JPS61188289A - Infinitely variable 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 (Industrial Application Field) The present invention is directed to a bicycle gear mounted on the crankshaft side of a bicycle, which can transmit variable speed steplessly by a pawl that engages with an internal ratchet. This invention relates to a gear transmission.

(Prior art) As a conventional device of this type, for example,
There is one disclosed in Publication No. 2.

(Problems to be Solved by the Invention) However, since the above-mentioned conventional device has a single-row pawl feeding mechanism, there is a limit to the number of pawls that can be mounted.
There was a problem in that pulsation was not sufficiently eliminated.

In addition, when the conventional device sequentially relays the load applied to the winter melon in the drive range during eccentricity, due to the speed difference between the drive ratchet and the driven claw to which the next load is applied, the drive ratchet that is about to engage next There is a problem in that a gap is created between the tips of the teeth of the driven pawl, which causes a shock when the driven pawl is replaced.

The present invention has been made to solve the above-mentioned problems, and its object is to significantly reduce pulsation and shock during speed-up driving of this type of continuously variable bicycle transmission.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention provides a plurality of rows of internally toothed ratchet rings on the inner periphery of the input-side rotating member fixed to the crank arm via a one-way clutch. installed in parallel,
The bases of multiple rows of pawls that mesh with the ratchets of this internally toothed ratchet ring can be freely adjusted in eccentricity with respect to the central axis, and are alternately arranged and pivoted on the small diameter cylindrical part of a rotatably provided carrier. , a plurality of rows of internally toothed ratchet knit rings are arranged in parallel on one inner circumference of the large diameter cylindrical portion of this carrier via a one-way clutch, and the bases of the plurality of rows of pawls that mesh with the ratchets of this internally toothed ratchet ring are cranked. A continuously variable bicycle transmission is configured by being pivotally supported by an output rotating member fixed to a gear.

(Function) As described above, in the present invention, since the internal ratchet ring and the pawls are provided in multiple rows, the number of pawls that can be attached can be greatly increased compared to a single row. . Therefore, the pulsation of the transmission force can be significantly reduced.

In addition, the plurality of rows of internally toothed ratchet rings are each provided rotatably in one direction on the drive side member via a one-way clutch, and the claws in the plurality of rows are arranged so as to alternately mesh with the ratchets of the internally toothed ratchet rings. Since the,
It is possible to prevent the shock from occurring when the driven claws are replaced.

(Example) Hereinafter, an example of the continuously variable transmission device for a bicycle according to the present invention will be described with reference to the drawings.

In the diagram, 1 (see Figure 2) is the main pipe of the bicycle frame, 2 is the vertical pipe, 3 is the chain stay, 4 (see Figure 1)
5 is a hanger lug, 5 is a crankshaft rotatably provided with respect to the hanger lug 4, 6 is a crank arm fixed to the crankshaft 5, and 7 is its lock nut.

In this embodiment, an output rotating member 9 is fitted onto the crankshaft 5 via a bearing 8, and a crank gear 10 is fixed to the rotating member 9. 11 is the cheno.

Further, the center 02 of the hollow disc-shaped fixed case 12 (see FIG. 2) is set to the center 0 of the crankshaft 5. It is eccentrically offset by 11 with respect to the main body, and is fixed to the chain stay 3 via the right side of the bracket 13 (see FIG. 2) and bolts 14, etc.

Note that 15 (see FIG. 1) is a ball bearing inserted between the fixed case 12 and the output rotating member 9.
□゛Also, 12 (j!2
=j! A ring-shaped carrier frame 16 having an inner circular hole 16b whose center 03 is eccentric by +) is rotatably fitted into the fixed case 12. 17 is about 12 times the carrier frame 16
In order to rotate the cable by 0 degrees, the operating wire is wound around a groove 16C carved on the outer peripheral surface of the carrier frame 16. 17a is a wire end for fixing the cable end q, and this operating wire 17 is attached to a fixed case. The operating wire 17 is led out through a hole 12a provided in the
by moving the carrier frame 16 approximately 120°.
It is designed to rotate forward and backward.

Also, a large diameter cylindrical portion 18a and a small diameter cylindrical portion 18 concentric therewith.
The large diameter cylindrical portion 18a of the carrier 18 integrally formed with the ball bearing 19 is inserted into the carrier frame 16.
A frying pan-shaped input end rotating member 2 is rotatably fitted through the carrier 18 and encloses the small diameter cylindrical portion 18b of the carrier 18.
0 is fixed concentrically to the crankshaft 5 via the crank arm 6, and a plurality of rows (two rows in this embodiment, but two rows in this embodiment) are connected to the inner circumference of the input end rotating member 20 via a one-way clutch 21. Internal tooth ratchet rings 22, 23 (can be arranged in three or more rows) are arranged in parallel, and each of these ratchet rings 22, 23 has four rows (4 teeth) 22a, 23 on the inner circumferential surface thereof.
a and ratchet) 22 a, 23 a
The bases of the double-row pawls 24 and 25, each of which has a plurality of rows (five in this embodiment) that mesh with the cylindrical portion 18b of the carrier 18, are attached to the outer periphery of the small-diameter cylindrical portion 18b of the carrier 18 via pins 26. 21a is a ball forming the one-way clutch 21, and 21b is its extrusion spring.This one-way club, chi 21, can be used with other clubs using, for example, ratchets and pawls. For 27, the tips of the pawls 24 and 25 are always attached to the ratchet 2.
2a, 23&.

Furthermore, a plurality of rows (two rows in this embodiment) of internally toothed ratchet rings 28 and 29 are arranged in parallel on the inner circumferential surface of the large diameter cylindrical portion 18a of the carrier 18 via a one-way clutch 21 similar to that described above.
Ratchets 28a and 29a are provided on the inner peripheral surface of each of these ratchet rings 28 and 29, and several (5 in this embodiment) ratchets are provided on each side in a double row that engages with the ratchets 28a and 29a, respectively. The base of the claw 30゜31,
The output-side rotating member 9, which is integral with the crank gear 10, is pivotally supported by being arranged alternately on the left and right through pins 32 on the outer circumference of the output-side rotating member 9. For 33, always ratchet the tips of the claws 30 and 31) 28
This is a spring for bringing pressure into contact with a and 29a.

Next, the operation of the apparatus of the present invention constructed as described above will be explained. First, to explain the transmission sequence for the embodiment shown in FIGS. 1 to 4, the crank arm 6 rotates via a crank pedal (not shown), and the rotation is transmitted to the manually rotated member 20. The rotation of the rotating member 20 is transmitted to the internally toothed ratchet ring 22.23 via the one-way clutch 21, and is further transmitted to the pawl 24.25 and pin 26 from the ratchets 22a and 23a.
is transmitted to the carrier 18 via. When the carrier 18 rotates, the internal tooth ratchet is activated via the one-way clutch 21)
IJ song 8, 29 rotates, resulting in type 30, 3L
Rotation is transmitted to the output side rotating member 9 and the crank gear 10 via the pin 32.

That is, in this device, there are two transmissions, a first stage transmission by the pawls 24.25 and a second stage transmission by the pawls 30.31.
It will be transmitted through a set of transmissions.

1 to 3 show the carrier 18 via the carrier frame 16.
is in the maximum eccentric state, but when the operating wire 17 is operated to rotate the carrier frame 16 by 120 degrees from the state shown in FIG. 3 to the state shown in FIG. 4, the state shown in FIG. The center 03 of the carrier 18 is the center 0. of the crankshaft 5.
become concentric with Note that since FIGS. 5 and 6 are explanatory diagrams of the operation, the number of claws is also reduced. Furthermore, since the configurations of the two sets of transmissions are the same, the same drawings will be described. When the carrier 18 becomes concentric with the crankshaft 5 as shown in FIG. The body is arrow C in Figure 5.
When it rotates in the direction of
Since the two rotate integrally, the gear ratio in this case is 1:■.

Further, when the carrier frame 16 is rotated 120 degrees from the state shown in FIG. 5 by operating the operating wire 7 to reach the maximum eccentric state as shown in FIG. The rotation is transmitted to the ratchet rings 22, 23, 28, 29 via the directional clutch 21, and the ratchet rings 22, 28 transmit the rotation to the driven rotating bodies 18b, 9 via the pawls 24.30 in the a row, and the ratchet rings 23, 2
9 is a driven rotating body 18b via pawls 25 and 31 in row b.

9 tells the rotation.

If the carrier 18 is eccentric, the speed increase rate due to the pawl a1 within the drive range E shown in FIG. Therefore, the driven rotors 18b and 9 are rotated at increased speed by this pawl a1, and the other pawls are rotated by the ratchet ring 22,
23.28.29 each ratchet 22a.

It will slide and rotate in the direction of arrow F with respect to 23 a, 28 a, and 29 a.

Then, when the pawl a1 moves out of the drive range E and the pawl b1 enters the drive range E, the pawl b1 is then driven at an increased speed, and the weights a2+ b2 . The transmission type changes to a3+ b3.

The gear ratio (speed increase ratio) in this case is the center 0 of the crankshaft 5.
Angle θ1 is the drive range of the claw with 03 as the base point, and angle θ2 is the drive range of the claw with the center 03 of the carrier 18 as the base point.
The ratio is The maximum speed increasing ratio of this embodiment shown in Figures 1 to 3 is the total of the first stage and the second stage, and the total is approximately 2.
．． It becomes 15.

Note that the speed increase rate transmitted through the claws in the drive range E is not uniform over the entire range of the drive range E, and this appears as pulsations in the transmission force, so the smaller the drive range E, the smaller the pulsations. . In other words, the greater the number of pawls, the smaller the pulsation can be, but in the present invention, the ratchet ring and pawls are arranged in multiple rows, so the number of pawls installed can be reduced compared to the conventional single row. Can be doubled in quantity. Therefore, according to the present invention, pulsations occurring in the transmission system can be significantly reduced.

In addition, with conventional single-row devices, when the pawls in the drive range change, if there is a gap between the tip of the pawl that is being replaced and the tooth surface of the ratchet, this gap causes a shock. there were.

In contrast, in the present invention, a plurality of rows of internally toothed ratchet rings are provided on the drive side member via one-way clutches so as to be rotatable in only one direction, and the pawls of the plurality of rows are arranged alternately between the internally toothed ratchet rings. Since it is arranged so as to mesh with the ratchet, it is possible to prevent the shock from occurring when the driven pawl is replaced.

That is, the pawls a1 in the a row in the driving range E in FIG. 6 are tightly engaged with the ratchet and transmit the driving force from the driving rotary body 20.degree. 18a to the driven rotary bodies 18b and 9.

In this case, the toe speeds of the other pawls bl a2+ b2 + a3 + b3 are all faster than the rotational speed of the crawling ratchet, so they slide and rotate in the direction of arrow F with respect to the ratchet.

and a pawl with a toe speed closest to that ratchet speed,
Since no load is applied to the ratchet rings 22 and 28 of the row A, the ratchet rings 23, 29 of the row B are rotated faster by the friction drive of the pawls of the row B in the clockwise direction in which the one-way clutch 21 does not work. I can do it.

In other words, the power to rotate the ratchet rings 23 and 29 in row b faster than row a is generated by the drag caused by the contact friction of the fast claws b2+h3 in row b, and
The pawl b1 having the slowest speed in the row enters the drive range E in a state in which it is tightly engaged with the ratchets 23a and 29a of the b row before it enters the drive range E, that is, in front of the relay receiving angle. Therefore, the pawls b1 of the row B receive the rotational force of the driving rotors 20 and 13a without any shock due to transfer, and smooth rotation can be obtained by sequentially relaying the rotational force of the rows A and B alternately.

(Effects of the Invention) As mentioned above, in the present invention, since the ratchet of the transmission device installed on the crankshaft of a bicycle is provided with multiple rows of IJ songs and pawls, it can be installed more easily than with a single row. The number of nails can be significantly increased. Therefore, it is possible to obtain the effect that the pulsation of the transmission force can be significantly reduced.

In addition, a plurality of rows of internally toothed ratchet rings are provided on the drive side member via one-way clutches so as to be rotatable in only one direction, and the pawls of the plurality of rows are arranged alternately so as to mesh with the ratchets of the internally toothed ratchet rings. So,
Since it is possible to prevent the shock from occurring when the driven pawls change as described above, the present invention provides a front type continuously variable transmission for a bicycle that provides smooth rotation with less pulsation and shock overall. You can get excellent results.

A brief explanation of the previous episode FIG. 1 is a cross-sectional plan view of the device of the present invention; Figure 2 is a sectional view taken along line A-A in Figure 1. Figure 3 is a sectional view taken along line B-B in Figure 1. Figure 4 is an operational diagram of Figure 2, FIG. 5 and FIG. 6 are action explanatory diagrams.

1... Main pants 2... Standing hump 3... Chain stay 4... Hanger lug 5... Crankshaft
6... Crank arm 9... Output side rotating member (driven rotating body) 10... Crank gear 12... Fixed case 16... Carrier frame 17... Operation wire 18... Carrier □ 18a ...Large diameter cylindrical part (driving rotor) 18b...Small diameter cylindrical part (driven rotor) 20...Input side rotating member (drive rotor) 21...One-way clutch 22, 23... Internal tooth ratchet ring 24.25...
・Claw 28.29...Internal tooth ratchet ring 30.31...
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Claims (1)

[Claims] 1. Multiple rows of internally toothed ratchet rings are arranged in parallel on the inner periphery of the input side rotating member fixed to the crank arm via a one-way clutch, and the bases of multiple rows of pawls that mesh with the ratchets of this internally toothed ratchet ring are The eccentricity can be freely adjusted with respect to the central axis, and they are arranged alternately and pivotally supported on the small diameter cylindrical part of a rotatably provided carrier, and a one-way clutch is connected to the inner periphery of the large diameter cylindrical part of this carrier. A continuously variable transmission device for a bicycle, in which a plurality of rows of internally toothed ratchet rings are arranged in parallel, and the bases of the plurality of rows of pawls that mesh with the ratchets of the internally toothed ratchet rings are pivotally supported on an output side rotating member fixed to a crank gear.