阅读说明：本技术 利用变速电机和行星齿轮机构的自行车变速装置 (Bicycle speed changing device using variable speed motor and planetary gear mechanism ) 是由 孙淳荣 于 2019-03-04 设计创作，主要内容包括：本发明涉及利用变速电机和行星齿轮机构的自行车变速装置,具体包括：第一输入旋转轴,其连接于主动力源旋转；第二输入旋转轴,其从变速电机接收旋转力；行星齿轮机构,其从所述第一输入旋转轴和第二输入旋转轴接收旋转力；输出轴,其从所述行星齿轮机构接收旋转力；控制部,其控制所述变速电机而控制第二输入旋转轴的旋转方向和速度；且所述第一输入旋转轴与所述输出轴位于同心圆上,使变速装置的简洁小型化和多档变速得以实现。(The invention relates to a bicycle speed changing device using a speed changing motor and a planetary gear mechanism, which specifically comprises: a first input rotation shaft connected to the main power source for rotation; a second input rotary shaft receiving a rotational force from the variable speed motor; a planetary gear mechanism that receives rotational forces from the first and second input rotational shafts; an output shaft that receives a rotational force from the planetary gear mechanism; a control unit for controlling the variable speed motor to control a rotation direction and a speed of the second input rotary shaft; and the first input rotating shaft and the output shaft are positioned on a concentric circle, so that the simple miniaturization and multi-gear speed change of the speed change device are realized.)

1. A bicycle shifter utilizing a shift motor and a planetary gear mechanism, comprising:

a first input rotary shaft (10) which is connected to a main power source (11) and rotates;

a second input rotary shaft (20) receiving a rotational force from a speed change motor (21);

a planetary gear mechanism (30) that receives rotational forces from the first input rotational shaft (10) and the second input rotational shaft (20);

an output shaft (40) that receives a rotational force from the planetary gear mechanism (30);

a control unit (50) that controls the speed change motor (21) to control the rotational direction and speed of the second input rotary shaft (20);

the first input rotary shaft (10) and the output shaft (40) are located on a concentric circle.

2. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 1,

a worm (22) is arranged on the outer peripheral surface of the second input rotating shaft (20);

the planetary gear mechanism (30) includes: a frame (31) which is coupled to the first input rotation shaft and rotates together with the first input rotation shaft; a plurality of planetary gears (32) rotatably provided on the carrier (31); a ring gear (33) having an inner peripheral surface meshed with the outer peripheral surface of the planetary gear (32); a sun gear (34) having an extension (34 a) on one side, the extension being provided with a worm wheel (34 b) on the outer peripheral surface thereof, the worm wheel rotating around the first input rotary shaft (10) and meshing with the worm (22);

the second input rotary shaft (20) intersects an extension (34 a) of the sun gear (34) at a right angle.

3. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 2,

the ring gear (33) is provided with a hollow extension portion (33 a) surrounding the first input rotation shaft (10), the extension portion (33 a) is connected with an output shaft (40) surrounding the first input rotation shaft (10), and the output shaft (40) and the first input rotation shaft (10) are positioned on a concentric circle.

4. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 2,

the planetary gear (32) has a structure including: a first planetary gear (32 a) which is externally connected with the sun gear (34) for rotation;

and a second planetary gear (32 b) that rotates while being circumscribed about the first planetary gear (32 a) and while being inscribed in the ring gear (33).

5. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 1,

a worm (22) is arranged on the outer peripheral surface of the second input rotating shaft (20);

the planetary gear mechanism (30) includes: a frame (31) which is coupled to the first input rotation shaft (10) and rotates together therewith; a plurality of planetary gears (32) rotatably provided on the carrier (31); a ring gear (33) having an inner peripheral surface meshed with the outer peripheral surface of the planetary gear (32) and an outer peripheral surface provided with an extension (34 a) meshed with a worm wheel (33 b) rotating with the worm (22); a sun gear (34) meshed with the planetary gear (32) for rotation;

the second input rotary shaft (20) intersects an extension (33 a) of the ring gear (33) at a right angle.

6. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 5,

the sun gear (34) is provided with a hollow extension portion (34 a) surrounding the first input rotation shaft (10), the extension portion (34 a) is connected with an output shaft (40) surrounding the first input rotation shaft (10), and the output shaft (40) and the first input rotation shaft (10) are positioned on a concentric circle.

7. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 1,

a worm (22) is arranged on the outer peripheral surface of the second input rotating shaft (20);

the planetary gear mechanism (30) includes: a sun gear (34) that rotates together with the first input rotary shaft (10); a plurality of planetary gears (32) that are meshed with the sun gear (34) and rotate; the planetary gear (32) is rotatably provided and is provided with a carrier (31) having an extension part (31 b) on the outer peripheral surface of which a worm wheel (31 c) that is meshed with the worm (22) to rotate is provided; a ring gear (33) having an inner peripheral surface meshed with the outer peripheral surface of the planetary gear (32);

the second input rotation axis (20) intersects the extension of the frame (31) at right angles.

8. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 7,

the ring gear (33) is provided with a hollow extension portion (33 a) surrounding the first input rotation shaft (10), the extension portion (33 a) is connected with an output shaft (40) surrounding the first input rotation shaft (10), and the output shaft (40) and the first input rotation shaft (10) are positioned on a concentric circle.

9. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 1,

a worm (22) is arranged on the outer peripheral surface of the second input rotating shaft (20);

the planetary gear mechanism (30) includes: a ring gear (33) that rotates in conjunction with the first input rotary shaft (10); a plurality of planetary gears (32) having an outer peripheral surface meshed with an inner peripheral surface of the ring gear (33); the planetary gear (32) is rotatably provided and is provided with a carrier (31) having an extension part (31 b) on the outer peripheral surface of which a worm wheel (31 c) that is meshed with the worm (22) to rotate is provided; a sun gear (34) meshed with the planetary gear (32) for rotation;

the second input rotary shaft (20) intersects an extension (31 b) of the frame (31) at a right angle.

10. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 9,

the sun gear (34) is provided with a hollow extension portion (34 a) surrounding the first input rotation shaft (10), the extension portion (34 a) is connected with an output shaft (40) surrounding the first input rotation shaft (10), and the output shaft (40) and the first input rotation shaft (10) are positioned on a concentric circle.

11. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 9,

the planetary gear (32) has a structure including:

a first planetary gear (32 a) which is externally connected with the sun gear (34) for rotation;

and a second planetary gear (32 b) which is circumscribed to the first planetary gear (32 a) and is inscribed to the ring gear (33) for rotation.

12. The bicycle shifter using a variable speed motor and a planetary gear mechanism according to claim 1,

the main power source (11) is connected to both ends of the first input rotary shaft (10), respectively.

Technical Field

The present invention relates to a transmission, and more particularly, to a bicycle transmission using a shift motor and a planetary gear mechanism, which can facilitate shifting by transmitting power through a planetary gear mechanism including a ring gear, a planetary gear, a sun gear, and a carrier.

Background

It is generally possible to efficiently transmit a large power to a compact type device by using a planetary gear device.

The gear device has the advantages that compared with the gear device used by the existing manual speed change gear with a plurality of gears respectively arranged on more than two parallel shafts, the gear teeth (Gearteteth) of each gear are less in load, small in arrangement space and low in running noise.

The disadvantage of this is that the required transmission ratio cannot be obtained with one planetary gear device, and that more than two planetary gear devices are required, which makes the structure complicated.

The structure of the planetary gear device includes: a frame; a plurality of planetary gears provided on the carrier; a ring gear in inner contact engagement with the planetary gear; and the sun gear is externally engaged with the planet gear. The speed ratio is adjusted according to the number of teeth of the sun gear and the ring gear, which part of the input shaft and the output shaft for transmitting the main power is meshed with the sun gear, the ring gear and the carrier of the planetary gear device, the rotating direction and the rotating speed of the sun gear, the ring gear and the carrier, and the like.

The Planetary gear (Planetary gears) can simplify and lighten the gear box, is widely applied to equipment such as intelligent robots, R/C, aircrafts, automobiles, office equipment, mechanical tools and the like which need to be small and light, has outstanding transmission efficiency and uniform force distribution, and can better resist high torque.

Conventionally, transmission devices that perform multi-speed transmission using two or more planetary gear devices have been used in various fields such as automobiles, but the larger the number of transmission stages, the larger the number of planetary gear device groups, and the more complicated the structure.

In the case of a bicycle, a ring gear (Internal gear) such as Shimano (Shimano) and Sram (pram) is a principle of a plurality of planetary gear devices using machines, and has a complicated structure and a large number of components. As proposed in korean registered patent No. 10-1434483, multi-speed transmission can be achieved using the principle of two driving motors and a planetary gear device, but there is a problem in that the structure is complicated. The electric bicycle uses a plurality of gears to reduce speed and simultaneously realize multi-gear speed change, but the speed reduction ratio is fixed, a motor with relatively large capacity is required, and the speed change gear is relatively limited. The problems that have arisen are miniaturization and energy use efficiency.

The problems of downsizing and improving energy use efficiency of a transmission have been always concerned in the entire industrial fields of bicycles and the like.

Disclosure of Invention

Technical subject

The present invention has been made in view of the above problems, and it is an object of the present invention to provide a bicycle transmission apparatus using a shift motor and a planetary gear mechanism, which is miniaturized by disposing a first input rotary shaft for providing a main power and an output shaft for receiving the power and transmitting a rotational force through a shifting process to the outside on concentric circles, and independently connecting a second input rotary shaft for providing a power of a shifting power for shifting, the first input rotary shaft, and the output shaft to a plurality of components of the planetary gear mechanism.

The invention aims to provide a bicycle speed changing device using a speed changing motor and a planetary gear mechanism, which can improve the design of a bicycle and realize the light weight of the bicycle.

The present invention provides a bicycle transmission device using a shift motor and a planetary gear mechanism, which has a reduced number of parts, simplifies the coupling between components, and reduces the manufacturing cost.

Technical scheme

To solve the above problems, a bicycle shifting device using a shift motor and a planetary gear mechanism of the present invention includes: a first input rotation shaft connected to the main power source for rotation; a second input rotary shaft receiving a rotational force from the variable speed motor; a planetary gear mechanism that receives rotational forces from the first and second input rotational shafts; an output shaft that receives a rotational force from the planetary gear mechanism; a control unit for controlling the variable speed motor to control a rotation direction and a speed of the second input rotary shaft; and the first input rotating shaft and the output shaft are positioned on a concentric circle.

A worm is arranged on the peripheral surface of the second input rotating shaft; the planetary gear mechanism includes: a frame coupled to the first input rotation shaft to rotate together; a plurality of planet gears rotatably disposed on the carrier; a ring gear having an inner peripheral surface meshed with an outer peripheral surface of the planetary gear; a sun gear having an extension part of a worm wheel provided on one side surface thereof, the extension part surrounding the first input rotary shaft and being engaged with the worm to rotate; the second input rotary shaft intersects the extension of the sun gear at a right angle.

The gear ring is provided with a hollow extension part surrounding the first input rotating shaft, the extension part is connected with an output shaft surrounding the first input rotating shaft, and the output shaft and the first input rotating shaft are positioned on a concentric circle.

The structure of the planetary gear includes: a first planetary gear circumscribing the sun gear; and a second planetary gear circumscribed with the first planetary gear and inscribed with the ring gear to rotate.

A worm is arranged on the peripheral surface of the second input rotating shaft; the planetary gear mechanism includes: a frame coupled to the first input rotation shaft to rotate together; a plurality of planet gears rotatably disposed on the carrier; a ring gear having an inner peripheral surface meshed with the outer peripheral surface of the planetary gear and an outer peripheral surface provided with an extension portion meshed with a worm wheel rotating with the worm; a sun gear meshed with the planetary gear for rotation; and the second input rotary shaft intersects the extension of the ring gear at right angles.

The sun gear is provided with a hollow extension portion surrounding the first input rotating shaft, the extension portion is connected with an output shaft surrounding the first input rotating shaft, and the output shaft and the first input rotating shaft are positioned on a concentric circle.

A worm is arranged on the peripheral surface of the second input rotating shaft; the planetary gear mechanism includes: a sun gear coupled to the first input rotation shaft to rotate together; a plurality of planetary gears meshed with the sun gear for rotation; the planetary gear is rotatably arranged and is provided with a frame, the outer peripheral surface of the frame is provided with an extension part meshed with a worm wheel rotating by the worm; a ring gear having an inner peripheral surface meshed with the outer peripheral surface of the planetary gear); and the second input rotation axis intersects the extension of the frame at right angles.

The gear ring is provided with a hollow extension part surrounding the first input rotating shaft, the extension part is connected with an output shaft surrounding the first input rotating shaft, and the output shaft and the first input rotating shaft are positioned on a concentric circle.

A worm is arranged on the peripheral surface of the second input rotating shaft; the planetary gear mechanism includes: a ring gear coupled to the first input rotation shaft to rotate together; a plurality of planetary gears having an outer peripheral surface meshed with an inner peripheral surface of the ring gear; the planetary gear is rotatably arranged and is provided with a frame, the outer peripheral surface of the frame is provided with an extension part meshed with a worm wheel rotating by the worm; a sun gear meshed with the planetary gear for rotation; and the second input rotation axis intersects the extension of the frame at right angles.

The sun gear is provided with a hollow extension portion surrounding the first input rotating shaft, the extension portion is connected with an output shaft surrounding the first input rotating shaft, and the output shaft and the first input rotating shaft are positioned on a concentric circle.

The structure of the planetary gear includes: a first planetary gear circumscribing the sun gear; and the second planetary gear is externally connected with the first planetary gear and internally connected with the gear ring to rotate.

The main power source is connected to both ends of the first input rotation shaft, respectively.

Advantageous effects

The bicycle speed changing device using the speed changing motor and the planetary gear mechanism according to the present invention has an advantageous effect in that a first input rotation shaft and an output shaft receiving a rotation force from a main power source are disposed on a concentric circle, and a plurality of members of the planetary gear mechanism are connected to a second input rotation shaft and an output shaft receiving a rotation force from the first input rotation shaft and the speed changing motor, thereby constituting a planetary gear mechanism and a speed changing motor, thereby achieving miniaturization of the speed changing device;

due to the realization of miniaturization, when the bicycle is applied to equipment such as bicycles and the like, the aesthetic feeling on design can be increased, and the bicycle can also realize diversified design;

the bicycle can be miniaturized and multi-gear speed change can be realized, so that the weight of the bicycle is reduced;

the number of fittings is small, and the connecting structure among a plurality of components is not complex, so that the manufacturing cost is saved;

the speed of the main power generated from the main power source for running can be changed by adjusting the speed of the main power by a speed change motor little by little, thereby realizing the miniaturization of the speed change motor.

Drawings

FIG. 1 is a schematic view showing a first embodiment of a bicycle shifting device utilizing a shift motor and a planetary gear mechanism in accordance with the present invention;

FIG. 2 is a schematic view showing a second embodiment of the bicycle shifting device utilizing the shift motor and the planetary gear mechanism of the present invention;

FIG. 3 is a schematic view showing a third embodiment of the bicycle shifting device utilizing the shift motor and the planetary gear mechanism of the present invention;

FIG. 4 is a schematic diagram showing a fourth embodiment of the bicycle shifting device utilizing the shift motor and the planetary gear mechanism of the present invention.

Detailed Description

Embodiments of a bicycle shifting device utilizing a shift motor and a planetary gear mechanism in accordance with the present invention will be described in detail with reference to the accompanying drawings.

FIG. 1 is a schematic view showing a first embodiment of a bicycle shifting device utilizing a shift motor and a planetary gear mechanism in accordance with the present invention;

the transmission of the present invention illustrated in fig. 1 is a transmission that transmits a rotational force generated according to the movement of pedals provided to a bicycle to a wheel while increasing and decreasing the rotational force as needed, and has a structure including: a first input rotary shaft 10 powered from the outside; a second input rotary shaft 20 receiving a rotational force from a variable speed motor 21; a planetary gear mechanism 30 that receives rotational force from the first input rotational shaft 10 and the second input rotational shaft 20; an output shaft 40 that receives a rotational force from the planetary gear mechanism 30; and a control unit 50 for controlling the speed change motor 21 to control the rotational direction and speed of the second input rotary shaft 20.

The first input rotation shaft 10 is connected to the main power source 11 to receive a rotation force and rotate. At least one of both ends of the first input rotary shaft 10 is connected to a main power source 11 such as a pedal or a driving motor (e.g., an electric bicycle) which is rotated by a user's foot, and the first input rotary shaft 10 is rotated by a rotational force transmitted from the main power source 11.

That is, the main power source 11 may be connected to only one side end of the first input rotation shaft 10, but may be connected to one end of the first input rotation shaft 11.

The second input rotary shaft 20 is rotated by receiving a rotational force from the speed change motor 21, and the rotary shaft of the speed change motor 21 may be integrally formed by extending or may be formed by connecting a single shaft to the rotary shaft of the speed change motor 21.

The structure of the planetary gear mechanism 30 includes: a frame 31; a plurality of planetary gears 32 rotatably provided on the carrier 31; a ring gear 33 having an inner peripheral surface meshed with the outer peripheral surface of the pinion gear 32; a sun gear 34 that rotates in mesh with the planetary gears 32.

The carrier 31 rotatably supports a plurality of planetary gears 32, and a central portion thereof is coupled to the first input rotary shaft 10 to rotate together with the first input rotary shaft 10 in the same direction and at the same speed. At this time, since the thickness of the frame 31 is too thin, the frame 31 and the first input rotary shaft 10 cannot be stably coupled, a hollow extension (not shown) having a certain length is formed to protrude at a central portion of the frame 31, and the hollow extension is coupled to the first input rotary shaft 10 to reinforce the coupling force with the first input rotary shaft 10.

More specifically, when the first input rotary shaft 10 is coupled to the central portion of the bracket 31, a plurality of elongated protrusions are formed on the first input rotary shaft 10 by a coupling relationship of splines and bushings, and an insertion groove into which the protrusions are inserted is formed in the center portion of the bracket 31, so that the first input rotary shaft 10 is inserted through the central portion of the bracket 31 and the rotational force of the first input rotary shaft 10 is transmitted to the bracket 31 without loss. In addition, since there are various coupling structures for transmitting the rotational force of the first input rotary shaft 10 to the carrier 31 without loss, descriptions of other coupling methods will be omitted here.

The carrier 31 includes a plurality of support shafts 31a, and the support shafts 31a penetrate through the central portions of the planetary gears 32. The planetary gear 32 further rotates about the support shaft 31a of the carrier 31.

The planetary gears 32 are rotatably supported by a support shaft 31a, are disposed around a sun gear 34, and are composed of first planetary gears and second planetary gears 32b circumscribed with the first planetary gears 32 a.

The first planetary gears 32a are circumscribed for rotation with the sun gear 34.

The second planetary gear 32b is circumscribed with the first planetary gear 32a and rotates in contact with the ring gear 33.

The ring gear 33 is a portion where the output shaft 40 is provided, and the inner peripheral surface is provided with gear teeth with which the second planetary gears 32b are meshed.

The central portion of the ring gear 33 is provided with a hollow extension 33a that surrounds the first input rotation shaft 10. The extension 33a of the ring gear 33 is connected to an output shaft 40 that surrounds the first input rotation shaft 10, and the output shaft 40 and the first input rotation shaft 10 are located on a concentric circle.

The sun gear 34 receives a rotational force from the second input rotary shaft 20 and rotates in mesh with the planetary gears 32. The sun gear 34 is located at the most central position of the planetary gear mechanism 30, and teeth are formed along the outer peripheral surface thereof, which mesh with teeth formed on the outer peripheral surface of the first planetary gears 32 a.

The sun gear 34 is penetrated through the first input rotary shaft 10 at the center, and a bearing is provided between the first input rotary shaft 10 and the sun gear 34 so that the rotational force of the first input rotary shaft 10 does not directly affect the sun gear 34.

A hollow extension portion 34a surrounding the first input rotary shaft 10 is provided on one side surface of the sun gear 34, and a worm wheel 34b is provided on an outer peripheral surface of the extension portion 34a of the sun gear 34.

The worm 22 meshing with the worm wheel 34b is provided on the outer peripheral surface of the second input rotary shaft 20, and when the second input rotary shaft 20 is rotated by the transmission motor 21 to which the rotational force is transmitted, the worm 22 is also rotated to rotate the worm wheel 34b meshing with the worm 22, and the extension portion 34a of the sun gear 34 is rotated by the rotation of the worm wheel 34b, and finally the sun gear 34 is rotated.

The output shaft 40 is a part provided in the ring gear 33 to receive the rotational force, and may be integrally formed by extending the extension part 33a of the ring gear 33, or may be formed by coupling a hollow pipe to the extension part 33a of the ring gear 33 by the spline and bushing method described above.

The output shaft 40 is disposed concentrically with the first input rotation shaft 10 because the center portion thereof is penetrated by the first input rotation shaft 10. And the output shaft 40 is disposed on a concentric circle with the carrier 31 and the ring gear 33 and the sun gear 34.

As described above, the second input rotary shaft 20 is provided with the worm 22 on the outer peripheral surface thereof, and the extension 34a of the sun gear 34 is provided with the worm wheel 34b that is meshed with the worm 22 and rotates, so that the second input rotary shaft 20 and the extension 34a of the sun gear 34 intersect at a right angle.

The control unit 50 controls the rotation speed of the shift motor 21 by rotating the shift motor 21 in the forward and reverse directions.

The shifting process of the shifting apparatus of fig. 1 constituted as described above will be briefly described.

When the main power source 11 such as a pedal or a drive motor is operated, the first input rotary shaft 10 rotates, and the rotational force of the first input rotary shaft 10 is transmitted to the carrier 31, the planetary gears 32, and the ring gear 33 in this order.

While the variable speed motor 21 is operated and the second input rotation shaft 20 is rotated, the rotation force of the second input rotation shaft 20 is sequentially transmitted to the sun gear 34 and the planetary gear 32.

Whereupon the rotational force provided by the main power source 11 and the rotational force provided by the change speed motor 21 are combined and shifted and transmitted to the output shaft 40 via the ring gear 33.

In addition, the bicycle shifting device using the shift motor and the planetary gear mechanism of the present invention can also be constructed as shown in fig. 2.

FIG. 2 is a schematic diagram showing a second embodiment of the bicycle shifting device utilizing the shift motor and the planetary gear mechanism of the present invention.

The transmission of the present invention illustrated in fig. 2 is not significantly different from the transmission illustrated in fig. 1 in terms of structure, and the description will be mainly made with a distinguished portion as a main point.

The structure of the transmission device of the present invention illustrated in fig. 2 includes: a first input rotary shaft 10 connected to the main power source 11 for rotation; a second input rotary shaft 20 receiving a rotational force from a variable speed motor 21; a planetary gear mechanism 30 that receives rotational force from the first input rotational shaft 10 and the second input rotational shaft 20; an output shaft 40 that receives a rotational force from the planetary gear mechanism 30; and a control unit 50 for controlling the speed change motor 21 to control the rotational direction and speed of the second input rotary shaft 20.

The planetary gear mechanism 30 includes: a frame 31; a plurality of planetary gears 32 rotatably provided on the carrier 31; a ring gear 33 having an inner peripheral surface meshed with the outer peripheral surface of the pinion gear 32; a sun gear 34 rotating in mesh with the planetary gears 32 and provided with an output shaft 40.

The carrier 31 rotatably supports the plurality of planetary gears 32, and a central portion thereof is coupled to the first input rotary shaft 10 to rotate together with the first input rotary shaft 10 in the same direction and at the same speed. The carrier 31 includes a support shaft 31a penetrating a central portion of the planetary gear 32.

The planetary gears 32 are rotatably supported on the support shafts 31a of the carrier 31.

The ring gear 33 is provided with gear teeth on an inner peripheral surface thereof, which are engaged with the planetary gears 32 to receive a rotational force from the second input rotational shaft 20.

In addition, the ring gear 33 is provided with an extension 33a that surrounds the first input rotation shaft 10, and a worm wheel 33b is provided on the outer circumferential surface of the extension 33a of the ring gear 33. The second input rotary shaft 20 is provided on its outer peripheral surface with a worm 22 meshing with the worm wheel 33 b. When the second input rotary shaft 20 is rotated by the transmission motor 21 transmitting the rotational force, the worm 22 is also rotated, the worm wheel 33b engaged with the worm 22 is rotated, the extension 33a of the ring gear 33 is rotated by the rotation of the worm wheel 33b, and finally the ring gear 33 is rotated.

The sun gear 34 is located at the center of the planetary gear mechanism 30 and has gear teeth along the outer peripheral surface thereof, which are engaged with the gear teeth formed on the outer peripheral surface of the planetary gear 32.

Since the sun gear 34 is penetrated through the first input rotary shaft 10 at the center and a bearing is provided between the first input rotary shaft 10 and the sun gear 34, the rotational force of the first input rotary shaft 10 does not directly affect the sun gear 34.

The sun gear 34 has a hollow extension portion 34a provided at a central portion thereof so as to surround the first input rotation shaft 10, and an output shaft 40 provided on the extension portion 34a of the sun gear 34 so as to surround the first input rotation shaft 10.

The output shaft 40 may be integrally formed by extending the extension portion 34a of the sun gear 34, or may be formed by combining a hollow pipe with the extension portion 34a of the sun gear 34 by spline or bushing.

The output shaft 40 is disposed concentrically with the first input rotation shaft 10 because the center portion thereof is penetrated by the first input rotation shaft 10. And the output shaft 40 is disposed on a concentric circle with the carrier 31 and the ring gear 33 and the sun gear 34.

As described above, the second input rotary shaft 20 has the worm 22 on the outer peripheral surface thereof, and the extension portion 34a of the ring gear 33 has the worm wheel 33b that is engaged with the worm 22 and rotates, so that the second input rotary shaft 20 and the extension portion 33a of the ring gear 33 intersect at a right angle.

The shifting process of the shifting apparatus of fig. 2 constituted as described above will be briefly described.

When the main power source 11 such as a pedal or a drive motor is operated, the first input rotary shaft 10 rotates, and the rotational force of the first input rotary shaft 10 is transmitted to the carrier 31, the planetary gears 32, and the sun gear 34 in this order.

While the variable speed motor 21 is operated and the second input rotation shaft 20 is rotated, the rotation force of the second input rotation shaft 20 is sequentially transmitted to the ring gear 33 and the planetary gears 32.

Whereupon the rotational force provided by the main power source 11 and the rotational force provided by the shift motor 21 are combined and shifted and transmitted to the output shaft 40 via the sun gear 34.

The transmission illustrated in fig. 1 and 2 is explained above, and the transmission illustrated in fig. 3 is explained below.

FIG. 3 is a schematic diagram showing a third embodiment of the bicycle shifting device utilizing the shift motor and the planetary gear mechanism of the present invention.

When the transmission device of the present invention illustrated in fig. 3 is explained, the explanation will be mainly focused on the differences from the transmission device illustrated in fig. 1 and 2.

The structure of the transmission device of the present invention illustrated in fig. 3 includes: a first input rotary shaft 10 connected to the main power source 11 for rotation; a second input rotary shaft 20 receiving a rotational force from a variable speed motor 21; a planetary gear mechanism 30 that receives rotational force from the first input rotational shaft 10 and the second input rotational shaft 20; an output shaft 40 that receives a rotational force from the planetary gear mechanism 30; and a control unit 50 for controlling the speed change motor 21 to control the rotational direction and speed of the second input rotary shaft 20.

The planetary gear mechanism 30 includes: a sun gear 34; a plurality of planetary gears 32 meshed with the sun gear 34 for rotation; a carrier 31 in which the planetary gears 32 are rotatably provided; the inner peripheral surface of the ring gear 33 is meshed with the outer peripheral surface of the planetary gear 32 and provided with the output shaft 40.

The sun gear 34 is located at the center of the planetary gear mechanism 30, and has gear teeth formed along the outer peripheral surface thereof, which are engaged with the gear teeth formed on the outer peripheral surface of the planetary gear 32.

The sun gear 34 is coupled to the first input rotary shaft 10 at a central portion thereof by a spline and a sleeve, and rotates in the same direction and at the same speed together with the first input rotary shaft 10.

The planetary gear 32 is rotatably supported by a support shaft 31a of the carrier 31, and is circumscribed with the sun gear 34 and inscribed with the ring gear 33.

The carrier 31 receives a rotational force from the second input rotation shaft 20.

In addition, the extension 31b surrounding the first input rotation shaft 10 is provided on the frame 31, and the worm wheel 31c is provided on the outer peripheral surface of the extension 31b of the frame 31. The second input rotary shaft 20 is provided with a worm 22 meshing with the worm wheel 31 c. When the second input rotary shaft 20 is rotated by the transmission motor 21 transmitting the rotational force, the worm 22 is also rotated, the worm wheel 31c engaged with the worm 22 is rotated, the extension portion 31b of the holder 31 is rotated by the rotation of the worm wheel 31c, and finally the ring gear 31 is rotated.

The ring gear 33 is provided with gear teeth on an inner peripheral surface thereof, which are engaged with the pinion gears 32, and a hollow extension 33a around the first input rotation shaft 10 at a central portion thereof.

An output shaft 40 is connected to the extension 33a of the ring gear 33 so as to surround the first input rotation shaft 10.

The output shaft 40 may be formed by integrally extending the extension portion 33a of the ring gear 33, or may be formed by combining a hollow pipe with the extension portion 33a of the ring gear 33 by a spline and a sleeve method.

The output shaft 40 is penetrated through the first input rotation shaft 10 at a central portion thereof and is disposed concentrically with the first input rotation shaft 10. And the output shaft 40 is disposed on a concentric circle with the carrier 31, the ring gear 33, and the sun gear 34.

As described above, the second input rotary shaft 20 has the worm 22 on the outer peripheral surface thereof, and the extension 31b of the frame 31 has the worm wheel 31c that is engaged with the worm 22 and rotates, so that the second input rotary shaft 20 and the extension 31b of the frame 33 intersect at a right angle.

The shifting process of the shifting apparatus of fig. 3 constituted as described above will be briefly described.

After the main power source 11 such as a pedal or a driving motor is operated, the first input rotation shaft 10 is rotated, and the rotational force of the first input rotation shaft 10 is sequentially transmitted to the sun gear 34, the planetary gears 32, and the ring gear 33.

While the variable speed motor 21 is operated and the second input rotation shaft 20 is rotated, the rotation force of the second input rotation shaft 20 is sequentially transmitted to the carrier 31 and the planetary gears 32.

Whereupon the rotational force provided by the main power source 11 and the rotational force provided by the change speed motor 21 are combined and shifted and transmitted to the output shaft 40 via the ring gear 33.

The transmission illustrated in fig. 1 to 3 is described above, and the transmission illustrated in fig. 4 is described below.

FIG. 4 is a schematic diagram showing a fourth embodiment of the bicycle shifting device utilizing the shift motor and the planetary gear mechanism of the present invention.

In describing the transmission of the present invention illustrated in fig. 4, the explanation will be mainly given of the portions different from the transmission illustrated in fig. 1 to 4.

The structure of the transmission device of the present invention illustrated in fig. 4 includes: a first input rotary shaft 10 connected to the main power source 11 for rotation; a second input rotary shaft 20 receiving a rotational force from a variable speed motor 21; a planetary gear mechanism 30 that receives rotational force from the first input rotational shaft 10 and the second input rotational shaft 20; an output shaft 40 that receives a rotational force from the planetary gear mechanism 30; and a control unit 50 for controlling the speed change motor 21 to control the rotational direction and speed of the second input rotary shaft 20.

The planetary gear mechanism 30 includes: a ring gear 33; a plurality of planetary gears 32 whose outer peripheral surfaces mesh with the inner peripheral surface of the ring gear 33; a carrier 31 in which the planetary gears 32 are rotatably provided; a sun gear 34 engaged with the planetary gears 32 and provided with an output shaft 40.

The ring gear 33 is provided with gear teeth on an inner peripheral surface thereof, which are engaged with the planetary gears 32 and receive a rotational force from the first input rotational shaft 10.

In addition, the ring gear 33 is coupled to the first input rotary shaft 10 at a central portion thereof by means of splines and bushings, and rotates in the same direction and at the same speed together with the first input rotary shaft 10. If the thickness of the ring gear 33 is too thin, the ring gear 33 and the first input rotary shaft 10 cannot be stably coupled, and therefore, a hollow extension portion (not shown) of a certain length is formed to protrude from the central portion of the ring gear 33, and the hollow extension portion is coupled to the first input rotary shaft 10 to reinforce the coupling force with the first input rotary shaft 10.

The planetary gear 32 is rotatably supported by a support shaft 31a of the carrier 31 and disposed around a sun gear 34, and is composed of a first planetary gear 32a, and a second planetary gear 32b circumscribed with the first planetary gear 32 a.

The first planetary gears 32a are circumscribed for rotation with the sun gear 34.

The second planetary gear 2b is circumscribed with the first planetary gear 32a and rotates in contact with the ring gear 33.

It should be noted that the first planetary gear 32a and the second planetary gear 32b are disposed between the ring gear 33 and the sun gear 34, the first planetary gear 32a is circumscribed with the sun gear 34, the second planetary gear 32b is inscribed with the ring gear 33, and the first planetary gear 32a and the second planetary gear 32b are circumscribed with each other and rotate in opposite directions.

The carrier 31 is a member having a support shaft 31a penetrating a central portion of the planetary gears 32 on one side end thereof for rotatably supporting the plurality of planetary gears 32. The carrier 31 receives a rotational force from the second input rotation shaft 20.

In addition, a hollow extension 31b surrounding the first input/rotation shaft 10 and the output shaft 40 is provided at a central portion of one end of the frame 31, and a worm wheel 31c is provided on an outer circumferential surface of the extension 31b of the frame 31. The second input rotary shaft 20 is provided with a worm 22 meshed with the worm wheel 31 c. When the second input rotary shaft 20 is rotated by the transmission motor 21 transmitting the rotational force, the worm 22 is also rotated, the worm wheel 31c engaged with the worm 22 is rotated, the extension portion 31b of the holder 31 is rotated according to the rotation of the worm wheel 31c, and finally the holder 31 is rotated.

The sun gear 34 is located at the center of the planetary gear mechanism 30 and has gear teeth along the outer peripheral surface thereof, which are engaged with the gear teeth provided on the outer peripheral surface of the first planetary gears 32 a.

The sun gear 34 is penetrated through the first input rotary shaft 10 at the center, and a bearing is provided between the first input rotary shaft 10 and the sun gear 34 so that the rotational force of the first input rotary shaft 10 does not directly affect the sun gear 34.

A hollow extension portion 34a surrounding the first input rotation shaft 10 is provided at a central portion of the sun gear 34, and an output shaft 40 surrounding the first input rotation shaft 10 is connected to the extension portion 34a of the sun gear 34.

The output shaft 40 is provided on the sun gear 34 to receive the rotational force, and may be integrally formed by extending the extension portion 34a of the sun gear 34, or may be formed by coupling a hollow pipe to the extension portion 34a of the sun gear 34 by means of a spline and a sleeve.

The output shaft 40 is disposed concentrically with the first input rotation shaft 10 because the center portion thereof is penetrated by the first input rotation shaft 10. And the output shaft 40 is disposed on a concentric circle with the carrier 31 and the ring gear 33 and the sun gear 34.

As described above, the second input rotary shaft 20 has the worm 22 on the outer peripheral surface thereof, and the extension 31b of the frame 34 has the worm wheel 31c that is engaged with the worm 22 and rotates, so that the second input rotary shaft 20 and the extension 31b of the frame 33 intersect at a right angle.

The shifting process of the shifting apparatus of fig. 4 constituted as described above will be briefly described.

When the main power source 11 such as a pedal or a drive motor is operated, the first input rotary shaft 10 rotates, and the rotational force of the first input rotary shaft 10 is transmitted to the ring gear 33 and the second planetary gears 32b, the first planetary gears 32a, and the sun gear 34 in this order.

While the variable speed motor 21 is operated and the second input rotation shaft 20 is rotated, the rotation force of the second input rotation shaft 20 is sequentially transmitted to the carrier 31 and the planetary gears 32.

Whereupon the rotational force provided by the main power source 11 and the rotational force provided by the shift motor 21 are combined and shifted and transmitted to the output shaft 40 via the sun gear 34.

The shifting process and the speed increase and decrease of the bicycle shifting device using the shift motor and the planetary gear mechanism of the present invention, which is constituted as described above, will be described with reference to fig. 2 and 4.

First, the acceleration and deceleration effect will be briefly described with reference to fig. 2.

The first input rotary shaft 10 rotates in the same direction and at the same speed as the carrier 31 of the planetary gear mechanism 30. The second input rotation shaft 20 rotates at a reduced speed of the rotation speed of the ring gear 33 as a result of the meshing of the teeth of the worm wheel 33b and the worm 22. That is, the shift motor 21 and the second input rotary shaft are controlled so that the rotational direction and the rotational speed of the ring gear 33 reach the target levels. The output shaft 40 rotates in the same direction and at the same speed as the sun gear 34.

The rotation direction and rotation speed of the first input rotation shaft 10 are thus the rotation direction and rotation speed of the carrier 31, the target rotation direction and rotation speed of the variable speed motor 21 and the second input rotation shaft 20 are the rotation direction and rotation speed of the ring gear 33, and the rotation direction and rotation speed of the output shaft 40 are the rotation direction and rotation speed of the sun gear 34.

First, when the ring gear 33 receiving the rotational force of the change speed motor 21 is fixed in the stopped state of the change speed motor 21, the carrier 31 serves as an input element, and the sun gear 34 serves as an output element, as shown in fig. 2, the fixed speed ratio in the single pinion planetary gear system in which the plurality of pinion gears 32 surround the sun gear 34 in one row is such that the sun gear 34 is increased in speed by (the number of sun gear teeth + the number of ring gear teeth)/the number of sun gear teeth when the carrier 31 rotates once.

If the number of teeth (ZR) of the ring gear 33 is 48 and the number of teeth (ZS) of the sun gear 34 is 16, (ZS + ZR)/ZS = 64/16 =4, the speed is increased by 4 times.

Typically a bicycle rider pedals at 60rpm, assuming that the carrier 31 rotates at 60rpm, the rotational speed of the output shaft 40 and sun gear 34 is 60rpm x (ZS + ZR)/ZS = 240 rpm.

Using the calculation formula, when the carrier 31 is rotated at 50rpm and 70rpm, the rotational directions and rotational speeds of the output shaft 40 and the sun gear 34 are 200rpm and 280rpm, respectively.

Table 1 is the corresponding summary table. Hereinafter, for convenience, the + is set to the clockwise direction, -is set to the counterclockwise direction, and the + sign is omitted.

[ TABLE 1 ]

First input (frame)	50 rpm	60 rpm	70 rpm
				Second input (circle)	0 rpm	0 rpm	0 rpm
Output (Sun)	200 rpm	240 rpm	280 rpm

When the carrier 31 receiving the rotational force of the main power source 11 is fixed, the ring gear 33 connected to the change speed motor 21 and the second input rotary shaft 20 serves as an input element, and the sun gear 34 serves as an output element, the fixed speed ratio in the single pinion planetary gear system is such that the sun gear 34 is reversely rotated by the number of teeth of the ring gear/the number of teeth of the sun gear by the multiple of the number of teeth of the ring gear when the ring gear 33 rotates once.

With a single pinion planetary gear system, the ring gear rotates in the opposite direction to the sun gear. By using the above-mentioned tooth numbers, — ZR/ZS = -48/16 = -3, so the speed increase is reversed by three times.

Table 2 shows the rotational direction and rotational speed of the output shaft 40 and the sun gear 34 when the ring gear 33 connected to the transmission motor 21 and the second input rotary shaft 20 rotates at-10 rpm, 0rpm, and +10rpm, respectively, in the stopped state of the carrier 31 connected to the main power source 11.

[ TABLE 2 ]

First input (frame)	0 rpm	0 rpm	0 rpm
				Second input (circle)	10 rpm	- 0 rpm	+ 10 rpm
Output (Sun)	+ 30 rpm	0 rpm	- 30 rpm

The rotational speed of the first input rotary shaft 10 connected to the main power source 11 and the carrier 31 was constant at 60rpm, and the rotational directions and rotational speeds of the output shaft 40 and the sun gear 34 when the gear 33 connected to the variable speed motor 21 and the second input rotary shaft 20 were rotated at-10 rpm, 0rpm, and +10rpm, respectively, are shown in table 3.

[ TABLE 3 ]

First input (frame)	60 rpm	60 rpm	60 rpm
				Second input (circle)	- 10 rpm	0 rpm	+ 10 rpm
Output (Sun)	270 rpm	240 rpm	210 rpm

As described above, the single pinion planetary gear system structure generates various output rotational speeds according to the difference in the number of teeth between the ring gear and the sun gear, the input/output element, and the like.

When the ring gear 33 connected to the main power source 11 and the first input rotation shaft 10 and the carrier 31 are rotated at a constant speed of 60rpm under the conditions of the ring gear tooth number (ZR) 48 and the sun gear tooth number (ZS) 16, and the variable speed motor 21 and the second input rotation shaft 20 are fixed (0 rpm), the rotation speed of the output shaft 40 and the sun gear 34 is 240 rpm.

When carrier 31 rotates at a constant speed of 60rpm and ring gear 33 rotates at 10rpm in the clockwise direction (+) or counterclockwise direction (-), sun gear 34, which is an output element, decelerates and accelerates at 210rpm and 270rpm, respectively.

Therefore, the speed can be reduced and increased by using the variable speed motor and the single pinion planetary mechanism.

Table 4 shows the rotational speed data of the sun gear 34 as the output element when the element carrier 31 as the first input element rotates at 50rpm, 60rpm, and 70rpm and the rotational speed of the ring gear 33 as the second input element changes from-40 to +40rpm at 10 rpm.

[ TABLE 4 ]

As shown in table 4, when the first input rotary shaft 10 connected to the main power source 11 and the carrier 31 are rotated at a constant speed of 50rpm or 60rpm, and the ring gear 33 connected to the variable speed motor 21 and the second input rotary shaft 20 is rotated in the clockwise direction (+) or the counterclockwise direction (-) at-40 rpm to 40rpm, the rotation number of the sun gear 34 connected to the output shaft 40 can be increased and decreased.

Table 4 shows the result of setting the rotational speed interval of the ring gear 33 connected to the shift motor 21 and the second input rotary shaft 20 to 10rpm, and the shift speed number is 9. When the rotation speed of the ring gear 33 is set to 5rpm, the number of shift stages is 17. Thus, various gear structures can be realized by the present invention.

As shown in fig. 2, in the single pinion planetary gear system, when the carrier 31 is used as the first input element connected to the main power source 11 and the ring gear 33 connected to the change speed motor 21 is used as the second input element, the rotational speed of the sun gear 34 as the output element is increased and decreased by a combination of an increase rate of [ sun gear tooth number (ZS) + ring gear tooth number (ZR) ]/sun gear tooth number (ZS) and a reverse increase rate of-ZR/ZS as shown in table 4. The ring gear tooth number (ZR) and the sun gear tooth number (ZS) can be adjusted.

The acceleration and deceleration effect will be briefly described with reference to fig. 4.

The first input rotary shaft 10 rotates in the same direction and at the same speed as the ring gear 33 of the planetary gear mechanism 30. The second input rotation shaft 20 rotates at a reduced speed as a result of the sum of the teeth of the worm wheel 31c and the worm 22, and the rotation speed of the carrier 31. That is, the variable speed motor 11 and the second input rotary shaft 10 are controlled so that the rotational direction and the rotational speed of the carrier 31 reach the target levels. The output shaft 40 rotates in the same direction and speed as the sun gear 34.

The rotational direction and rotational speed of the first input rotary shaft 10 are thus the rotational direction and rotational speed of the ring gear 33, the target rotational direction and rotational speed of the shift motor 21 and the second input rotary shaft 20 are the rotational direction and rotational speed of the carrier 31, and the rotational direction and rotational speed of the output shaft 40 are the rotational direction and rotational speed of the sun gear 34.

First, when the ring gear 31 receiving the rotational force of the change speed motor 21 is fixed in the stopped state of the change speed motor 21, the ring gear 33 serves as an input element, and the sun gear 34 serves as an output element, as shown in fig. 4, the fixed speed ratio in the double pinion planetary gear system in which the plurality of pinion gears 32 are arranged in two rows around the sun gear 34 is such that the sun gear 34 is increased in speed by the number of teeth of the ring gear/the number of teeth of the sun gear when the ring gear 33 rotates by 1.

If the number of teeth (ZR) of the ring gear 33 is 48 and the number of teeth (ZS) of the sun gear 34 is 12, the speed increase is 4 times as large as the number of teeth (ZR)/the number of teeth (ZS) =48/12 = 4.

Typically a bicycle rider pedals at 60rpm, assuming that the ring gear 33 rotates at 60rpm, the rotational speed of the output shaft 40 and sun gear 34 is 60rpm x (ZS + ZR)/ZS = 240 rpm.

Using the calculation formula, when the ring gear 33 rotates at 50rpm and 70rpm, the rotational directions and rotational speeds of the output shaft 40 and the sun gear 34 are 200rpm and 280rpm, respectively.

Table 5 is the corresponding summary table. Hereinafter, for convenience, the + is set to the clockwise direction, -is set to the counterclockwise direction, and the + sign is omitted.

[ TABLE 5 ]

First input (frame)	50 rpm	60 rpm	70 rpm
				Second input (circle)	0 rpm	0 rpm	0 rpm
Output (Sun)	200 rpm	240 rpm	280 rpm

When the carrier 31 connected to the change-speed motor 21 and the second input rotary shaft 20 is fixed, the sun gear 34 functions as an output element, and the fixed speed ratio in the double pinion planetary gear system is such that the sun gear 34 is reversed and accelerated by a factor of [ sun gear tooth number (ZS) -ring gear tooth number (ZR) ]/sun gear tooth number (ZS) when the carrier 31 rotates 1.

Under the double pinion planetary gear system, the direction of rotation of the ring gear is the same as the direction of rotation of the sun gear. The above-mentioned tooth numbers, (ZS-ZR)/ZS = (12-48)/12) = -3 are applied, so the speed increase is reversed by three times.

Table 6 shows the rotational directions and rotational speeds of the output shaft 40 and the sun gear 34 when the carrier 31 connected to the transmission motor 21 and the second input rotary shaft 20 is rotated at-10 rpm, 0rpm, and +10rpm, respectively, in the state where the carrier 33 connected to the main power source 11 is stopped.

[ TABLE 6 ]

First input (frame)	0 rpm	0 rpm	0 rpm
				Second input (circle)	- 10 rpm	0 rpm	+ 10 rpm
Output (Sun)	+ 30 rp	0 rpm	- 30 rpm

The rotational speeds of the first input rotary shaft 10 and the ring gear 33 connected to the main power source 11 were 60rpm and were constant, and the rotational directions and rotational speeds of the output shaft 40 and the sun gear 34 when the carrier 31 connected to the variable speed motor 21 and the second input rotary shaft 20 were rotated at-10 rpm, 0rpm, and +10rpm, respectively, are shown in table 7.

[ TABLE 7 ]

First input (frame)	60 rpm	60 rpm	60 rpm
				Second input (circle)	- 10 rpm	0 rpm	+ 10 rpm
Output (Sun)	270 rpm	240 rpm	210 rpm

As described above, the double pinion planetary gear system structure generates various output rotational speeds according to the difference in the number of teeth between the ring gear and the sun gear, the input/output element, and the like.

When the carrier 31 connected to the main power source 11 and the first input rotation shaft 10 and the ring gear 33 is fixed (0 rpm) and the speed of the output shaft 40 and the sun gear 34 is 240rpm, the carrier is connected to the variable speed motor 21 and the second input rotation shaft 20, and the number of teeth of the ring gear (ZR) 48 and the number of teeth of the sun gear (ZS) 12 are set to rotate at a constant speed of 60 rpm.

When ring gear 33 rotates at a constant speed of 60rpm and carrier 31 rotates at 10rpm in the clockwise direction (+) or counterclockwise direction (-), sun gear 34, which is an output element, decelerates and accelerates at 210rpm and 270rpm, respectively.

Therefore, the speed can be reduced and increased by using the variable speed motor and the double-pinion planetary mechanism.

Table 8 shows the rotational speed data of the sun gear 34 as the output element when the ring gear 33 as the first input element rotates at 50rpm, 60rpm, and 70rpm, and the rotational speed of the carrier 31 as the second input element changes from-40 to +40rpm at 10 rpm.

[ TABLE 8 ]

As shown in table 8, when the first input rotary shaft 10 and the ring gear 33 connected to the main power source 11 were rotated at a constant speed of 50rpm or 60rpm, and the carrier 31 connected to the variable speed motor 21 and the second input rotary shaft 20 was rotated in the clockwise direction (+) or the counterclockwise direction (-) at-40 rpm to 40rpm, the number of rotations of the sun gear 34 connected to the output shaft 40 was increased and decreased.

Table 8 shows the result of setting the rotational speed interval of the carrier 31 connected to the shift motor 21 and the second input rotary shaft 20 to 10rpm, and the number of shift stages is 9 stages. When the rotational speed of the carrier 31 is set to 5rpm, the number of shift stages is 17. Thus, various gear structures can be realized by the present invention.

As shown in fig. 4, in the double pinion planetary gear system, when the ring gear 33 is used as the first input element connected to the main power source 11 and the carrier 31 connected to the change speed motor 21 is used as the second input element, the rotational speed of the sun gear 34 as the output element is increased and decreased by the combination of the speed increase [ ring gear tooth number (ZR)/sun gear tooth number (ZS) ] and the reverse speed increase [ sun gear tooth number (ZS) -ring gear tooth number (ZR) ]/sun gear tooth number (ZS) ] as shown in table 8. The ring gear tooth number (ZR) and the sun gear tooth number (ZS) can be adjusted.

In the past, a single-gear bicycle in which one front Sprocket (Sprocket) and one rear Sprocket (Sprocket) are provided was manufactured in such a manner that the rear wheel rotates 3 when the pedals 1 rotate 1. The present invention is applied to a bicycle in which a plurality of sprockets of a thick rear spindle roller, a front and rear transmission, a rear shift lever, and the like are not required, and a single-gear bicycle in which the number of teeth of the front and rear sprockets (sprockets) is identical and multi-speed increase and decrease are easy can be manufactured.

The preferred embodiments have been described above with reference to the accompanying drawings, but the invention is not limited to the specific embodiments described above; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: modifications may still be made to the solutions described in the foregoing embodiments without departing from the scope of the solutions described in the embodiments of the present invention.