JPS62143786A - Variable speed driving device for bicycle - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

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 Problems) In order to achieve the above-mentioned object, the present invention transmits the rotation of the manual operation lever as accelerated rotation to the output shaft via a speed increasing mechanism, and increases the speed of the output shaft. In a device for changing the speed of a bicycle by rotation, a bicycle speed change operating device is constructed by providing an energy storage mechanism using a spiral spring in the speed increasing mechanism.

(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 rotation speed increased through the speed increasing mechanism allows the transmission to be shifted, for example, via a worm and a worm gear. When the device is under heavy load, the displacement energy caused by the rotation of the manual operation lever is 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 at once.

Therefore, according to the device of the present invention, it is possible to allow gear shifting operations under heavy loads, which were previously impossible, by using the energy storage mechanism, and it is also possible to preset gear shifting operations, and furthermore, it is possible to prevent gear shifting operations caused by forced operations. 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 operating lever is small, a large amount of speed change operation can be obtained by speed increasing rotation. The rotation angle of the manual operation lever can be set to an appropriate value even for a large-volume transmission.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings. 9th
Figures 1 to 12 show an example of a continuously variable bicycle transmission device suitable for using the present invention.
is a bicycle frame chain stay, 2 is a back hawk,
3 is a rear pawl, 4 is a rear wheel hub shaft 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.

An inner eccentric cam 9 is screwed and fixed to the threaded portion 4a of the rear wheel hub shaft 4 outside the bearing 7, and an outer eccentric cam 11 is formed integrally with a worm gear 10 on the outer periphery of the inner eccentric cam 9. It is fitted so that it can rotate freely. 12 is a worm meshed with this worm gear 10, 12a is its shaft,
It fits into the peripheral end 13a (see FIG. 10) of the inner wire 13 and is rotatable with respect to the case 14. 1
5 is a bearing, 16 is a collar, and 17 is a cap.

Reference numeral 18 denotes a carrier in which a small-diameter cylindrical portion 18a and a large-diameter cylindrical portion 18b are integrally connected. , a large-diameter cylindrical portion 18b is located within a hollow cylindrical case 6a formed integrally with the rear wheel hub 6.

Reference numeral 20 denotes a dish-shaped case, which is formed integrally with the case 14 of the worm 12, and the case 20 is fixed to the rear wheel hub shaft 4 by an inner eccentric cam 9 and a lock nut 5. 21 is the sprocket for the rear wheel, 21
A is a cylindrical portion formed integrally with this sprocket 21, and this sprocket 21 is rotatably provided between the case 20 and the rear wheel hub 6 via bearings 22 and 23. 24 is Cheno.

Furthermore, a plurality of rows of ratchet rings 26 are connected to the inner peripheral surface of the cylindrical portion 21a of the sprocket 21 via a one-way clutch 25.
, 27, each of these ratchet rings 26
, 27 are provided with ratchets 26a and 27a, respectively.
and a plurality of ratchets in each row (in this embodiment, 5
The bases of the claws 28 and 29 are pivotally supported by being arranged alternately on the left and right sides via pins 30 on the outer periphery of the small diameter cylindrical portion 18a of the carrier 18-. Note that 25a is a ball forming the one-way clutch 25, and 25b is a spring for pushing it out. This one-way clutch 25 may be of another type using a ratchet and pawl, for example. In addition, 31 always holds the tips of the claws 28 and 29 in the ratchet 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. Ratchet 32a,
33a and a ratchet 32a.

The bases of the double-row pawls 34 and 35, each row having a plurality of pawls 34 and 35 (five in this embodiment) that mesh with the pins 33a, are attached to the outer periphery of the boss portion 6b in the case 6a of the rear wheel hub 6 using a pin 36.
They are arranged alternately on the left and right and are pivotally supported. In addition,
37 is a pawl 34"; the tip of 35 is always ratcheted 32a
, 33a.

Next, the operation of the continuously variable transmission configured as described above will be explained. First, the transmission order will be explained. A crank gear rotates via a crank pedal (not shown), and the rotation is transmitted to the sprocket 21 by the chino 24. The rotation of the sprocket 21 is transmitted to the ratchet rings 26 and 27 via the one-way clutch 25, and further transmitted from the ratchets 26a and 27a to the carrier 18 via the pawls 28 and 29 and the pin 30. When the carrier 18 rotates, the ratchet ring 32 is activated via the one-way clutch 25.
, 33 are rotated, and as a result the claws 34, 35 and the bin 3 are rotated.
Rotation is transmitted to the rear wheel hub 6 via the rear wheel hub 6.

That is, in this device, the power is transmitted through two sets of transmissions: a first stage transmission made up of pawls 28 and 29, and a second stage transmission made up of pawls 34 and 35.

9 to 12 show the case where the outer eccentric cam 11 is in the maximum eccentric state, but when the outer eccentric cam 11 is rotated 1800 times via the worm gear 10 by rotating the inner wire 13, The outer peripheral surface of the outer eccentric cam 11 is concentric with the rear wheel hub shaft 4. When the outer eccentric cam 11 becomes concentric, the drive rotary body 21a.

18b1 and each ratchet ring 26, 27, 3
2.

33 is also concentric with the rear wheel hub shaft 4, so when the drive rotating body rotates clockwise in Fig. 11.12 in this state, each ratchet ring and pawl rotate integrally via the one-way clutch. , the gear ratio in this case is 1:1.

Also, by rotating the inner wire 13, the outer eccentric cam 11 is rotated 1800 times from the eccentric O state to the 11th.
As shown in FIG. 12, when the maximum eccentricity is reached, the rotation of the drive rotors 21a and 18b in the direction of the arrows occurs through the one-way clutch 25 and the ratchet rings 26 and 27.

32, 33, ratchet rings 26, 32
transmits rotation to the driven rotating bodies 18a, 6 via the pawls 28, 34, and the ratchet rings 27, 33 transmit rotation to the pawls 29, 3
The rotation is transmitted to the driven rotors 18a and 6 via the rotary shaft 5.

If the outer eccentric cam 11 is eccentric, the 11th
Since the speed increase rate by the pawl within the drive range E in the figure (in this case, there are 10 winds, so the angle is 36 degrees, which is equally divided by 1θ of 360 degrees), the driven rotor rotates at an increased speed due to this pawl. The other pawl will slide and rotate in the direction of the arrow with respect 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 center O of the rear wheel hub shaft 4.
The angle θ is the drive range of the claw with I as the base point.

is the ratio of the angle θ2 which is the drive range of the pawl with the center 03 of the outer eccentric cam 11 as the base point.

The above speed increasing effect is the same for the second stage device shown in Figure 12, and the sum of the speed increasing ratios of the first stage in Figure 11 and the second stage in Figure 12 is the total increase. It becomes the speed ratio.

The present invention is suitable for a speed change operating 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 gear shift operating device, and 40 is the screw 4 used to fix the case body 39 to the frame pipe 38.
1 is a band fixed to the case body 39, and 42 is a screw for fastening the band 40 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. On one side of the case body 39, a disk-shaped lever body 44 is provided rotatably 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 main body 44, and an internal gear wheel 48 is further formed inside the lever main body 44 having a disc shape. A shaft cylinder 49 is rotatably fitted to the main shaft 43 inside the space formed by the case body 39 and the lever body 44.
A sun gear 50 is formed at the right end in the figure.
Further, a large-diameter spur gear 51 is integrally formed at the left end. Reference numeral 52 denotes a case body 3 facing both end surfaces of the shaft tube 49.
9 and the lever main body 44.

Reference numeral 53 denotes a carrier having a tongue-like protrusion 53b at one location on the outer periphery of the disc portion 53a, and a shaft tube portion 53c. is rotatably fitted around the outer periphery of the The disk 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, it has a disc part 54a and a shaft cylinder part 54b, and a protrusion 54c that slightly protrudes outward is provided at one location on the outer periphery of the disc part 54a. Spring holder A5 includes curved plate-shaped protrusions 54d that protrude from the front and back sides of the disk portion 54a, respectively, on the outer circumference of the protrusion 54c.
As shown in FIG.
54a are fitted in sliding contact.

Further, as shown in detail in FIG. 8, it has a disc part 55a and a shaft cylinder part 55b, and a protrusion 55c that slightly protrudes outward is provided at one location on the outer periphery of the disc part 55a. The protrusion 55c has a curved plate-shaped protrusion 55d on the outer circumference thereof, which protrudes from the front and back sides of the disc part 55a, and further includes a shaft cylinder part 55.
A spring holder 855 with a spring locking groove 55e is integrally formed in b, and as shown in FIG.
55a are fitted in sliding contact, in this case No. 1.3.
As shown in FIG. 4, the protrusion 54d of the spring holder A54 is positioned below the protrusion 53b of the carrier 53, and the protrusion 55d of the spring holder 855 is positioned above the protrusion 53b of the carrier 53. position.

Further, as shown in Fig. 1.3.4, each protrusion 54d, 55
The tip 56a fits into the gap between the two protrusions 54d and 55d while the protrusions 54d and 55d engage with each other on both sides of the protrusion 53b.7) The par 56 is screwed into the case body 39.

Then, the spiral spring 57 is attached to the shaft cylinder portion 5 of the spring holder B55.
5b, and the inner end 5 of this spiral spring 57
As shown in FIG. 4, the outer end 57b is engaged with the spring locking groove 55e of the spring holder B55, and the outer end 57b is engaged with the protrusion 54d of the spring holder A54. and the protruding piece 55 of the spring holder 855.
d always corresponds to 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, on the outer peripheral surface of the internal gear 48 which is integral with the lever main body 44, a large number of hemispherical recesses 48a are arranged in parallel on the circumference, and these recesses 48a are fitted. Insert the ball 58 into the hole 39a provided in the case body 39, insert the push pin 59 into the hole 39a, press the outwardly projecting end of the push pin 59 with the leaf spring 60, and rotate the lever 47. When the lever 47 is operated, 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.

Further, a plurality of (three in this embodiment) planetary gears 62 that mesh with the internal gear 48 that is integral with the lever main body 44 and the sun gear 50 are connected to the carrier 5 by a shaft 63.
3 (see Figure 3).

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 disc-shaped lid 64 is fixed to this opening 39b with screws 65. The shaft 66 spans between the inner side of the case body 39 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. An intermediate gear 69 integrally formed with the gear 68 is rotatably supported by the shaft 66.

Note that 70 is a collar fitted onto the shaft 66.

In addition, a small diameter bevel gear 71 that meshes with the bevel gear 68 is attached to the output shaft 7.
2 to be rotatably provided in the case body 39.

73 is a bushing for the bearing.

A square hole 72a is formed in the outwardly projecting end of the output shaft 72, and the square end 13a of the inner wire 13 is fitted into the square hole 72a. 73 is an outer wire of the inner wire 13, and 74 is this outer wire 7.
This is a cap for fixing the end portion of 3 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 Figure 3.

In this case, the carrier 53 remains stationary because the stopper 56, the projections 54d, 55d, and the projection 53b are held together by the biasing force of the spiral spring 57. It is assumed that When the carrier 53 is in a stationary state 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 FIG.

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.

Also, when the spur gear 67 rotates, the bevel gear 68 integrated with it
As the bevel gear 68 rotates, 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, a speed increasing rotation of about 38 times can be obtained as a whole.

Since this accelerated rotation is transmitted to the worm 12 shown in FIGS. 9 and 10 via the inner wire 13, the worm gear 10 meshing with the worm 12
By rotating the outer eccentric cam 11 with respect to the inner eccentric cam 9 via the cam, the amount of eccentricity of the entire cam 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 the arrow in the opposite direction, the eccentric cam can be returned to its original position by performing the operation opposite to the above-mentioned operation.

Next, if a gear shift operation is performed while the transmission system of the bicycle is under load, an excessive force may be applied to the gear shift operating device, damaging the device, or the lever 47 may not move.

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

In other words, when a heavy load is applied to the bicycle's transmission system,
When the lever 47 is rotated in the direction of arrow F as shown in Fig. 1.3.4.5, (Fig. (The direction is opposite.) The internal gear 48 also rotates in the direction of the arrow H, but in this case the sun gear 50 does not rotate, so the planetary gear 62 rotates in the direction of the arrow I in FIG. It revolves like this. Therefore, the carrier 53 also rotates in the direction of the arrow via the shaft 63.

When the carrier 53 rotates in the direction of the arrow, 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. 55d, the spring holder B55 is rotated in the direction of the arrow, and the inner end 57a of the spiral spring 57 is accordingly rotated from the position shown in FIG. 4 to the position shown in FIG. In this case, since the outer end 57b of the spiral spring 57 is immovable, the spiral spring 57 is loaded with energy only by the rotational bone indicated by the arrow.

Note that even if the lever 47 is released in this state, the lever 47 is held at the gear shift position by the engagement between the ball 58 and the recess 48a shown in FIG. If, for example, the transmission system becomes a light load or no-load state in the preset state of the gear shift operation, for example, once the pedal is stopped being depressed, 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 the arrow M in FIG. 3, the planetary gear 62 rotates in the direction of the arrow N by meshing with the internal gear 48, which is stationary in this case, so that the sun gear 50 is rotated as a planetary gear. By rotating the gear 62 in the direction of the arrow M and rotating in the direction of the arrow N, it is possible to perform 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 lever 47 is operated as shown by arrow O, internal gear 4
8 also rotates in the direction of arrow P, the planetary gear 62 rotates in the direction of arrow Q and revolves in the direction of arrow R. (
(Since the sun gear 50 does not rotate), 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 piece 54d. As a result, force is stored in the spiral spring 57 by displacing the outer end 57b of the spiral spring 57 from the position shown in FIG. 4 to the position shown in FIG. As described above, if the resistance of the transmission system is reduced 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 the spiral spring 57, when the transmission is under a light load, the rotation speed increased through the speed increasing mechanism allows the transmission to be shifted, for example, through the worm 12 and the worm gear 10. In addition, when the transmission is under heavy load, the displacement energy caused by the rotation of the manual operation lever 47 is temporarily stored in the spiral spring 57 of the energy storage mechanism provided in the speed increasing mechanism, and when the load is light, When this occurs, 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 a gear shift operation under heavy load, which was previously impossible, and also enables presetting of the gear shift operation.
Furthermore, it is possible to prevent damage to the device due to forced operation.

Further, 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 amount of speed change operation can be obtained by speed increasing rotation. This also provides the effect that the rotation angle of the manual operation lever 47 can be set to an appropriate value even for a transmission that requires a large amount of operation.

[Brief explanation of drawings]

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 cross section taken along the line n-If in FIG. 1; FIG. 4 is a sectional view taken along IV-IV in FIG. 2, FIGS.
) Front view of spring holder A, Figure (b) is its side view, Figure 8 (a) Front view of spring holder B, Figure (b) is its side view, Figure 9 is continuously variable speed. FIG. 10 is a side view showing a part of the apparatus in cross section, FIG. 11 is a sectional view taken along line G-XI in FIG. 10... Worm gear 12... Worm 13.
...Inner wire 39...Case body 43...
Main shaft 44...Lever body 47...Lever (manual fi-operation lever) 48...Internal gear
50...Sun gear 51...Spur gear 53.
...Carrier 53b...Protrusion 54...Spring holder A34d...Protrusion piece 55...Spring holder B55d...Protrusion piece 56...Stopper 5
7... Spiral spring 57a... Inner end 57b
... Outer end portion 62 ... Planetary gear 67 ... Spur gear 68 ... Bevel gear 72 ... Output shaft patent Applicant Brideston Cycle Co., Ltd. No. 1
Figure 2 diagram. Fig. 4 62 (Planetary tooth button Fig. 7'a) (b> Fig. 8 (a": (b) 55 (trtu, q-B)

Claims (1)

[Claims] 1. In a device in which the rotation of a manual operating lever is transmitted as accelerated rotation to an output shaft via a speed increasing mechanism, and the speed of the bicycle is changed by the rotation of this output shaft, there is a spiral in the speed increasing mechanism. A bicycle gear shift operating device characterized by being equipped with a spring-based energy storage mechanism.