the third sun gear 11a-3 are in an idle state and do not participate in torque transmission.

Further, when the second sun gear 11a-2 cannot be rotated about the axle 14, the number of teeth of the second sun gear 11a-2 is a2, and the number of teeth of the outer ring gear 11d for transmission is d1 as in the above example. Then, the speed increasing ratio from the planetary carrier 11c for transmission to the outer ring gear 11d for transmission is
[A2 / d1] +1
It becomes.

Further, when the third sun gear 11a-3 cannot be rotated on the axle 14, the number of teeth of the third sun gear 11a-3 is a3, and the teeth of the planetary gear 11b for transmission that meshes with the third sun gear 11a-3. If the number is b3, and the number of teeth of the transmission planetary gear 11b meshing with the transmission outer ring gear 11d is b2, and the number of teeth of the transmission outer ring gear 11d is d1 as in the above example, the planetary carrier for transmission is The speed increasing ratio from 11c to the outer ring gear 11d for transmission is
[(A3 × b2) / (b3 × d1)] + 1
It becomes.

The drive motor 8 is arranged in parallel in the axial direction of the speed change mechanism 11 and the axle 14, and the output of the drive motor 8 is transmitted to the planetary carrier for transmission via the speed reduction mechanism 10 using the planetary gear mechanism. 11c is decelerated and transmitted.
Further, the transmission planetary carrier 11 c is accelerated by the transmission mechanism 11 and transmitted to the hub case 12. The speed increase ratio at this time varies depending on which transmission sun gear 11 a cannot rotate with respect to the axle 14 by the shift control mechanism 15.

The output from the driving motor 8 is b4 for the number of teeth of the planetary gear 10b for the reduction gear meshing with the sun gear 10a for the reduction gear, d2 for the number of teeth of the outer ring gear 10d for the reduction gear, and the number of teeth for the sun gear 10a for the reduction gear. Is a4, and the number of teeth of the reduction gear planetary gear 10b meshing with the reduction gear outer ring gear 10d is b5, the reduction ratio from the reduction gear sun gear 10a to the transmission planet carrier 11c is [(d2 × b4) / (A4 × b5)] + 1
It becomes.

When the forward drive is not driven, the reverse input from the rear wheel 2 is transmitted from the hub case 12 to the planetary gear 11b for transmission. At this time, the clutch 16 provided between each transmission sun gear 11a and the axle 14 makes any one of the transmission sun gears 11a non-rotatable with respect to the axle 14 with respect to the reverse input. The others are rotatable.
As a result, the reverse input from the rear wheel 2 is decelerated via the speed change mechanism 11 and transmitted to the planetary carrier 11c for transmission, and further accelerated and transmitted to the drive motor 8 via the speed reduction mechanism 10. Regenerative charging is possible.

With these configurations, the driving force (stepping force) from the rear sprocket 9 is increased and transmitted to the rear wheel 2. The driving force from the drive motor 8 is decelerated via the speed reduction mechanism 10 and transmitted to the planetary carrier 11c for transmission, and then accelerated through the speed change mechanism 11 and transmitted to the rear wheel 2. .
On the other hand, the reverse input torque from the rear wheel 2 is decelerated by the speed change mechanism 11, accelerated by the speed reduction mechanism 10, and transmitted to the drive motor 8, so that regenerative charging is possible.

  Next, details of the shift control mechanism 15 will be described. As shown in FIGS. 1 to 3, the transmission control mechanism 15 includes three main members provided around the axle 14, that is, a control member 15a, a connecting member 15d, and an operation member 15e (see FIG. 1). The same applies to the embodiments shown in FIGS.

  The control member 15a, the connecting member 15d, and the operating member 15e are connected along the axial direction of the axle 14 by serration coupling so that they can rotate together as a unit. Further, the control member 15a is disposed so that a part thereof enters between the axle 14 and the transmission sun gear 11a.

Pockets 15b for holding at least two or more clutch members 16a are formed in the control member 15a in an equally divided direction (equally distributed) around the axis. As described above, in this embodiment, the clutch member 16a is a ball.
The pocket 15b has a longitudinal shape and extends in a direction intersecting in an oblique direction with respect to the axial direction of the axle 14 while being twisted in the axial direction over the entire length thereof.

In this embodiment, four clutch members 16a are arranged around the axle 14, but the number is arbitrary. However, for engagement stability, it is desirable to use two or more.
Further, when a plurality of the clutch members 16a are provided around the axis, it is desirable to arrange them in an equally divided direction around the axis of the axle 14.

  Further, the same number of ball grooves 14 a as pockets 15 b are formed on the outer surface of the axle 14. In this embodiment, the ball groove 14a extends in a direction intersecting in an oblique direction with respect to the axial direction of the axle 14 while being twisted in the axial direction over the entire length thereof. The ball groove 14 a may be formed in a straight line parallel to the axial direction of the axle 14.

  A ball as the clutch member 16a is held in each pocket 15b, and the ball is accommodated in the ball groove 14a.

The pocket 15b and the ball groove 14a extend linearly, and the intersection angle between the pocket 15b and the ball groove 14a is 30 degrees or more. If this crossing angle (twisting angle) is 30 degrees or more, smooth axial movement of the ball is possible when the control member 15a is rotated.
It is desirable that the twist angle of the pocket 15b and the ball groove 14a with respect to the axial direction of the axle 14 is the same angle in the opposite direction with respect to the axial direction of the axle 14.

A wire or the like (not shown) is connected to the operation member 15 e of the speed change control mechanism 15, and the wire is pulled by a signal from the above-described speed change switch, and the operation member 15 e is rotated around the axle 14. .
When the operation member 15e rotates around the axis of the axle 14, the control member 15a also rotates around the axis of the axle 14 via the connecting member 15d.

  By the rotation of the control member 15a, the ball moves in one direction along the axial direction of the axle 14 so as to be pushed out to the inner wall of the long pocket 15b. At this time, since the ball is accommodated in the ball groove 14a, the movement of the ball is guided in the direction in which the ball groove 14a extends. If the control member 15a rotates in the reverse direction, the ball moves in the other direction along the axial direction of the axle 14. The rotation of the control member 15a in the reverse direction automatically utilizes the urging force of an elastic member such as a spring, regardless of the operation of the wire, and when the pulling force of the wire is released or loosened. It may be performed.

  Each transmission sun gear 11a is provided with a petal-like cam surface 11k having concavities and convexities along the circumferential direction on the inner surface thereof. By the movement of the ball in the axial direction, the ball can move between a position facing the cam surface 11k of the transmission sun gear 11a and a position separated from the facing position in the axial direction. it can.

  If the ball is positioned so as to face the cam surface 11k of one transmission sun gear 11a by the movement, the cam surface 11k and the ball groove 14a of the axle 14 are engaged with each other via the ball (see FIG. 3). ), The axle 14 and the transmission sun gear 11a become non-rotatable. At this time, the clutch 16 can be engaged with the relative rotation in both directions around the axis of the axle 14 and the transmission sun gear 11a, so that the transmission sun gear 11a is also capable of driving force. It is impossible to rotate against reverse input.

  Further, if the ball is at a position away from the position facing the cam surface 11k, the transmission sun gear 11a can rotate around the axis of the axle 14. Therefore, the other two transmission sun gears 11a whose balls do not face the cam surface 11k can rotate around the axis of the axle 14 with respect to the driving force and the reverse input.

  Further, the ball groove 14a has a relief groove (for avoiding simultaneous interference with the adjacent transmission sun gear 11a when the ball is engaged with the cam surface 11k of one transmission sun gear 11a. (Not shown) may be provided. The escape groove may be formed slightly deeper than the other parts of the ball groove 14a at a position separated from the position facing the cam surface 11k in the axial direction.

  If the ball enters the escape groove, the ball moves slightly toward the inner diameter side, so that it does not interfere with the cam surface 11k of the transmission sun gear 11a. For this reason, when the engagement by the ball is switched from one transmission sun gear 11a to another transmission sun gear 11a, there is a neutral state that does not engage any of the transmission sun gears 11a. Therefore, smooth switching is possible.

  Further, as another embodiment of the speed change control mechanism 15, for example, a configuration in which a ball as the clutch member 16a is attached to each transmission sun gear 11a so as not to move in the axial direction can be employed. . Each ball is connected to a fixed element in the axle 14 by an elastic member accommodated in a radial hole provided in the axle 14, and each ball is moved in the outer diameter direction by the elastic force of the elastic member. It is energized.

  When the control member 15a of the speed change control mechanism 15 is rotated around the axis of the axle 14, when the ball faces a hole provided in the control member 15a (a hole penetrating in the radial direction of the axle 14), the ball It protrudes to an outer diameter direction through, and will be in the state which can be engaged with the cam surface 11k of the sun gear 11a for transmission which faces. Since the ball not facing the hole is prevented from protruding in the outer diameter direction by the control member 15a, the ball cannot be engaged with the cam surface 11k of the transmission sun gear 11a.

  This hole is a group of holes provided in the same number (four in this embodiment) as the number of balls arranged in the circumferential direction corresponding to one transmission sun gear 11a. The same number as the number of sun gears 11a for use is provided in parallel in the axial direction. The holes juxtaposed in the axial direction are provided at positions having different azimuths around the axis.

  For this reason, among the sun gears 11a for each transmission, the holes face all the balls arranged in the circumferential direction only with respect to one sun gear 11a for the transmission, and the balls protrude in the outer diameter direction through the holes. To do. Thereby, the transmission sun gear 11a can be made unrotatable with respect to the axle 14 in both directions of rotation around the axis.

  In this state, the positions of the holes are set so that the holes do not face the balls with respect to the other transmission sun gears 11a, and these balls do not protrude in the outer diameter direction. For this reason, the other transmission sun gear 11a can rotate in both directions of rotation around the axis with respect to the axle 14.

  That is, when the ball enters the hole of the control member 15a, it moves to a position where it can engage with the cam surface 11k of the transmission sun gear 11a. It moves to a position disengaged from a position where it can engage with the cam surface 11k. Moreover, the ball | bowl as the clutch member 16a can be engaged with the cam surface 11k only about one transmission sun gear 11a among the plurality of transmission sun gears 11a, and about other transmission sun gears 11a, The ball as the clutch member 16a cannot be engaged with the cam surface 11k. Note that a key member may be used instead of the ball as the clutch member 16a.

  The key member is attached to each transmission sun gear 11a so as not to move in the axial direction. Each key member is connected to a fixed element in the axle 14 by an elastic member accommodated in a radial hole provided in the axle 14. Each key member is urged in the outer diameter direction by the elastic force of the elastic member. About the effect | action, it is the same as that of the above-mentioned embodiment using a ball | bowl.

1 Rear hub (hub)
2 Rear wheels (drive wheels)
3 Pedal 4 Driving force transmission element (chain)
5 Handle 6 Frame 7 Hub flange 8 Drive motor 8a Motor output shaft 8b Motor housing 8c Axle insertion hole 9 Rear sprocket (sprocket)
DESCRIPTION OF SYMBOLS 10 Reduction mechanism 10a Reduction gear sun gear 10b Reduction gear planetary gear 10d Reduction gear outer ring gear 10e Planet carrier shaft 11 Transmission mechanism 11a Transmission sun gear 11a-1 First sun gear 11a-2 Second sun gear 11a- 3 3rd sun gear 11b planetary gear 11c for transmission planetary carrier 11d for transmission outer ring gear 11e for transmission 11e planetary carrier shaft 11f spacing material 11g first carrier part 11h second carrier part 11i connecting part 11j pocket part 11k cam surface 12 Hub case 14 Axle 15 Transmission control mechanism 15a Control member 15b Pocket 15d Connection member 15e Operation member 16 Clutch 16a Clutch members 21, 22, 23, 24, 25, 26 Bearing portion

Claims (12)

  A transmission mechanism (11), a speed reduction mechanism (10), and a drive motor (8) are arranged in parallel in the axial direction of the axle (14) inside the hub (1) of the drive wheel supported by the frame (6). The transmission mechanism (11) is constituted by a planetary gear mechanism, and includes at least one transmission sun gear (11a), a transmission planetary gear (11b) meshing with the transmission sun gear (11a), and A transmission planetary carrier (11c) that holds the transmission planetary gear (11b), and transmits the driving force by the pedaling force from the pedal to the drive wheel. The reduction mechanism (10) is driven by the planetary gear mechanism. And at least one reduction gear sun gear (10a) and a reduction gear planetary gear (10b) meshing with the reduction gear sun gear (10a), wherein the reduction gear planetary gear (10b) For transmission The driving force from the motor output shaft (8a) of the driving motor (8), which is held by the star carrier (11c), is transmitted to the driving wheel, and the transmission sun gear (11a) is transmitted to the driving wheel by the driving force A shift control mechanism (15) that shifts around the axle (14) so as to be rotatable or non-rotatable is provided, and both axial ends of the axle (14) are supported by the frame (6). A motor-assisted bicycle or an electric motorcycle.   A driving force by a pedaling force from the pedal is input to the speed change mechanism (11) via a sprocket (9) provided on one end side in the axial direction of the axle (14) with respect to the hub (1). In (1), the transmission mechanism (11), the speed reduction mechanism (10), and the drive motor (8) are provided in parallel from one axial end side to the other end side of the axle (14). The battery-assisted bicycle or the electric motorcycle according to claim 1.   The battery-assisted bicycle or electric motorcycle according to claim 1 or 2, wherein the driving motor (8) is supported by the axle (14).   An axle insertion hole (8c) extending in the axial direction is formed in the motor output shaft (8a) by aligning the axis of the motor output shaft (8a) of the drive motor (8) with the axis of the axle (14). The axle (14) is provided through the axle insertion hole (8c) and pulled out from one axial end side to the other end side of the drive motor (8). The electric assistance bicycle or electric motorcycle according to one.   The planetary gear for transmission (11b) and the planetary gear for reduction gear (10b) are held by the planetary gear for transmission (11c) by the same planetary carrier shaft (11e). Item 5. The battery-assisted bicycle or the electric motorcycle according to any one of Items 1 to 4.   The transmission planetary gear (11b) and the reduction gear planetary gear (10b) are the same number, and the planetary carrier shaft (11e) is connected to the transmission planetary gear (11b) and the reduction gear planetary gear. 6. The battery-assisted bicycle or electric motorcycle according to any one of claims 1 to 5, wherein the number is the same as (10b).   7. The battery-assisted bicycle or the motor-driven bicycle according to claim 1, wherein the number of planetary gears for transmission (11 b) and the number of planetary gears for reduction gears (10 b) are three each. Motorcycle.   The planetary gear for transmission (11b) and the planetary gear for reduction gear (10b) are held on the planetary carrier for transmission (11c) by separate planetary carrier shafts (10e, 11e), and are used for the transmission. The distance from the axis of the axle (14) of the planet carrier shaft (11e) holding the planetary gear (11b) and the planet carrier shaft (10e) holding the planetary gear (10b) for the speed reducer. The battery-assisted bicycle or electric motorcycle according to any one of claims 1 to 7, characterized in that a distance from an axis of the axle (14) is varied.   A spacing member (11f) is provided between the transmission planetary gear (11b) and the reduction gear planetary gear (10b), and the spacing member (11f) is connected to the transmission planetary gear (11b) and the reduction gear. The battery-assisted bicycle or motor-driven motorcycle according to any one of claims 1 to 8, wherein the motor-assisted bicycle or the motor-driven motorcycle functions as a cushioning material by being in contact with the planetary gear (10b). The shift control mechanism (15) performs the switching between the rotatable and non-rotatable via a clutch member (16a) provided between the transmission sun gear (11a) and the axle (14). The battery-assisted bicycle or electric motorcycle according to any one of claims 1 to 9.   The transmission control mechanism (15) is configured for the transmission with respect to relative rotation in both directions around the axis between the transmission sun gear (11a) and the axle (14) via the clutch member (16a). The sun gear (11a) can be switched to be rotatable or non-rotatable on the axle (14), and the transmission sun gear (11a) and the axle (14) 11. The electric motor according to claim 10, further comprising: a regenerative mechanism that reduces the regenerative power generated by reverse input to the rechargeable battery (13) through the drive motor (8) by making the motor non-rotatable. Auxiliary bicycle or electric motorcycle.   The planetary gear (10b) for the speed reducer is a two-stage gear, and the outer ring gear (10d) for the speed reducer provided in the motor housing (8b) holding the drive motor (8) in one gear is the other gear. The electric motor according to any one of claims 1 to 11, wherein a reduction gear sun gear (10a) provided on a motor output shaft (8a) of the drive motor (8) meshes with the gear. Auxiliary bicycle or electric motorcycle.

Images