JPH025629B2 - - Google Patents

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a bicycle equipped on the crankshaft side of a bicycle, which can transmit variable speed continuously by a pawl that engages with an internal ratchet. The present invention relates to a continuously variable transmission for use in a vehicle.

(Prior art) As a conventional device of this type, for example,
There is one disclosed in Publication No. 1722.

(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 attached, and as a result, pulsation is not sufficiently eliminated. There was a problem.

Furthermore, when the conventional device sequentially relays the load applied to each pawl in the drive range during eccentricity, the speed difference between the drive ratchet and the driven pawl to which the next load is applied makes it difficult for the drive ratchet to engage next. There was a problem in that a gap was created between the tips of the teeth of the driven pawl and a shock occurred when the driven pawl was replaced.

The present invention has been made to solve the above-mentioned problems, and it is an object of the present invention 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, in the present invention, a plurality of rows of internally toothed ratchet rings are provided on the inner circumference of the input side rotating member fixed to the crank arm via a one-way clutch. are arranged in parallel, and the bases of multiple rows of pawls that engage with the ratchets of this internal tooth ratchet ring,
The amount of eccentricity can be 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. Continuously variable transmission for bicycles is achieved by arranging multiple rows of internal tooth ratchet rings in parallel, and pivoting the bases of the multiple rows of pawls that mesh with the ratchets of the internal tooth ratchet rings to an output side rotating member fixed to a crank gear. Configure the device.

(Function) As described above, in the present invention, since the internal tooth 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. Can be done. Therefore, the pulsation of the transmission force can be significantly reduced.

Further, the plurality of rows of internal toothed ratchet rings are each provided on the driving side member via a one-way clutch so as to be rotatable in only one direction, and the claws of the plurality of rows are arranged so as to alternately mesh with the ratchets of the internal toothed ratchet rings. Therefore, 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, and 4 is the main pipe of the bicycle frame.
(See Figure 1) is a hangarug, 5 is a crankshaft rotatably provided with respect to the hangarug 4, 6 is a crank arm fixed to this crankshaft 5, and 7
is the 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 chain.

Also, the center 0 ₂ (see Fig. 2) of the hollow disc-shaped fixed case 12 is l ₁ relative to the center 0 ₁ of the crankshaft 5.
The chain stay 3 is fixed to the chain stay 3 via a bracket 13 (see FIG. 2), a bolt 14, etc. Note that 15 (see FIG. 1) is a ball bearing inserted between the fixed case 12 and the output side rotating member 9.

Also _{, l 2 (} l ₂
A ring-shaped carrier frame 16 having an inner circular hole 16b whose center 0 ₃ is eccentric by an amount equal to l ₁ ) is rotatably fitted into the fixed case 12 . 17 rotates the carrier frame 16 by approximately 120 degrees.
The operating wire 17 is wound around a groove 16c carved on the outer peripheral surface of the cable, and 17a is a wire end for fixing the end of the cable.The operating wire 17 is led out from a hole 12a provided in the fixed case 12. By moving the operating wire 17 using an operating mechanism (not shown), the carrier frame 16 is reciprocated by about 120 degrees.

Further, the carrier 1 is formed by integrally forming a large diameter cylindrical portion 18a and a small diameter cylindrical portion 18b concentric with the large diameter cylindrical portion 18a.
The large diameter cylindrical portion 18a of the carrier 18 is rotatably fitted into the carrier frame 16 via a ball bearing 19, and the frying pan-shaped input side rotating member 20 enclosing the small diameter cylindrical portion 18b of the carrier 18 is attached to the crank arm 6. A plurality of rows (in this embodiment, two
Although it is a row, it can also be made into three or more rows. ) internal tooth ratchet rings 22 and 23 are arranged in parallel, and ratchets 22a and 23a are respectively provided on the inner circumferential surfaces of these ratchet rings 22 and 23, and the ratchets are double rows that mesh with the ratchets 22a and 23a, respectively, and Plural (5 in this example) claws 2 in each row
The bases of 4 and 25 are arranged and pivotally supported on the outer circumference of the small-diameter cylindrical portion 18b of the carrier 18 via pins 26, alternating left and right. Note that 21a is a ball forming the one-way clutch 21, and 21b is its extrusion spring. The one-way clutch 21 may also be of other types, for example using a ratchet and pawl. Further, reference numeral 27 denotes a spring for always pressing the tips of the claws 24, 25 against the ratchets 22a, 23a.

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. A ratchet 28 is provided on the inner peripheral surface of each ratchet ring 28, 29.
a, 29a, and ratchets 28a,
A pin 32 is attached to the outer periphery of the output-side rotating member 9 that is integrated with the crank gear 10, and the bases of a plurality of claws 30, 31 in each row (five in this embodiment) in a double row that mesh with the crank gear 10, respectively. They are arranged alternately on the left and right and are pivotally supported. Incidentally, reference numeral 33 denotes a spring for keeping the tips of the claws 30, 31 in pressure contact with the ratchets 28a, 29a.

Next, the operation of the apparatus of the present invention constructed as described above will be explained. First, to explain the transmission sequence in 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 input rotating member 20. The rotation of the rotating member 20 is transmitted to the internally toothed ratchet rings 22, 23 via the one-way clutch 21, and further transmitted from the ratchets 22a, 23a to the carrier 18 via pawls 24, 25 and pin 26. carrier 18
When rotates, the internally toothed ratchet rings 28, 29 rotate via the one-way clutch 21, and as a result, rotation is transmitted to the output rotating member 9 and crank gear 10 via the pawls 30, 31 and pin 32.

That is, in this device, the claws 24 and 25
The power is transmitted through two sets of transmissions: a first-stage transmission and a second-stage transmission using pawls 30 and 31.

1 to 3 show the case where the carrier 18 is in the maximum eccentric state via the carrier frame 16, by operating the operating wire 17, the carrier frame 18
When rotated by 120 degrees from the state shown in FIG. 3 to the state shown in FIG. 4, the center ₀₃ of the carrier 18 becomes concentric with the center ₀₁ of the crankshaft 5, as shown in FIG. 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 similar, the same drawings will be described. When the carrier 18 becomes concentric with the crankshaft 5 as shown in FIG.
is concentric with the crankshaft 5, so if the drive rotor rotates in the direction of arrow C in Fig. 5 in this state,
Since the driven rotors 18b and 9 rotate integrally through the one-way clutch 21 and the respective ratchet rings and pawls, the gear ratio in this case is 1:1.

Further, when the carrier frame 16 is rotated 120 degrees from the state shown in FIG. 5 by operating the operating wire 17 to the maximum eccentric state as shown in FIG.
0, 18a in the direction of arrow D through the one-way clutch 21, the ratchet rings 22, 23, 2
8, 29, ratchet rings 22, 28
is connected to the driven rotating body 18 via the pawls 24 and 30 in row a.
Transmit rotation to b, 9, ratchet rings 23, 2
9 is a driven rotating body 18 via pawls 25 and 31 in row b.
Transmit rotation to b and 9.

If the carrier 18 is eccentric, the speed increase rate due to the pawl _a1 within the drive range E in Fig. 6 (in this case, there are six pawls, so the angle is 60 degrees divided into six equal parts of 360 degrees) is Since it is the largest, the driven rotors 18b and 9 are rotated at increased speed by this pawl _a1 , and the other pawls are rotated for each ratchet 22a, 23a, 28a, 29a of the ratchet rings 22, 23, 28, 29. This results in a sliding rotation in the direction of arrow F.

Then, as the pawl a ₁ moves out of the drive range E, the pawl b ₁
When it enters the drive range E, it is now driven at an increased speed via pawl b ₁ , and the transmission pawls are sequentially changed to pawls a ₂ , b ₂ , and b ₃ .

The gear ratio (speed increase ratio) in this case is the crankshaft 5
Angle θ ₁ which is the driving range of the claw with the center 0 ₁ as the base point
and the angle θ ₂ which is the drive range of the pawl with the center 0 ₃ of the carrier 18 as the starting point. The maximum speed increasing ratio of this embodiment shown in FIGS. 1 to 3 is approximately 2.15 in total for the first stage and the second stage.

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.
The smaller this drive range E is, the smaller the pulsation becomes. In other words, the greater the number of pawls, the smaller the pulsation can be. However, in the present invention, since the ratchet ring and pawls are arranged in multiple rows, the number of pawls installed can be reduced compared to the conventional single row. can be more than doubled. 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 can cause a shock. The dot was hot.

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 in the plurality of rows are alternately connected to the internally toothed ratchet rings. Since it is arranged so as to mesh with the ratchet of the ring, it is possible to prevent the occurrence of a shock when the driven pawl is changed as described above.

In other words, the pawls _a1 in the a row in the drive range E in FIG.
The driving force from 18a is transmitted to driven rotors 18b and 9.

In this case, the other pawls b ₁ , a ₂ , b ₂ , a ₃ , and b ₃ are all rotated in the direction of arrow F relative to the ratchet because their toe speeds are faster than the rotational speed of the ratchet. Since no load is applied to pawl _b1 whose toe speed is closest to the ratchet speed, the ratchet rings in row B are in a clockwise rotation direction in which the one-way clutch 21 does not work, rather than the ratchet rings 22 and 28 in row A. 23 and 29 can be rotated quickly by friction drive by the b-row pawls.

In other words, the power to rotate the ratchet rings 23, 29 in row b faster than row a is generated by the pawls in row b.
This is caused by the drag caused by the contact friction of the fast toe speeds of b ₂ and b ₃ , and the slowest speed pawl b ₁ in row b is moved forward before reaching the drive range E, that is, in front of the relay receiving angle. At row b ratchets 23a, 29
Since it enters the driving range E in a state in which it is tightly meshed with a, the pawls _b1 in row b receive the rotational force of the drive rotors 20 and 18a without a transfer shock, and in turn a
Smooth rotation can be obtained by alternately relaying the b-columns.

(Effects of the Invention) As described above, in the present invention, the ratchet rings and pawls of the transmission device installed on the crankshaft of the bicycle are provided in multiple rows, making it easier to install them than with a single row. The number of claws can be significantly increased. Therefore, it is possible to obtain the effect that the pulsation of the transmission force can be significantly reduced.

Further, 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 alternately engaged with the ratchets of the internally toothed ratchet rings. Since the driven pawls are arranged in the same direction, it is possible to prevent the occurrence of shock when changing the driven pawls. Accordingly, according to the present invention, the front type stepless rotation of the bicycle, which provides smooth rotation with less pulsation and shock as a whole, can be achieved. This provides an excellent effect of providing a transmission.

[Brief explanation of drawings]

Fig. 1 is a cross-sectional plan view of the device of the present invention, Fig. 2 is a sectional view taken along line AA in Fig. 1, Fig. 3 is a sectional view taken along BB in Fig. 1, and Fig. 4 is an explanation of the operation in Fig. 2. FIG. 5 and FIG. 6 are action explanatory diagrams. 1...Main pump, 2...Vertical pump, 3...Chain stay, 4...Hanger jack, 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 portion (driving rotating body), 1
8b... Small diameter cylindrical portion (driven rotating body), 20... Input side rotating member (driving rotating body), 21... One-way clutch, 22, 23... Internal toothed ratchet ring, 24,
25...Claw, 28, 29...Internal tooth ratchet ring,
30, 31...nails.

Claims (1)

[Claims] 1. A plurality of rows of internal tooth 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 the plural rows of pawls mesh with the ratchets of the internal tooth ratchet rings. of,
The amount of eccentricity can be 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. A continuously variable bicycle transmission device in which multiple rows of internal tooth ratchet rings are arranged in parallel, and the bases of multiple rows of pawls that mesh with the ratchets of the internal tooth ratchet rings are pivotally supported on an output side rotating member fixed to a crank gear. .