JPS62103286A - Speed change changeover device for speed change gear 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 switching device for a speed change device provided on the crankshaft of a bicycle.

(Prior art) The bicycle transmission that is currently widely used uses a chain 7 that extends between multiple sprockets as a derailleur.
It is a so-called external transmission that is changed through the transmission.

In addition to this, there is also a so-called internal transmission, which has a transmission mechanism built into the hub of the rear wheel, but it is not widely used.

Further, as a transmission device incorporating a planetary gear mechanism in a crankshaft portion, there is one disclosed, for example, in Japanese Utility Model Publication No. 2849.

However, the conventional device disclosed in Utility Model Publication No. 1989-19 has the problem of being difficult to commercialize due to its limited three-speed transmission due to the arrangement of the planetary gears and its complicated structure. there were.

In order to solve the above-mentioned problems, the present applicant first arranged three or more shafts on the same circumference of a carrier integrated with the crank arm, and each of these shafts had a plurality of rows of planets with different numbers of teeth. In addition to integrally forming a plurality of rows of internal gears in which the gears are rotatably fitted and meshed with each of these planetary gears,
A driven rotating body having a sprocket formed on its outer periphery is rotatably provided on the carrier, a one-way clutch is provided between the driven rotating body and the carrier, and multiple rows of sun gears mesh with each of the planetary gears. The present application has been filed for a bicycle transmission device in which one-way clutches are provided between the inner peripheral portion of the frame and a fixed shaft portion integral with the frame, and one of these one-way clutches can be selectively connected.

(Problem to be Solved by the Invention) However, the above-mentioned bicycle transmission has one-way clutches provided between the inner circumferential portions of the sun gears in multiple rows and a fixed shaft portion integral with the frame, and each of these Since this is a special device in which the gears are changed by selectively connecting one of the one-way clutches, there is a problem that the gear change operation cannot be performed using conventional gear shifting devices.

(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, a ratchet is formed on the inner circumferential portion of each row of sun gears having different numbers of vA, and a fixed shaft portion integral with the frame is provided. A plurality of pawls that can be engaged with and disengaged from each of the ratchets are arranged in parallel on the outer periphery of the cylindrical part and the wire reel part, and springs are provided to bias these pawls so as to engage with their corresponding ratchets. A stepped opening having a plurality of steps through which the tips of the plurality of pawls can pass through is provided in the cylindrical portion of the speed change cylinder, and the cylindrical portion of the speed change cylinder is configured to surround the fixed shaft portion. A speed change operation wire is wound around the wire reel portion to form a speed change switching device for a bicycle transmission.

(Function) As described above, the device of the present invention performs a speed change operation by rotating a speed change cylinder having a step-like opening, and for increasing speed, three pawls move outward from the opening one by one. This is done by protruding and sequentially engaging each corresponding ratchet,
The speed change for deceleration is performed by pulling the three claws protruding outward from the opening into the opening one by one.

In other words, according to the device of the present invention, both the increase and deceleration can be performed by simply moving one claw in and out. Since there is no need to do this, there is no slippage or simultaneous meshing during gear shifting, and the gear shifting is performed smoothly.

Furthermore, the device of the present invention has the advantage that it is easy to operate and works reliably.

(Example) Hereinafter, an example of the present invention will be described with reference to the drawings. 1 in the figure (see figure 2) is the main pipe of the bicycle frame,
2 is a vertical pipe, 3 is a hinge, 4 (see Figure 1)
5 is a hanger pipe, 5 is a fixed shaft portion that is screwed into the hanger pipe 4 and is integrally fixed to the frame, and is also used as a bearing unit; 6 is a crankshaft that is rotatably provided through the fixed shaft portion 5; 7
8 is a crank arm fitted onto the crankshaft 6, 9 is a washer, and 10 is a nut.

As shown in FIG. 2, the transmission of this embodiment has a wheel-shaped carrier 11 having five radial arms Ila fitted into the boss portion 8a of the crank arm 8.
Three or more (five in this embodiment) axes 12 on the same circumference of
are arranged at equal positions on the circumference. That is, in this embodiment, the shaft 12 is fixed by screws 13 inserted into each arm lla of the carrier 11. Note that 14 is a cover plate that is applied to the outer surface of the carrier 11 and fixed with screws 13, and 15 is a washer for the screw 13.

Also, multiple rows each having a different number of teeth (three in this example)
The i-star gears 16, 17, and 18 are rotatably fitted to the shaft 12 via the collar 19, and each of these planetary gears 16
．． 17. Three rows of internal gears meshing with 18 respectively 20.
2L 22 is integrally formed, and a driven rotating body 24 having a sprocket 23 formed on its outer periphery is rotatably provided on the carrier 11 via a bearing 25.

The carrier 11 also has an arm II as shown in FIG.
Protrusions 11b are provided at five locations between a, and a donut-shaped ring plate H1c is applied to these protrusions 11b and the end face of the shaft 12, and ten screws are inserted as shown in FIG. 13.

Further, a ring plate 24a is similarly fitted on the inner surface side of the driven rotating body 24, and between the inner circumference of the ring plate 24a, which is integrated with the driven rotating body 24, and the outer circumference of the ring plate 1c, which is integrated with the carrier 11. A one-way clutch 26 is provided. That is, 26a in FIG. 3 is a ratchet formed on the inner periphery of the ring plate 24a, and 26b is this ratchet 26.
A pawl 26c provided on the outer edge of the ring plays 1 to llc so as to be freely engageable and detachable from the pawl 26c is a spring that urges the pawl 26b to engage with the ratchet 26a. That is, these ratchets 26a and pawls 26b.

The spring 26c forms the one-way clutch 26, but the one-way clutch may be of other types.

Furthermore, three sun gears 27, 28, and 29 that mesh with the planetary gears 16, 17, and 18, respectively, are loosely fitted to the fixed shaft portion 5 that is integrated with the frame, and the outer peripheral portion of the fixed shaft portion 5 and the sun gears are provided. A one-way clutch 30 is provided between each inner peripheral portion of the gears 27, 28, and 29. That is, in FIG. 4, 30a is a ratchet formed on the inner periphery of each sun gear 27, 28, 29, 30b is three pawls arranged in parallel on the fixed shaft portion 5 so as to be able to engage and detach from these ratchet wheels 1-30a, and 30c. are ring-shaped springs that urge these pawls 30b to engage their respective ratchets 30a. A one-way clutch 30 is formed by the ratchet 30a, pawl 30b, and spring 30c.

In the present invention, one of the plurality of sets (three sets in this embodiment) of one-way clutches 30 described above can be selectively connected.

Specifically, as shown in this embodiment, a small diameter cylindrical portion 31 is rotatably fitted to the outer circumferential portion of the fixed shaft portion 5 having a claw 30b.
a, and a large diameter cylindrical portion 3 having a larger diameter than the outer diameter of the hanger pipe 4.
1b, and this large diameter cylindrical portion 31b.
A wire reel portion 31c is provided in the transmission cylinder 31 to form a transmission cylinder 31, and a plurality of stages (mains) through which the tips of the plurality of (three in this embodiment) pawls 30b can each pass through the small diameter cylindrical portion 31a of the transmission cylinder 31. In the embodiment, the step portions 32a, 32 (three steps)
b, 32c (see Figures 5 and 6)
form 2.

As shown in FIG. 1, this speed change cylinder 31 is fitted so that its small diameter cylindrical portion 31a surrounds the fixed shaft portion 5,
In this fitted state, the three steps 32a of the opening 32,
Three claws 30 with 32b and 32c provided on the fixed shaft portion 5
When the tip of the winter melon 30b is located within the opening 32, the pawl 30b protrudes outward under the action of the spring 30c and engages with the corresponding ratchet 30a. Then, the one-way clutch 30 is connected.

The speed change cylinder 31 is rotated by operating the operating wire 33 wound around the wire reel portion 31 as shown by arrows A and B in FIG. 33a shown in FIG. 2 is a wire end for fixing the operating wire 33 to the wire reel portion 31c.

Reference numeral 34 shown in FIG. 1 is a coil spring for biasing the speed change cylinder 31 so as to always rotate clockwise in FIG.
1b, and the other end 34b is locked to the protrusion 4a of the hanger pipe 4. In addition, numeral 35 in the figure is a chino wound around the sprocket 23.

Next, the operation of the transmission configured as described above and the transmission switching device of the present invention will be explained. By operating the speed change operation device (not shown) and pulling the operation wire 33 in the direction of arrow A in FIG. When rotated to the maximum counterclockwise direction in the figure, the opening 32 provided in the small diameter cylindrical portion 31a of the speed change cylinder 31 and the opening 32 provided in the fixed shaft portion 5 open.
The relationship with each claw 30b is as shown in FIG. 7(a). That is, in this case, all the pawls 30b are located within the small diameter cylindrical portion 31a, so there is no pawl 30b that engages with the ratchet 30a.

All sun gears 27, 28, 29 can therefore rotate freely in this case.

In this state, if the crank arm 8 is rotated in the direction of arrow C in FIG. 2 via a crank pedal (not shown),
The carrier 11 fixed to the Tarazoku arm 8 and the ring plate llc of the carrier 11 integrally connected to the carrier 11 rotate in the direction of the arrow in FIG. Therefore, the claw 26b of the one-way clutch 26 and the ratchet 26a
As a result of this engagement, the ring plate 24a integrally connected to the driven rotating body 24 rotates in the direction of arrow E in FIG. Therefore, the driven rotor 24 and sprocket 23 also rotate integrally with the crank arm 8 in the direction of arrow C in FIG. The bicycle travels by driving the In this case, the gear ratio between the crankshaft 6 and the sprocket 23 is 1:1.

At this time, since the carrier 11 and the driven rotating body 24 rotate integrally, the planetary gears 16, 17, and 18 also rotate integrally with the internal gears 20, 2122 that are meshed with each other. The sun gears 27, 28, and 29 meshing with 16, 17, and 18, respectively, are also connected to the crank arm 8.
This rotation is caused by the one-way clutch 30.
There is no problem as both are currently disconnected.

In addition, the sun gears 27, 28, and 29 are loosely fitted to the outer circumference of the small diameter cylindrical portion 31a of the speed change cylinder 31, but in the present invention, three or more (in this embodiment, five) planetary gears are respectively fitted. Because the sun gear is inscribed and meshed, the sun gear does not need to be pivoted by a central axis.

Next, from the state shown in FIG. 7(a) described above, the operation wire 33 is
When loosened by one step in the direction of arrow B in Fig. 2, the transmission cylinder 3
1 is rotated clockwise in FIG. 2 by the action of the coil spring 34, and as a result, the opening 32 moves from the state shown in FIG. 7(a) to the position shown in FIG. 7(b).

As a result, the tip of one pawl 32b is exposed within the stepped portion 32a of the opening 32, and this pawl 32b engages with the corresponding ratchet 32a by the action of the spring 32c.

Therefore, the one-way clutch 32 between the sun gear 27 and the fixed shaft portion 5 is connected.

When the crank arm 8 is rotated in the direction of arrow C in FIG. 2 in this state, each planet gear 16, 17, and 18 is rotated in the direction of arrow G in FIG. revolve. However, in this case, only the sun gear 27 is prevented from rotating in the direction of the arrow G by the one-way gear 30, so the planetary gear 16 meshing with the sun gear 27 rotates in the direction of the arrow H in FIG. . Therefore, the internal gear 20 meshing with the planetary gear 16 rotates at increased speed in the direction shown by arrow I in FIG. 4 by revolution in the direction of arrow G and rotation in the direction of arrow H. This rotation causes the driven rotary body 24 and the sprocket 23 to rotate together, so that the bicycle travels as described above. In this case, the speed increasing ratio of the driven rotating body 24 to the crank arm 8 is approximately 1:1.3 in this embodiment.

In this case, the other planetary gears 17 and 18 are also meshing with the internal gears 21 and 22, so as a result of their revolution and rotation, the sun gears 28 and 29 also rotate to some extent, but these sun gears 28 and 29 Each one-way clutch 3
Since 0 is in a free state, no problem will occur.

In this case, the ring plate 11c in FIG.
Although the rotation of the ring plate 24a in the direction of the arrow E is faster than the rotation in the direction of the arrow E, this rotational speed difference is allowed by the one-way clutch 26.

Next, from the state shown in FIG. 7(b) described above, the working wire 33 is
7(b) to the position shown in FIG. 7(c). Therefore, since the second pawl 30b is also exposed from the stepped portion 32b of the opening 32, the one-way clutch 30 by this pawl 30b is also connected.

When the crank arm 8 is rotated in the direction of arrow C in FIG. 2 in this state, in this case, the internal gear 21 rotates due to the revolution of the planetary gear 17 in the direction of arrow G in FIG. Rotate in the direction of arrow I. However, the rotation speed of the planetary gear 17 in the direction of arrow 11 in this case is faster than the rotation speed of the planetary gear 16 by the difference in the number of teeth, so the speed increase ratio in this case is the previous speed increase ratio. Become bigger.

In this case, the speed increasing ratio in this embodiment is approximately 1:1.5.

In this case, the pawl 30b in the stepped portion 32a of the opening 32 is also in a state of engagement with the ratchet 30a, but in this case, no problem occurs because the ratchet 30a of the sun gear 27 rotates in a direction to overcome the pawl 30b. .

Next, as shown in FIG. 7(c) or FIG. 5(a) (b),
) When the operating wire 33 is loosened one more step, the opening 32 opens as shown in FIG. 7(d) or FIG. 6(a)(b).
), the third pawl 30b is exposed from the stepped portion 32c of the opening 32 and engages with the latch 30a of the sun gear 29, as shown in FIG. 6(b).

As a result, when the crank arm 8 rotates in the direction of arrow C, in this case, the internal gear 22 rotates in the direction of arrow ■ due to the revolution of the planetary gear 18 in the direction of arrow G in FIG. 4 and the rotation in the direction of arrow H. do. And the planetary gear 18 in this case
Since the rotation speed in the direction of arrow (1) becomes faster than the rotation speed of the planetary gear 17 by the difference in the number of teeth, the speed increase ratio in this case will eventually become even larger than the previous speed increase ratio. In this case, the speed increasing ratio in this example is approximately 1:1.6.
It is.

In addition, when decelerating, contrary to the speed increasing operation described above, pull the operating wire 33 in the direction of arrow A in FIG. (c)
, (b), and (a), the gear stage can be shifted to 4-3-2-1.

(Effects of the Invention) As described above, the transmission switching device of the present invention has a stepped opening 3.
The speed change operation is performed by rotating the speed change cylinder 31 having a cylindrical shaft 2, and in order to increase the speed, the three pawls 30b protrude outward from the opening 32, one by one, and the corresponding ratchet l-30a is used. 3 protruding outward from the opening 32, and the speed change for deceleration is performed by sequentially meshing with the opening 32.
This is done by pulling the claws 30b into the opening 32 one by one.

In other words, according to the device of the present invention, both acceleration and deceleration can be performed by simply moving one claw in and out, and when one clutch is operated as in the past, the other clutch is synchronized and operated in the opposite direction. Since there is no need to do this, an excellent effect can be obtained in that the gear shift is smoothly performed without idling or simultaneous meshing during gear shifting. The device of the present invention also has the advantage of being easy to operate and working reliably.

[Brief explanation of drawings]

Fig. 1 is a longitudinal cross-sectional view of a bicycle transmission equipped with the device of the present invention, Fig. 2 is a side view thereof, Fig. 3 is a cross-sectional view taken along the line mm in Fig. 1, and Fig. 4 is a cross-sectional view taken along the line TV-TV. Fig. 5(a) is a plan view showing a part of the transmission cylinder part cut away, Fig. 5(b) is an elevational view showing a part thereof in cross section, and Fig. 6(a).
) is an elevational view showing the state in which the transmission cylinder part is displaced, Figure 7(b) is an elevational view showing a part of it in cross section, and Figure 7(a)
) to (d) are plan views showing the state of the transmission cylinder at each gear stage. 4...Hanger pipe 5...Fixed shaft part 6...
Crankshaft 8--Crank arm 11--Carrier 12--Shaft 14--Cover plate 16
．． 17.18...Planetary gears 20, 21.22...Internal gears 23...Sprockets 24...Followed rotating body 26...One-way clutches 27, 28.29...
...Sun gear 30...One-way clutch 30a...
Ratchet 30b...Claw 30c...Spring
31... Speed change cylinder 31a... Small diameter cylindrical part (
Cylindrical part) 31c... Wire reel part 32... Opening 32a
, 32b, 32c...Stepped portion 33...Operation wire 34...Coil spring 35...Chain Patent Applicant Brideston Cycle Co., Ltd. Figure 5 (a) (b> Figure 6 (a) (b) Figure 7 (a) (b) (C) (d)

Claims (1)

[Claims] 1. A ratchet is formed on the inner periphery of a plurality of rows of sun gears having different numbers of teeth, and a plurality of pawls that can be freely engaged with and disengaged from each of the ratchets are arranged in parallel on the outer periphery of a fixed shaft part that is integrated with the frame. , a plurality of springs are provided for urging each of these pawls to engage with a corresponding ratchet, and the tips of the plurality of pawls can each be passed through a cylindrical portion of a variable speed cylinder having a cylindrical portion and a wire reel portion. A bicycle transmission device comprising: a stepped opening having stepped portions; a cylindrical portion of the speed change cylinder is fitted so as to enclose the fixed shaft portion; and a speed change operation wire is wound around the wire reel portion. transmission switching device.