JPH0319116B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a speed change operation device for changing the speed ratio of a bicycle transmission.

(Prior Art) Conventional transmissions are operated by a push-pull method using one wire, or by a method in which a wire reel is rotated using two wires.

(Problems to be Solved by the Invention) However, depending on the type of transmission device, it may be difficult to perform a speed change operation using the conventional speed change operation device described above.

SUMMARY OF THE INVENTION An object of the present invention is to provide a bicycle speed change operation device suitable for a type of speed change device in which it is difficult to perform a speed change operation using such a conventional speed change operation device.

(Means for solving the problem) In order to achieve the above-mentioned object, in the present invention,
A lever body formed integrally with the lever is rotatably provided on the bicycle frame, and the rotation of the lever body is accelerated and taken out by a gear speed increasing device including a planetary gear device. A bicycle speed change operating device is constructed by interposing a spiral spring in a transmission system with a sun gear so as to store energy in the spiral spring when the speed change device is under heavy load.

(Function) As described above, according to the present invention, the rotation of the manual operation lever is transmitted as accelerated rotation to the output shaft via the speed increasing mechanism, and a spiral spring is provided in the speed increasing mechanism. Since the energy storage mechanism is provided, when the transmission is under a light load, the speed of the transmission can be changed by the rotation increased through the speed increasing mechanism, for example, through a worm and a worm gear. When the transmission is under heavy load, the displacement energy generated by the rotation of the manual operation lever is temporarily stored in the spiral spring of the energy storage mechanism installed in the speed increasing mechanism, and when the load becomes light, the displacement energy is released. A predetermined speed change can be performed all at once.

Therefore, according to the device of the present invention, it is possible to use the power storage mechanism to perform a gear shift operation under heavy load, which was previously impossible, and it is also possible to preset the gear shift operation. damage can be prevented.

Furthermore, since the device of the present invention has a speed increasing mechanism,
Even if the rotation angle of the manual operation lever is small, a large shift operation amount can be obtained by speed-up rotation, so according to the present invention, the manual operation lever The rotation angle of can be set to an appropriate value.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings. 9 to 12 show an example of a continuously variable bicycle transmission device suitable for using the device of the present invention, in which 1 is a chain stay of a bicycle frame, 2 is a backhawk, 3 is a rear gear, 4 is a rear wheel hub axle fixed to the rear pawl 3 with a lock nut 5;
6 is a rear wheel hub rotatably fitted through a bearing 7, and 8 is a spoke.

Threaded portion 4 of rear wheel hub axle 4 outside bearing 7
An inner eccentric cam 9 is screwed and fixed to a.
An outer eccentric cam 11 integrally formed with a worm gear 10 is rotatably fitted around the outer periphery of the inner eccentric cam 9. A worm 12 meshes with the worm gear 10, and a shaft 12a thereof is fitted with a corner end 13a of the inner wire 13 (see FIG. 10) so as to be rotatable with respect to the case 14. 1
5 is a bearing, 16 is a collar, and 17 is a cap.

Further, reference numeral 18 denotes a carrier in which a small diameter cylindrical portion 18a and a large diameter cylindrical portion 18b are integrally connected.
The large-diameter cylindrical portion 18b is fitted into the outer periphery of the outer eccentric cam 11 via the rear wheel hub 6, and is located within a hollow cylindrical case 6a formed integrally with the rear wheel hub 6.

Further, 20 is a dish-shaped case in which the worm 1 is
This case 20 is fixed to the rear wheel hub shaft 4 by an inner eccentric cam 9 and a lock nut 5. 21 is a sprocket for the rear wheel, and 21a is a cylindrical part formed integrally with this sprocket 21. This sprocket 21 is rotatably installed between the case 20 and the rear wheel hub 6 via bearings 22 and 23. It is being 24 is chain.

Furthermore, a plurality of rows of ratchet rings 26 and 27 are arranged in parallel on the inner circumferential surface of the cylindrical portion 21a of the sprocket 21 via a one-way clutch 25, and a ratchet ring 26a is provided on the inner circumferential surface of each of these ratchet rings 26 and 27, respectively. , 27a, and a double row of pawls 28, 29 each meshing with the ratchets 26a, 27a, each row having a plurality of pawls (five in this embodiment).
The base of the carrier 18 is connected to the small diameter cylindrical portion 18a of the carrier 18.
They are arranged alternately on the left and right and are pivotally supported via pins 30 on the outer periphery of the. Note that 25a is a ball forming the one-way clutch 25, and 25b is its extrusion spring. The one-way clutch 25 can also be of other types, such as using a ratchet and pawl. Further, reference numeral 31 denotes a spring for constantly pressing the tips of the claws 28, 29 against the ratchets 26a, 27a.

Furthermore, a plurality of rows of ratchet rings 32 and 33 are arranged in parallel on the inner circumferential surface of the large-diameter cylindrical portion 18b of the carrier 18 via a one-way clutch 25 similar to that described above. Ratchets 32a and 33a are provided, and a plurality of claws 3 in each row (five in this embodiment) are provided in double rows and engage with the ratchets 32a and 33a, respectively.
4 and 35 to the case 6a of the rear wheel hub 6.
The inner boss portion 6b is pivotally supported on the outer periphery of the inner boss portion 6b via pins 36, which are arranged alternately on the left and right. Note that 37 always latches the tips of claws 34 and 35 to 32a and 32a.
This is a spring for pressure contact with 3a.

Next, the operation of the continuously variable transmission configured as described above will be explained. First, to explain the transmission sequence, a crank gear rotates via a crank pedal (not shown), and the rotation is transmitted to the sprocket 21 by the chain 24. The rotation of the sprocket 21 is controlled by the ratchet ring 2 via a one-way clutch 25.
6, 27, and further ratchet 26a,
It is transmitted from 27a to the carrier 18 via claws 28, 29 and pin 30. As the carrier 18 rotates, the ratchet rings 32, 33 rotate via the one-way clutch 25, so that the pawls 34, 35,
Rotation is transmitted to the rear wheel hub 6 via the pin 36.

In other words, in this device, the claws 28 and 29
The power is transmitted through two sets of transmissions: a first-stage transmission and a second-stage transmission using pawls 34 and 35.

9 to 12 show the case where the outer eccentric cam 11 is in the maximum eccentric state, but by rotating the inner wire 13, the worm gear 10
When the outer eccentric cam 11 is rotated 180 degrees through the rotation angle, the outer peripheral surface of the outer eccentric cam 11 becomes concentric with the rear wheel hub shaft 4. When the outer eccentric cam 11 becomes concentric,
The drive rotors 21a, 18b and the ratchet rings 26, 27, 32, 33 are also concentric with the rear wheel hub axle 4, so in this state the drive rotors are in the first position.
When rotating clockwise in FIGS. 1 and 12, each ratchet ring and pawl rotate integrally through the one-way clutch, so the gear ratio in this case is 1:1.

Further, when the outer eccentric cam 11 is rotated 180 degrees from the zero eccentric state by the rotational operation of the inner wire 13 to the maximum eccentric state as shown in FIGS. 11 and 12, the arrow D The rotation in this direction is transmitted to the ratchet rings 26, 27, 32, 33 via the one-way clutch 25, and the ratchet rings 26, 32 transmit the rotation to the driven rotating bodies 18a, 6 via the pawls 28, 34, and The etching rings 27, 33 transmit rotation to the driven rotating bodies 18a, 6 via claws 29, 35.

If the outer eccentric cam 11 is eccentric, the speed increase rate due to the pawls within the drive range E shown in FIG. Since it is the largest, the driven rotor will be rotated at an increased speed by this pawl, and the other pawls will slide in the direction of arrow D relative to each ratchet of the ratchet ring.

Then, as the pawl within the drive range E moves out of the drive range E, it is driven at an increased speed via the pawl that enters the drive range E next, and the transmission pawls are sequentially replaced.

The gear ratio (speed increase ratio) in this case is the rear wheel hub axle 4
Angle θ ₁ which is the drive range of the claw with the center 0 ₁ as the base point
is the ratio of the angle θ ₂ which is the driving range of the pawl with the center 0 ₃ of the outer eccentric cam 11 as the starting point.

The speed increasing effect described above is the same for the second stage device shown in FIG. 12, and the first stage device in FIG. 11 and the second stage device in FIG.
The product of the speed increase ratios of the stages becomes the overall speed increase ratio.

The present invention is suitable for a speed change operation device for a continuously variable transmission as described above, and one embodiment thereof will be described below with reference to FIGS. 1 to 8. In the figure, 38 is the frame pipe of the bicycle, 39 is the case body of the speed change operation device, 40 is a band fixed to the case body 39 with screws 41 in order to fix this case body 39 to the frame pipe 38, and 42 is the band 4
0 to the frame pipe 38.

The case body 39 is formed into a substantially disk shape, and a main shaft 43 passes through the center thereof. A substantially disk-shaped lever body 44 is provided on one side of the case body 39 so as to be rotatable about a main shaft 43 . 45 is a washer fitted to both protruding ends of the main shaft 43, and 46 is a nut.

Further, a lever 47 is integrally formed with the lever body 44, and an internal gear wheel 48 is further formed inside the disk-shaped lever body 44. A shaft tube 49 is rotatably fitted onto the main shaft 43 inside the space formed by the case body 39 and the lever body 44, and a sun gear is attached to the right end of the shaft tube 49 in FIG. 50 is formed, and a large-diameter spur gear 51 is integrally formed at the left end. Reference numeral 52 denotes a collar inserted between both end surfaces of the shaft cylinder 49 and the case body 39 and the lever body 44 facing each other.

Further, 53 has a tongue-like protrusion 53b at one location on the outer periphery of the disc portion 53a, and a shaft cylindrical portion 53c.
This carrier 53 is rotatably fitted to the outer periphery of the shaft tube 49 via its shaft tube portion 53c. The disc portion 53a of this carrier 53 is positioned on the sun gear 50 side (on the right side in FIG. 2).

Further, as shown in detail in FIG. 7, the disk portion 54a
and a shaft cylindrical portion 54b, and a projection 54c that slightly projects outward is provided at one location on the outer periphery of the disk portion 54a, and a projection 54c is provided on the outer periphery of the projection 54c on the front and back of the disk portion 54a. A spring holder A54 having curved plate-shaped projecting pieces 54d is integrally formed, and the spring holder A54 is attached to both disc parts 53a and 5 with respect to the carrier 53, as shown in FIG.
4a are fitted so that they are in sliding contact.

Further, as shown in detail in FIG. 8, the disk portion 55a
and a shaft cylindrical portion 55b, and a projection 55c that slightly projects outward is provided at one location on the outer periphery of the disc portion 55a, and a projection 55c is provided on the outer periphery of the projection 55c on the front and back of the disc portion 55a. As shown in FIG. Both disk portions 54 are attached to the holder A54.
a, 55a are fitted in sliding contact, and in this case, as shown in FIGS. 1, 3, and 4, the spring holder A54
The protrusion 54d of the carrier 53 is positioned below the protrusion 53b of the spring holder B.
The protruding piece 55d of 55 is the protruding part 53b of the carrier 53.
so that it is located above.

Further, as shown in FIGS. 1, 3, and 4, each protrusion 54
d and 55d are respectively engaged with both sides of the protrusion 53b, the two protrusions 54d and 55
Stopper 5 whose tip 56a fits into the gap d
6 is screwed into the case body 39.

Then, the spiral spring 57 is fitted onto the outer periphery of the shaft cylinder portion 55b of the spring holder B55, and the spiral spring 5
As shown in FIG. 4, the inner end 57a of the spring holder B55 is engaged with the spring locking groove 55e, and the outer end 57b of the spring holder B55 is engaged with the projection 54d of the spring holder A54. The protruding piece 54d of A54 and the protruding piece 55d of the spring holder B55 are
Always the protrusion 53b of the carrier 53 and the stopper 56
Force is applied so that it is compressed from both sides.

Further, as shown in FIG. 1, the lever body 44
A large number of substantially hemispherical recesses 48a are circumferentially arranged in parallel on the outer peripheral surface of the internal gear 48, which is integral with the internal gear 48.
8a to be fitted into the hole 39a provided in the case body 39, a push pin 59 is inserted into the hole 39a, and the outwardly protruding end of the push pin 59 is pressed by the leaf spring 60. Lever 47
When the lever 47 is rotated, the lever 47 can be held at a desired position by a temporary stop function due to the engagement between the ball 58 and the recess 48a. Note that 61 is a screw for fixing the base of the leaf spring 60 to the case body 39.

Also, an internal gear 48 integrated with the lever main body 44
A plurality of planetary gears 62 (three in this embodiment) are pivotally supported on the carrier 53 by a shaft 63 and meshed with the sun gear 50.
(see figure).

Further, as shown in FIG. 2, a circular opening 39b is provided in the wall of the case body 39 on the side where the spur gear 51 is disposed, and a disk-shaped lid 64 is inserted into this opening 39b using screws 65.
The shaft 66 is fixed between the inside of the lid 64 and the inner protrusion 39c of the opposing case body 39, and has a small diameter spur gear 67 that meshes with the large diameter spur gear 51 described above. At the same time, an intermediate gear 69 having a bevel gear 68 integrally formed on its side surface is rotatably supported by the shaft 66. Note that 70 is axis 6
This is the collar fitted to 6.

Further, a small-diameter bevel gear 71 that meshes with the bevel gear 68 is rotatably provided on the case body 39 via an output shaft 72. 73 is a bush for the bearing.

In addition, a square hole 72 is provided at the outwardly projecting end of the output shaft 72.
a is formed, and the square end 13a of the inner wire 13 is fitted into this square hole 72a.
73 is the outer wire of the inner wire 13;
74 is a cap for fixing the end of this outer wire 73 to the case body 39.

Next, the operation of the shift operating device of the present invention constructed as described above will be explained.

First, a case will be described in which the transmission system of the bicycle, such as the above-mentioned continuously variable transmission, is in a no-load or light-load state, so the energy storage mechanism in the device of the present invention does not operate, and only the speed increasing mechanism operates.

When the lever 47 is rotated in the direction of arrow F in FIGS. 1 and 3, the lever main body 44 is rotated in the direction of arrow G as shown in FIG. Rotate in the direction of arrow H in the figure. The carrier 53 in this case is the spiral spring 5
The stopper 56 and the protruding piece 54 are
It is assumed that the carrier 53 is stationary because it is almost immobile due to the mutual engagement between the carrier 53 and the protrusion 53b. carrier 5
3 is at rest and the internal gear 48 rotates in the direction of arrow H in FIG. 3, each planetary gear 62 rotates in the direction of arrow I in FIG. It rotates at increased speed in the direction of arrow J in Figure 3. This transmission mechanism is a first stage speed increasing mechanism.

Next, when the sun gear 50 rotates, the large-diameter spur gear 51 rotates together through the shaft cylinder 49, and the small-diameter spur gear 67 that meshes with this rotates at an increased speed.
This transmission mechanism is a second stage speed increasing mechanism.

Further, when the spur gear 67 rotates, the bevel gear 68 integrated therewith also rotates, so that the small diameter bevel gear 71 meshing with the bevel gear 68 rotates at an increased speed. This is the third stage speed increasing mechanism, and in the case of this embodiment, the overall speed increasing rotation is approximately 38 times.

This accelerated rotation causes the inner wire 1
3 to the worm 12 shown in FIG. 9 and FIG. The amount of eccentricity can be changed. That is, the gear ratio can be changed according to the amount of operation of the lever 47.

If the lever 47 shown in FIG. 1 is rotated in the direction of arrow K in the opposite direction, the eccentric cam can be returned to its original position by performing the operation opposite to that described above.

Next, if you perform a gear shift operation while the bicycle's transmission system is under load, in some cases, excessive force may be applied to the gear shift operating device, damaging the device or causing the lever 47 to not move. .

However, according to the device of the present invention, since there is an energy storage mechanism, the gear shifting operation is possible even in the above-mentioned cases, and the displacement energy caused by the gear shifting operation is temporarily stored in the spiral spring of the energy storage mechanism. When the transmission system is under a light load or no load, such as when the pedal is loosened or once stopped, the stored force can be released to perform a speed change operation all at once. The effect will be explained below.

That is, when a heavy load is acting on the transmission system of the bicycle, if the lever 47 is rotated in the direction of arrow F as shown in Figs.
Since FIG. 6 is a view seen from the back side of FIGS. 1 and 3, the direction of the arrow is opposite. ) The internal gear 48 also rotates in the direction of arrow H, but in this case the sun gear 50 does not rotate, so the planetary gears 62 revolve in the direction of arrow L while rotating in the direction of arrow I in FIG. Therefore, the carrier 53 also rotates in the direction of arrow L via the shaft 63.

When the carrier 53 rotates in the direction of arrow L,
Since the protrusion 53b of the carrier 53 moves from the position of the stopper 56 shown in FIG. 4 to the position shown in FIG. The inner end 57 of the spiral spring 57
Rotate a from the position shown in Fig. 4 to the position shown in Fig. 5. In this case, the outer end 57b of the spiral spring 57
Since is not moving, the spiral spring 57 is charged by the amount of rotation of the arrow L.

Note that even if the lever 47 is released in this state, the lever 47 is held at its shift position by the engagement between the ball 58 and the recess 48a shown in FIG. If, for example, the pedal is stopped once in the preset state of the gear shift operation and the transmission system becomes a light load or no-load state, the resistance in the transmission system will suddenly decrease, and the spring holder B55 will change from the state shown in FIG. Rotate in the direction of arrow M to the state shown in Figure 4, and
The carrier 53 also rotates in the direction of arrow M via the protrusion 53b. When the carrier 53 rotates in the direction of arrow M in FIG. The planetary gear 62 can be rotated in the direction of arrow J by revolution in the direction of arrow M and rotation in the direction of arrow N, thereby performing a predetermined speed change operation as described above.

Note that FIG. 6 is an explanatory diagram when the lever 47 is operated to change gears as indicated by arrow 0 when the transmission system is under heavy load. When the lever 47 is operated in the direction of arrow 0, the internal gear 48 also rotates in the direction of arrow P, so that the planetary gear 62 rotates in the direction of arrow Q and revolves in the direction of arrow R. (Sun gear 5
0 does not rotate) Therefore, the carrier 53 also rotates in the direction of the arrow R via the shaft 63, so the spring holder A54 also rotates in the direction of the arrow R via the protrusion 53b and the protrusion 54d. As a result, by displacing the outer end 57b of the spiral spring 57 from the position shown in FIG. 4 to the position shown in FIG.
Save up to 7. As described above, if the resistance of the transmission system decreases in this state, the speed change operation is performed by the action of the spiral spring 57.

(Effects of the Invention) As described above, according to the present invention, the rotation of the manual operation lever 47 is transmitted as accelerated rotation to the output shaft 72 via the speed increasing mechanism, and Since the energy storage mechanism is provided with a spiral spring 57, when the transmission is under a light load, the rotation speed increased through the speed increasing mechanism increases the speed of the transmission through, for example, the worm 12 and the worm gear 10. In addition to being able to perform gear shifting operations, when the transmission is under heavy load, the displacement energy caused by the rotation of the manual operating lever 47 is temporarily stored in the spiral spring 57 of the energy storage mechanism provided in the speed increasing mechanism.
When the load becomes light, the displacement energy can be released to perform a predetermined speed change all at once.

Therefore, according to the device of the present invention, the power storage mechanism allows gear shifting operations under heavy loads, which were previously impossible, and also enables presetting of gear shifting operations. The effect is that damage to the device can be prevented.

Furthermore, since the device of the present invention has a speed increasing mechanism,
Even if the rotation angle of the manual operation lever 47 is small, a large shift operation amount can be obtained by increasing the speed. Another advantage is that the rotation angle of the lever 47 can be set to an appropriate value.

[Brief explanation of the drawing]

FIG. 1 is a front view showing a part of the speed change operating device of the present invention in cross section, FIG. 2 is a sectional view taken along the - arrow in FIG.
Fig. 3 is a sectional view of Fig. 2, Fig. 4 is a sectional view of Fig. 2, Figs. Figure 8b is a side view of the spring holder B, Figure 8a is a front view of the spring holder B, Figure b is a side view thereof, Figure 9 is a vertical sectional view of the continuously variable transmission, and Figure 10 is a part of it. Fig. 11 is a side view showing the cross section of Fig. 9 -
12 is a sectional view of the same. 10... Worm gear, 12... Worm, 1
3...Inner wire, 39...Case body, 4
3...Main shaft, 44...Lever body, 47...Lever (manual operation lever), 48...Internal gear, 50
... sun gear, 51 ... spur gear, 53 ... carrier, 53b ... protrusion, 54 ... spring holder A,
54d... Projection piece, 55... Spring holder B, 55
d... Projection piece, 56... Stopper, 57... Spiral spring, 57a... Inner end, 57b... Outer end, 62... Planetary gear, 67... Spur gear, 68...
...Bevel gear, 72...Output shaft.

Claims (1)

[Claims] 1. A lever body integrally formed with a lever is rotatably provided on a bicycle frame, and the rotation of the lever body is accelerated and taken out by a gear speed increasing device including a planetary gear device, and a carrier of the planetary gear device 1. A bicycle speed change operating device, characterized in that a spiral spring is interposed in a transmission system between the transmission system and the sun gear, and energy is stored in the spiral spring when the speed change device is under heavy load.