JPH07205874A - Gear shifter for bicycle - Google Patents

Abstract

PURPOSE:To provide the compact rear wheel drive type gear shifter for a bicycle, which is excellent in durability, and enables gear shifting to be simply and surely actuated. CONSTITUTION:A gear case 4 concurrently acting as a hanger is provided for the hanger section of a bicycle frame. A carrier 34 is fixed on a crank shaft 30 penetrating through the gear case, and a plurality of planet gears 35 on each of which a gear 35a, a gear 35b and a gear 35c different in the number of teeth respectively are integrally formed, are rotatably mounted over the same circumference of the carrier 34. A driven rotor 61 which combines a sun gear 60 with a bevel gear 35 so as to be integrally formed, is provided in the inner side of each planet gear 35 in such a way as to be meshed with one of the aforesaid planet gears 35, and a plurality of annuluses 39, 40 and 41 which are meshed with the planet gears 35a, 35b and 35c respectively are independently and rotatably set in parallel in the outer side of each planet gear 35. An one-way clutch C1 is interposed in each space between each annulus 39, 40 and 41 and the gear case 4 respectively, and one of these one-way clutches is so constituted as to be selectively connected therewith.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a bicycle gearbox with a planetary gear mechanism provided on a crankshaft portion of a bicycle, and more particularly to a shaft drive type transmission of the crankshaft portion from a transmission to a rear wheel. It is the one.

[0002]

2. Description of the Related Art A bicycle transmission that is widely used at present is a so-called external transmission in which a chain spanned between multiple sprockets is replaced by a derailleur. In addition to this, there is a so-called internal transmission in which a transmission mechanism is built in the hub of the rear wheels, but it is not widely used. Further, as a transmission in which a planetary gear mechanism is incorporated in the crankshaft, for example, Japanese Patent Laid-Open No. 62-992 previously proposed by the applicant of the present application.
There is one disclosed in Japanese Patent Application Laid-Open No. 93-93, and JP-A 1-2
There is also proposed a system combining a planetary gear mechanism and an external transmission as disclosed in Japanese Patent No. 66089 and Japanese Utility Model Laid-Open No. 50-26547. Further, as a shaft drive type, there is also a bicycle transmission device disclosed in Japanese Patent Laid-Open No. 4-176788.

[0003]

DISCLOSURE OF THE INVENTION The present invention is described in the above-mentioned Japanese Patent Application Laid-Open No.
The present invention relates to a transmission in which a planetary gear mechanism is incorporated in a crankshaft portion like the transmission of No. 2-99293, and an object thereof is to solve the problems of the conventional device and to provide a better transmission. Is. That is, unlike the generally used multi-stage external transmission, the transmission of the above-mentioned Japanese Patent Laid-Open No. 62-99293 proposed by the present applicant is different from the conventional transmission.
Since power is transmitted by a linear transmission path that is orthogonal to the crankshaft at any of the gears, the chain or sprocket does not apply excessive force, and it is a highly efficient and durable bicycle transmission that can be used by users. Are provided to.

However, the above-mentioned Japanese Patent Laid-Open No. 62-99.
It has been found that the conventional devices disclosed in Japanese Patent Laid-Open No. 293 and Japanese Patent Laid-Open No. 4-176788 have the following drawbacks. That is,
Since the one-way clutch for gear shifting in the device is configured to be provided on the inner peripheral portion of the sun gear, the lever ratio to the crank arm is large because the distance from the axis is very short, and as a result, the pedaling force on the pedal is increased. However, since a large load is applied to these one-way clutches, there is a problem that the durability of the ratchet, the claws, etc. that make up the one-way clutch is impaired, and the gear shifting operation is performed while the pedal force is applied. It turns out that the gear shifting operation becomes heavy in some cases. Further, in terms of structure, the device has a large outer shape in order to obtain a gear ratio suitable for traveling of a bicycle, and there is room for improvement in terms of weight and appearance.

Further, it is proposed in Japanese Patent Application Laid-Open No. 1-266089 and Japanese Utility Model Laid-Open No. 50-26547 (the former shows two sprockets, but the latter does not show the speed changing method). Such a mechanism, that is, a mechanism having multiple rows of sprockets on the output side of the planetary speed increasing mechanism and changing gears by changing chains by an external transmission (derailleur) requires an external transmission or a plurality of external transmissions. Since it is necessary to install the sprocket, the increase in weight and the increase in cost have been caused. In addition, since these devices have a structure in which the chain is slid over, there is a problem that the chain and sprocket are twisted, and in addition, the planetary gear has a cantilever structure, which reduces efficiency and durability. I was invited.

Further, Japanese Patent Laid-Open No. 62-9 proposed by the present applicant.
In a structure in which a transmission incorporating a planetary mechanism and a sprocket are concentrated on one side like the device of 9293, the width of the transmission becomes thicker as the number of gear stages is increased, and as a result, the crankshaft is increased. Becomes longer, the mounting position of the crank protrudes outward, and when the pedal force is applied to the pedal,
It has been found that there is a problem that the crankshaft bends and the gear is twisted, resulting in reduced efficiency.

[0007]

In order to solve the above-mentioned problems, in the present invention, a gear case which also serves as a hanger is provided on the hanger portion of the bicycle frame, and a carrier is provided on a crankshaft rotatably supported through the gear case. , And a plurality of planetary gears integrally formed with gears with different numbers of teeth are rotatably mounted on the same circumference of this carrier, and the sun gear and bevel gear are placed inside these planetary gears. A driven rotary body integrally formed by coupling is provided so as to mesh with one of the planetary gears, and a plurality of internal gears respectively meshing with the planetary gears are independently rotated outside the planetary gears. The bicycle transmission is arranged so as to be freely arranged, and one-way clutches are respectively interposed between the internal gear and the gear case so that one of these one-way clutches can be selectively connected. It is formed.

Further, as the above-mentioned one-way clutch, the ratchet teeth are engraved on the outer circumference of each of the internal gears, and the gear case has a pawl rotatably mounted on the gear case in association with the ratchet teeth. The cam is rotated by operating the operating wire so that one of the pawls can be selectively engaged with one of the ratchet teeth.

A one-way clutch may be provided between the crankshaft portion of the above-described bicycle transmission and the driven rotating body.

As the above-mentioned one-way clutch, ratchet teeth are engraved on the inner circumference of the driven rotating body, and a claw barrel is fixedly provided on the outer circumference of the crankshaft, so that the driven rotating body and the claw barrel are connected to each other. A pawl may be rotatably disposed between the pawls and the pawl may be engaged with the ratchet by a spring.

Further, a one-way clutch may be provided between the carrier fixed to the crankshaft of the above-mentioned bicycle transmission and the driven rotating body.

As the above-mentioned one-way clutch, ratchet teeth are engraved on the outer periphery of the driven rotor, and a pawl is rotatably disposed on the inner periphery of the carrier facing the ratchet teeth.
The pawl may be engaged with the ratchet by a spring.

[0013]

As described above, the device of the present invention is provided with a gear case which also serves as a hanger in the hanger portion of the bicycle frame, and the planetary speed change mechanism is incorporated in this gear case. ), And since the width of both support points that support this planetary speed change mechanism is wide, the gear and sprocket can rotate smoothly even if the pedal force is applied, and the external shape of the device itself. By suppressing the size to be small, it is possible to provide a lightweight and robust bicycle transmission that is suitable for mass production.

Further, in the device of the present invention, the force is transmitted by the linear transmission path which is orthogonal to the crankshaft at any of the shift stages, and moreover, since it has a double-supported structure, the transmission efficiency of each gear is excellent. Moreover, the structure is reasonably strong and has excellent durability. In addition, as a result of the structure that a one-way clutch for speed change is provided on the outer peripheral part of the device, the distance from the shaft center to the one-way clutch becomes longer, so the torque due to the pedaling force applied to the one-way clutch becomes smaller. In addition to improving the durability of the ratchet and the claws that make up the vehicle, the gear shifting operation becomes lighter when the pedal force is applied.

Further, the device of the present invention does not require an external transmission for replacing a plurality of sprockets or chains with the external transmission, which has been frequently used in the prior art, so that the cost and weight can be suppressed. Further, since the one-way clutch can be selected and the gear shifting operation can be performed only by operating the gear shifting operation lever and pulling or returning the operating wire, the gear shifting operation can be performed easily and reliably.

Further, if a one-way clutch is provided between the crankshaft portion and the driven rotary member or between the carrier fixed to the crankshaft and the driven rotary member, when the speed change pawl is broken, it suddenly spins. There is no risk of accidents.

[0017]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to the drawings. In the figure, 1 (see FIGS. 3, 4, 5 and 7) is a main pipe of the bicycle frame, 2 is a vertical pipe, 3 is a chain stay,
Reference numeral 4 denotes a gear case that also serves as a hanger provided on the hanger portion of the bicycle frame. The gear case 4 is formed by a case body 4a and a case lid 4b, and 4c, 4d, are flange portions projecting from the outer peripheral portions of the upper portions of the case body 4a and the case lid 4b, respectively, and 5 is the flanges. Section 4c,
It is an intermediate body sandwiched between 4d, and this intermediate body has two boss portions 5a and 5b. The main pipe 1 and the standing pipe 2 are fitted and connected to these boss portions 5a and 5b, respectively. There is. 6 is a bolt for fastening the flanges 4c, 4d and the intermediate body 5.

As shown in FIGS. 1 and 2, the case body 4a
A stay connecting portion 4e is provided on the rear part of the rear portion, and the chain stay 3 is applied to the connecting portion 4e and fixed by a bolt 7. Reference numeral 8 is a filler inserted in the chain stay 3. Further, 4f is a boss portion formed on the rear portion of the case lid 4b, and a bevel gear 9 is rotatably provided in the boss portion 4f via two bearings 10. 11 is a transmission shaft fitted with a bevel gear 9, 12 and 13 are bearings
Distance collar inserted between 10, 10, 14 is boss 4f
Reference numeral 15 is a pipe that encloses the transmission shaft 11.

Reference numeral 16 in FIG. 1 denotes a tire for the rear wheel of the bicycle, 17
Is a rim, 18 is a spoke, 19 is a hub, 20 is a rear axle that penetrates through the center of the hub 19, and is a claw 3a at the rear of the chain stay 3.
Is fastened to one end of the rear axle 20 by a nut 21, and a rear gear case 22 is fastened to the other end of the rear axle 20 by a nut 21.

Reference numeral 23 is a bevel gear for transmitting power to the hub 19, and the hub 19 may be provided with the above-mentioned internal transmission. 22a is a boss portion of the gear case 22, 24 is a bevel gear that meshes with the bevel gear 23, 25, 25 are bearings that support the bevel gear 24, 26,
27 is the distance collar between the bearings 25 and 25, 28 is the boss 22
a is a lid, 15 is a pipe fitted with the lid 28, 11 is a transmission shaft fitted in and fixed to the bevel gear 24 in the pipe 15, and 29 is between the bevel gear 23 and the gear case 22. It is the inserted covering.

Reference numeral 30 is a crankshaft which penetrates the center of the gear case 4, 31 is a hanger-one type bearing provided between the crankshaft 30 and the case body 4a, and 32 is between the crankshaft 30 and the case lid 4b. Ball bearing type bearings installed in
Are crank arms connected to both ends of the crankshaft 30.

1 to 7 show a first embodiment of the present invention. In this embodiment, a substantially disk-shaped carrier 34 is attached to a crankshaft in a case body 4a and a shaft cylinder of the bearing 31. Part 31
Stick through a. As shown in FIG.
As shown in Fig. 3, three recessed portions 34a are formed at equal circumferential positions, and a plurality of gears 35a, 35b, 35c having different numbers of teeth (three in this embodiment) are integrally formed. The three planetary gears 35 are inserted into the respective recessed portions 34a described above and are rotatably supported by the shaft 34 with respect to the carrier 34.
Further, 37 is a ring-shaped shaft support plate provided to support the right end of the shaft 36, and 38 is a bolt for fixing the shaft support plate 37 to the carrier 34.

Further, each gear 35a, 35b, of the planetary gear 35 is
An internal gear 39, 40, 41 having internal teeth on its inner circumference and engraved ratchet teeth on its outer circumference between 35c and the gear case 4.
Are provided for meshing with the planetary gears 35a, 35b, 35c, respectively. A one-way clutch C ₁ is interposed between the gear case 4 and the internal gears 39, 40, 41, respectively.

That is, 39a, 40a, 41a are the internal gears 39,
Inner teeth formed on the inner circumferences of 40 and 41, and 39b, 40b and 41b are ratchet teeth formed on the outer circumferences of the internal gears 39, 40 and 41.
In addition, the case body 4a of the gear case 4 has a substantially box-shaped protrusion.
4g, and the ratchet teeth 39b, 40
b, 41b respectively corresponding pawls 42, 43, 44 are rotatably provided by a shaft 45, and these pawls 42, 43, 44 are urged to engage the corresponding ratchet teeth 39b, 40b, 41b respectively. The spring 46 (see Fig. 4) to one side of each claw and the protrusion 4g of the case.
, And three cams 47, 48, 49 that come into contact with the other side of each pawl are fixed to the shaft 50 penetrating the protrusion 4g with their phases shifted from each other, as shown in FIG. A lever 51 is fixed to the outward protruding portion of the shaft 50, and an operation wire 53 (see FIG. 4) is connected to a free end portion of the lever 51 via a pin 52.
Reference numeral 54 (see FIG. 3) is a return spring of the lever 51 fitted to the shaft 50, 55 is a cover plate of the protrusion 4g of the case, and 56 is interposed between the internal gear 39 and the inner surface of the case lid 4b. It is a distance ring.

Further, a bevel gear 57 meshing with the bevel gear 9 and a shaft cylinder 57a are integrally formed on the crankshaft 30 in the case lid 4b, and are fitted to the ball bearing type bearing 58 and the shaft cylinder 57a. 3 is provided rotatably via the bush 59, and the inner peripheral portion 60a at the right end in FIG. 3 of the ring-shaped sun gear 60 meshing with the planetary gear 35a is provided with a spline 57b provided at the end of the shaft cylinder 57a. By fitting, the sun gear 60 and the bevel gear 57 are integrally formed as a driven rotary body 61.

Further, the sun gear 60 integrated with the driven rotor 61.
The ratchet teeth 60b (see FIG. 4) are engraved on the inner peripheral portion of the inner end of the claw barrel 62, and the claw barrel 62 is fixed to the outer periphery of the crankshaft 30 with screws. In this embodiment, two bases 63a of the claws 63 are rotatably pivoted, and the free ends of the claws 63 are engaged with the ratchet teeth 60b by springs (not shown). Configure directional clutch C ₂ . Reference numeral 64 is a distance collar fitted to the crankshaft 30 between the carrier 34 and the claw barrel 62.

FIG. 8 shows another embodiment. In the figure, the same reference numerals as those used in the previous figures denote the same elements. Difference from the first embodiment of this example, in the configuration of the clutch C _2, the clutch C ₂ In this embodiment, the inner peripheral portion of the carrier 34 and the shaft support plate 37 that is integrally coupled, a driven rotary It is provided between the body 61 and the outer peripheral portion of the shaft cylindrical portion of the sun gear 60 that is integrally connected. That is, the ratchet teeth 37a are formed on the inner peripheral portion of the shaft support plate 37.
And the base portions 63a of a plurality of (two in this embodiment) claws 63 are rotatably pivotally attached to the outer peripheral portion of the shaft portion of the sun gear 60. The one-way clutch C ₂ is configured so that each is connected to the ratchet teeth 37a by a spring (not shown).

FIG. 9 shows still another embodiment, in which the planetary gear 35 of the device of the first embodiment is formed by two planetary gears 35a and 35b by shifting the planetary gear 35 by one. Also has two gears 39, 40 and two claws 42, 43
The corresponding cam is also composed of two cams 47 and 48, and the number of gears is one less than that of the first embodiment, but the structure is simple. Since other configurations are similar to those of the first embodiment, the same components are designated by the same reference numerals and the description thereof will be omitted.

Further, FIG. 10 shows an embodiment in which only the clutch C ₂ is removed from the device of FIG. 9, and the same reference numerals as those used in the drawing denote the same components. With the structure of this embodiment, the number of gears is further reduced by one compared with the embodiment of FIG. 9, but the structure is simplified because the clutch C ₂ is eliminated.

Next, the operation of the device of the present invention configured as described above will be described. First, in the first embodiment of FIGS. 1 to 7, a gear shift operating device (not shown) is operated to operate the operation wire.
When 53 is pulled in the direction of arrow A in FIG. 4 to the maximum extent, the relationship between the claw and the ratchet tooth becomes the state shown in FIG. 11 (a). That is, in this case, the pawls 42, 43, 44 are all disengaged from the ratchet teeth 39b, 40b, 41b by the cams 47, 48, 49. Therefore, in this case, only the one-way clutch C ₂ between the driven rotary body 61 and the crankshaft 30 is connected. See also FIG.
In the case of the one described above, a one-way clutch C ₂ between the driven rotor 61 and the ring-shaped bearing plate 37 integrally connected to the carrier 34 is used.
Only connected.

In this state, when the crank arm 33 is rotated in the direction of arrow B in FIG.
30, the driven rotor 61 rotates in the direction of arrow B via the one-way clutch C ₂ , and the bevel gear 57 rotates in the same direction. Therefore, the bevel gear 9, the transmission shaft 11, the bevel gears 24, 23 (Fig. The rear wheel rotates via (1) and the bicycle runs. In this case, the rotation ratio between the crankshaft 30 and the bevel gear 57 is 1: 1 which is a so-called low state.

In the embodiment shown in FIG. 8, the rotation of the crankshaft 30 is transmitted to the carrier 34, the shaft 36, and the ring-shaped shaft support plate 37, and between the shaft support plate 37 and the sun gear 60 of the driven rotor 61. 1: 1 rotation is transmitted to the bevel gear 57 via the one-way clutch C ₂ provided in the. Therefore, the operation is the same in both embodiments.

Next, when the operating wire 53 is loosened further in the direction of arrow C from the state shown in FIG. 11 (a), the relationship between the pawl and the ratchet tooth becomes the state shown in FIG. 11 (b). That is, in this case, the pawl 44 is engaged with the ratchet teeth 41b by the rotation of the cam 49, and the one-way clutch C ₁ is engaged. Therefore, the internal gear 41
And the gear case 4 are connected.

In this state, when the crank arm 33 is rotated in the direction of arrow B in FIG. 4, the crank shaft 30 and the planet carrier are
The planetary gear 35 revolves in the direction of arrow D in FIG. 4 via the shaft 34 and the shaft 36. In this case, however, the internal gear 41 is prevented from rotating in the direction of arrow D by the one-way clutch C ₁ . The planetary gear 35c meshing with the tooth gear 41 rotates in the direction of arrow E. However, since the planetary gears 35a, 35b, 35c are integrally formed, rotation of the planetary gear 35 causes the internal gears to rotate.
39 and 40 rotate in the direction of arrow F, but in this case the internal gear
Since the one-way clutch C ₁ between the gears 39 and 40 and the gear case 4 is not connected, the internal gears 39 and 40 only idle. That is, the rotation of the planetary gear 35 is determined by the gear 35c. Therefore, the sun gear 60 meshed with the planetary gear 35a integrally formed with the planetary gear 35c and the bevel gear 57 integral with the sun gear 60 are accelerated in the direction of arrow G to rotate. The speed increasing ratio in this embodiment is 1.87.

When the operating wire 53 is further loosened in the direction of arrow H from the state shown in FIG. 11 (b), the relationship between the pawl and the ratchet tooth becomes the state shown in FIG. 11 (c). That is, in this case, the pawl 43 moves the ratchet teeth 40b by the rotation of the cam 48.
To engage the one-way clutch C ₁ . Therefore, the internal gear 40 and the gear case 4 are connected.

When the crank arm 33 is rotated in the direction of arrow B in FIG. 4 in this state, the crank shaft is rotated in the same manner as in the previous case.
The planetary gear 35 revolves in the direction of arrow D in FIG. 4 via 30, the planet carrier 34, and the shaft 36. In this case, the internal gear 40 is prevented from rotating in the direction of arrow D by the one-way clutch C ₁ . Therefore, the planetary gear 35b meshing with the internal gear 40 rotates in the direction of arrow E. However, the planetary gears 35a, 35b,
Since 35c is integrally formed, the internal gear 39 is indicated by the arrow F.
The internal gear 41 rotates in the direction opposite to the arrow F, but the one-way clutch C ₁ between the internal gear 39, 41 and the gear case 4 is not connected, so the internal gear 39, 41 rotates. 41 only idles. That is, in this case, the rotation of the planetary gear 35 is determined by the gear 35b. Therefore, the sun gear 60 meshing with the planetary gear 35a and the bevel gear 57 integrated with the sun gear 60 rotate in the direction of arrow G at a speed further increased than the previous time. The speed increasing ratio in this embodiment is 2.2.

When the operating wire 53 is further loosened in the direction of arrow I from the state shown in FIG. 11 (c), the relationship between the pawl and the ratchet tooth becomes the state shown in FIG. 11 (d). That is, in this case, the pawl 42 is rotated by the cam 47 to cause the ratchet teeth 39b to move.
To engage the one-way clutch C ₁ . Therefore, the rotation of the internal gear 39 in the arrow J direction is prevented.

When the crank arm 33 is rotated in the direction of arrow B in FIG. 4 in this state, the crank shaft is rotated in the same manner as in the previous case.
The planetary gear 35 revolves in the direction of arrow D in FIG. 4 via 30, the planet carrier 34, and the shaft 36. In this case, the internal gear 39 is prevented from rotating in the direction of arrow D by the one-way clutch C ₁ . Therefore, the planetary gear 35a meshing with the internal gear 39 rotates in the direction of arrow E. However, the planetary gears 35a, 35b,
Since 35c is integrally formed, the internal gears 40, 41 can be rotated in the direction opposite to the arrow F, but the one-way clutch C ₁ between the internal gears 40, 41 and the gear case 4 is not connected. Since there are no internal gears 40 and 41, they only idle. That is, in this case, the rotation of the planetary gear 35 is determined by the gear 35a. Therefore, the sun gear 60 meshed with the planetary gear 35a and the bevel gear 57 integrated with the sun gear 60 rotate in the direction of arrow G at a speed further increased than the previous time. This state is the so-called top state, and the speed increasing ratio in this embodiment is 2.6.

On the contrary, when decelerating, use the operation wire 53 as shown in FIG.
(d) Pull in the direction of arrow K. That is, in FIG.
You can operate like (d) → (c) → (b) → (a). The operation of the embodiment shown in FIG. 8 is the same as that of the first embodiment described above. However, since the clutch C ₂ of the embodiment shown in FIG. 8 has a larger transmission radius than the clutch C ₂ of the first embodiment, the strength of the transmission system can be easily increased correspondingly.

Further, in the embodiment shown in FIG. 9, the number of shift gear trains is one less than that of the device of the first embodiment described above, and therefore the number of gears is reduced by one. That is, the first embodiment has a four-speed shift, while the device of FIG. 9 has a three-speed shift. Further, the embodiment of FIG. 10 is a device capable of two-speed gear shift without the 1: 1 gear shift stage since the clutch C ₂ of the device of FIG. 9 is removed. Since the operation is similar to that of the first embodiment, the description will be omitted.

[0041]

As described above, the device of the present invention is provided with the gear case 4 also serving as a hanger on the hanger portion of the bicycle frame,
Since the planetary speed change mechanism is incorporated in this gear case 4,
The planetary speed change mechanism can be arranged at both ends (center part) of the crankshaft 30, and the width of both supporting points for supporting the planetary speed change mechanism is wide, so that even if the pedal force is applied to the gear and the follower. Since the rotating body 61 can rotate smoothly and the outer shape of the device itself is kept small, it is possible to provide a lightweight and robust bicycle transmission device suitable for mass production.

Further, in the device of the present invention, the force is transmitted by the linear transmission path which is orthogonal to the crankshaft 30 at any of the shift speeds, and moreover, since it has a double-supported structure, the transmission efficiency of each gear is excellent. In addition, the structure is reasonably strong and has excellent durability. In addition, as a result of the structure in which the one-way clutch C ₁ for shifting is provided on the outer peripheral portion of the device
Since the distance of the axis to the heart one-way clutch C ₁ becomes farther, the torque is reduced by depressing force applied to the one-way clutch C _1, the durability of the ratchet and pawl Thus constituting the one-way clutch C ₁ is As a result, it is possible to obtain an effect that the shift operation is lightened while the pedaling force is applied while being improved.

Further, the apparatus of the present invention does not require an external transmission for replacing a plurality of sprockets or chains with the external transmission, which has been frequently used in the prior art, so that the cost and weight can be suppressed. Further, since the one-way clutch C ₁ can be selected and the gear shifting operation can be performed only by operating the gear shifting operating lever and pulling or returning the operating wire 53, the gear shifting operation can be performed easily and reliably. The effect is obtained.

Between the crankshaft 30 and the driven rotary member 61,
Alternatively, the carrier 34 fixed to the crankshaft 30 and the driven rotating body
If a one-way clutch C ₂ is provided between the gear 61 and 61, there is no danger of accidental idling when the speed change pawl is broken, and there is an effect of being safe.

[Brief description of drawings]

FIG. 1 is a plan sectional view showing a transmission system for a crankshaft and a rear wheel of a bicycle equipped with the device of the present invention.

FIG. 2 is a plan sectional view of the crankshaft portion of FIG.

FIG. 3 is a vertical sectional view of the device of the present invention.

FIG. 4 is a sectional view taken along line MM in FIG.

FIG. 5 is a perspective view of three cams having different phases.

6 is an external view of the device of FIG.

FIG. 7 is an external view of the back surface of the device of FIG.

8 is a vertical cross-sectional view showing another embodiment corresponding to FIG.

FIG. 9 is a vertical sectional view showing another embodiment of the present invention.

FIG. 10 is a vertical cross-sectional view showing still another embodiment.

11 (a), (b), (c) and (d) are operation state diagrams of the one-way clutch.

[Explanation of symbols]

1 Main pipe 2 Stand pipe 3 Chain stay 4 Gear case 4a Case body 4b Case lid 4c, 4d Flange part 4e Stay connecting part 4f Boss part 4g Projection part 5 Intermediate body 6,7 Bolt 8 Filler material 9 Bevel gear 10 Bearing 11 Transmission shaft 12, 13 Distance collar 14 Lid 15 Pipe 16 Tire 17 Rim 18 Spoke 19 Hub 20 Rear axle 21 Nut 22 Rear gear case 23, 24 Bevel gear 25 Bearing 26, 27 Distance collar 28 Lid 29 Cover ring 30 Crankshaft 31, 32 Bearing 33 Crank arm 34 Carrier 35, 35a, 35b, 35c Planetary gear 36 Shaft 37 Shaft bearing plate 38 Bolt 39, 40, 41 Internal gear 39a, 40a, 41a Internal tooth 39b, 40b, 41b Ratchet tooth 42, 43, 44 Pawl 45 Axis 46 Spring 47, 48, 49 Cam 50 Axis 51 Lever 52 Pin 53 Operating wire 54 Return spring 55 Cover plate 56 Distance ring 57 Bevel gear 58 Bearing 59 Bush 60 Sun gear 61 Driven rotor 62 Claw Copper 63 Claw 6 4 Distance collar C ₁ , C ₂ Clutch

Claims (6)

[Claims] 1. A bicycle frame is provided with a gear case also serving as a hanger on a hanger portion of the bicycle frame, a carrier is fixed to a crank shaft rotatably supported by penetrating the gear case, and the number of teeth is set on the same circumference of the carrier. A plurality of planetary gears integrally formed with different gears are rotatably attached to the inside of the planetary gears, and a driven rotor integrally formed by coupling a sun gear and a bevel gear is formed inside the planetary gears. And a plurality of internal gears respectively meshing with the planetary gears are rotatably and independently arranged side by side on the outside of the planetary gears, and are arranged in one direction between the internal gears and the gear case. A bicycle transmission characterized in that one of these one-way clutches can be selectively connected through a clutch. 2. The one-way clutch according to claim 1,
By engraving the ratchet teeth on the outer circumference of each of the internal gears, the gear case is provided with a pawl that interlocks with a cam corresponding to each of the ratchet teeth and is rotatably attached to the gear case by operating an operation wire. A bicycle transmission characterized in that one of the pawls is selectively engageable with one of the ratchet teeth by rotating the cam. 3. A bicycle transmission according to claim 1, further comprising a one-way clutch provided between the crankshaft portion and the driven rotating body. 4. The one-way clutch according to claim 3,
Ratchet teeth are engraved on the inner circumference of the driven rotating body, and a claw barrel is fixedly provided on the outer circumference of the crankshaft, and a claw is rotatably disposed between the driven rotating body and the claw barrel. A bicycle transmission characterized in that the pawl is engaged with the ratchet by a spring. 5. A bicycle transmission according to claim 1, further comprising a one-way clutch provided between the carrier fixed to the crankshaft and the driven rotating body. 6. The one-way clutch according to claim 5,
The ratchet teeth are engraved on the outer periphery of the driven rotating body, and a pawl is rotatably disposed on the inner periphery of the carrier facing the ratchet tooth, and the pawl is engaged with the ratchet by a spring. And bicycle transmission.