JPS6280189A - Non-stage transmission - 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 is an automatic transmission device which is mainly suitable for bicycle transmissions, and which can transmit variable speeds 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, the Japanese Patent Publication No. 34-172
There is one disclosed in Publication No. 2.

(Problem to be Solved by the Invention) However, when the above-mentioned conventional device sequentially relays the load applied to the winter melon in the drive range during eccentricity, the speed between the drive ratchet and the driven pawl to which the next load is applied is Due to the difference, a gap is created between the tips of the teeth of the driving ratchet and the driven pawl that are about to be engaged next, which causes a problem in that a shock occurs when the driven pawl is replaced.

The present invention has been made in order to solve the above-mentioned problems, and it is an object of the present invention to significantly reduce relay shock during speed-up driving of this type of continuously variable transmission.

(Means for solving the problem) In order to solve the above-mentioned problem, in the present invention, multiple rows of internally toothed ratchet rings are arranged in parallel on the inner periphery of the drive rotation member on the input side via a one-way clutch. The M! A roller is interposed between the inner circumferential surface of a fixed ring fixed to the frame and the internally toothed ratchet ring, so that it revolves and rotates on its own axis by friction transmission, and the friction transmission caused by the operation of this planetary roller causes the internal toothed ratchet ring to rotate. The base of the multiple rows of pawls that mesh with this internal tooth ratchet is pivoted to a driven rotating body rotatably provided on an eccentric cam that can freely adjust the amount of eccentricity with respect to the central axis to extract output. A continuously variable transmission is constructed.

(Function) Since the present invention is configured as described above, when the rotating member at the input end rotates, the planetary rollers revolve accordingly, so the planetary rollers rotate due to frictional transmission between the planetary rollers and the fixed ring. The internal ratchet ring rotates due to frictional transmission caused by the revolution and rotation of the planetary rollers. In this case, the rotation of the internal ratchet ring is accelerated relative to the rotation of the rotating member on the input side, so even if there is a gap between the tooth tips of the ratchet and the pawl during the transmission relay of the driven pawl, Due to the accelerated rotation of the internally toothed ratchet ring described above, the ratchet immediately catches up with the pawl, thereby eliminating the gap between the tooth tips described above. Therefore, according to the present invention, it is possible to prevent the shock from occurring when the driven claws are replaced.

(Embodiment) Hereinafter, a first embodiment in which the present invention is applied to a continuously variable transmission for a bicycle will be described with reference to FIGS. 1 to 5.

In the figure, 1 is the chain stay of the bicycle frame, 2 is the rear wheel hub axle fixed to the chain stay 1 with a lock nut 3, and 4 is the chain stay of the bicycle frame.
is a rear wheel hub rotatably fitted via a bearing 5,
6 is a spoke.

In this embodiment, an inner eccentric cam 7 is screwed and fixed to the threaded portion 2a of the rear wheel hub shaft 2 on the right side in FIG. The outer eccentric cam 9 is rotatably fitted. 10 is an operating wire wound around this wire reel 8, 10a (see FIG. 2) is its wire end, and 11 is its araku wire.

Further, the flanged cylindrical portion 12a and the gear 12b are integrally coupled to form a carrier 12, and the cylindrical portion 12a of this carrier 12 is applied via a bearing 13 to an outer eccentric force.
- Fits onto the outer periphery of the frame 9.

Further, numeral 4 is a dish-shaped case, and this case 14 is fixed to the rear wheel hub shaft 2 by an inner eccentric cam 7 and a lock nut 3. 15 is a rear wheel sprocket (input side drive rotating member), 15a is a cylindrical part formed integrally with this sprocket 5, and this sprocket 15 is connected to the case 14 and the rear wheel hub 4 via bearings 16 and 17. It is rotatably installed between the 18 is cheno.

Furthermore, a plurality of rows (two rows in this embodiment) of internally toothed ratchet rings 20.21 are arranged in parallel on the inner circumferential surface of the cylindrical portion 15a of the sprocket 15 via a -direction clutch 19, and each of these ratchet rings 20.21 is Ratchets 20a, 21a are provided on the inner peripheral surface, and ratchets 20a, 2
A pin 24 (see FIG. 3) is attached to the outer periphery of the cylindrical portion 12a of the carrier 12 by attaching the bases of a plurality of claws 22, 23 in each row (four in this embodiment) in a double row that engages with the cylindrical portion 12a of the carrier 12.
The left and right sides are placed at different pressures and pivoted through the . Moreover, 25 is a spring for always pressing the tips of the pawls 22 and 23 against the ratchets 20a and 21a.

Also, an internal gear 26 meshing with the gear 12b of the carrier 12
and the same internal gear 2 as this internal gear 26.
7 are integrally formed back to back, and are rotatably provided concentrically with the inner eccentric cam 7 via a bearing 29. A gear 30 that meshes with the internal gear 27 is fixed to the rear wheel hub 4, and the bearing It is rotatably provided on the rear wheel hub axle 2 via the shaft 31.

In addition, as shown in FIGS. 1 and 3, notches are provided at multiple locations on the circumference (in this example, at three locations equally dividing the circumference) of the cylindrical portion 15a of the sprocket 15, which is the drive rotation member on the input side. 15b, cylindrical planetary rollers 32 are rotatably loosely fitted into the notches 15b, and a fixing ring 33 circumscribing these planetary rollers 32 is inserted through a fixing plate 33a as shown in FIG. It is fixedly installed on Chenostee-1.

In addition, a speed increasing ring 34 made of spring steel and an O-ring 35 that fits on the inner periphery of this ring 34 are combined, and are fitted into stepped portions provided on opposite sides of the ratchet rings 20 and 21 to reduce friction. At the same time, the outer peripheral surface of each speed increasing ring 34 is pressed against the planetary roller 32, and the planetary roller 32 is pressed against the inner peripheral surface of the fixed ring 33 by this pressing force. Note that 36 is a separate ring inserted between the internal ratchet rings 20 and 21.

Next, the operation of the apparatus of the present invention constructed as described above will be explained. First, to explain the transmission order, the crank gear rotates via a crank pedal (not shown), and the rotation is transmitted to the sprocket 15 by the chino 18. The rotation of the sprocket 5 is transmitted to the ratchet rings 20 and 21 through internal teeth through the one-way clutch 19, and then to the ratchet rings 20 and 21.
It is transmitted from Oa and 21a to carrier 12 via claws 22 and 23 and pin 24. When the carrier 12 rotates, the gear 12b rotates, and as shown in FIG. When the wheel 27 and the gear 30 mesh, the rear wheel hub 4 integrated with the gear 30 rotates, and the bicycle runs.

1 to 5 show the case where the outer eccentric cam 9 is in the maximum eccentric state, but when the operating wire 10 is operated and the outer eccentric cam 9 is rotated 180 degrees, the outer circumference of the outer eccentric cam 9 is The surface becomes concentric with the rear wheel hub axle 2. When the outer eccentric cam 9 becomes concentric, the sprocket 15, which is the driving rotating body, and each ratchet ring 20, 21 also become concentric with the rear wheel hub axle 2, so in this state, the sprocket 15, which is the driving side rotating body, becomes the second When rotated in the direction of arrow E in the figure, each ratchet ring 20.21
Since the pawls 22 and 23 rotate integrally, the gear ratio in this case is 1:1.

Further, by operating the operating wire 10, the outer eccentric cam 9 is brought to the maximum eccentric state as shown in the figure.
Rotation in the direction of arrow E is transmitted to the ratchet rings 20 and 21 via the one-way clutch 19, and the ratchet ring 20
transmits rotation to the carrier 12 via the pawl 22, and the ratchet ring 21 transmits rotation to the carrier 12 via the pawl 23.

If the outer eccentric cam 9 is eccentric, the speed increase rate due to the pawls in the drive range F in Fig. 3 (in this case, there are eight pawls, so the angle is 45° divided into 8 equal parts of 360°) is maximum. Therefore, the carrier 12, which is a driven rotating body, is rotated at an increased speed by this pawl, and the other pawls are connected to the ratchet ring 20.
It slides and rotates in the direction of arrow G with respect to each ratchet 20a, 21a of 21.

Then, when the pawl moves out of the drive range F and the next pawl enters the drive range F, it is then driven at an increased speed via that pawl,
The transmission pawl is sequentially replaced by the succeeding pawl.

In this case, the speed ratio (speed increase ratio) is the angle θ1 which is the drive range of the pawl with the center arm of the rear wheel hub shaft 2 as the base point, and the drive range of the pawl with the center 02 of the outer eccentric cam 9 as the base point. a certain angle θ2
The ratio is

Next, the functions of the planetary roller 32 and the speed increasing ring 34, which are the features of the device of the present invention, will be explained.

That is, when the sprocket 5, which is the rotating member on the input side, rotates in the direction of arrow E in FIG. 2, the planetary rollers 32 revolve in the direction of arrow H in FIG. The planetary roller 32 rotates in the direction of the arrow (■) due to the frictional resistance caused by the pressure contact with the planetary roller 33. The revolution and rotation of the planetary roller 32 are transmitted to the speed-increasing ring 34 via the planetary roller 32, and the O-ring 35 rotates almost integrally with the speed-increasing ring 34. In this case, the rotation of the speed increasing ring 34 is accelerated relative to the rotation of the sprocket 15 on the input side. It also rotates at increased speed. Therefore, at the time of the transmission relay of the driven pawl 22□23 described above, even if the ratchet 20a,
Even if there is a gap between the tooth tips of 21a and claws 22 and 23,
Due to the accelerated rotation of the internal ratchet ring 20.21, the ratchets 20a, 21a immediately catch up with the pawls 22.23, thereby eliminating the gap between the tooth tips.

Note that while the ratchets 20a, 21a and the pawls 22, 23 are fully engaged and driven, the planetary roller 32 appropriately slips on each contact member to absorb the speed difference between each member.

FIGS. 6 and 7 show a second embodiment of the present invention, and the same reference numerals as those mentioned above in the figures indicate equivalent parts. The only difference from the first embodiment is that a one-way clutch spring 37 is provided in place of the O-ring 35 of the first embodiment.

In other words, as shown in FIG. (2 times) and inserted, and one end portion 37a thereof is locked to the internal toothed ratchet rings 20 and 21, respectively.

In this way, the rotation of the speed increasing ring 34 in the direction of the arrow J in FIG. The rotation is not transmitted to the internally toothed ratchet rings 20 and 21.

Therefore, in the case of this second embodiment, the operation is the same as that of the first, male side, so the explanation will be omitted.

8 and 9 show a third embodiment of the present invention, and FIGS. 10 and 11 show a fourth embodiment. In the figure, the same reference numerals as the above-mentioned reference numerals indicate equivalent parts. In these embodiments, a friction force imparting member for each planetary roller 32 is provided on the inner surface of the fixing ring 33.

In other words, in FIGS. 8 and 9, an elastic ring 3g made of an elastic material such as rubber is fitted into the inner surface of the fixed ring 33, and an outer ring 39 made of spring steel is attached to the inner circumference of the elastic ring 38. A cylindrical planetary roller 32 is inserted between the inner surface of the outer ring 39 and the stepped portion of the internally toothed ratchet ring 20.21, and the planetary roller 32 revolves and rotates on its own axis, and this operation causes the internal tooth ratchet to rotate.
The increased rotation speed is transmitted to the triflies 20 and 21. Since its operation is similar to that of the previous embodiment, detailed explanation will be omitted.

10 and 11, a one-way clutch spring 40 is provided in place of the elastic ring 38 of the previous embodiment.

In other words, as shown in FIG. 11, this one-way clutch spring 40 is constructed by inserting a spring steel wire between the inner periphery of the fixed ring 33 and the outer periphery of the outer ring 39 multiple times (twice in this embodiment). It is wound and inserted, and its one end 40a is locked to the fixing ring 33.

In this way, rotation of the outer ring 39 in the direction of arrow M in FIG. 11 is prevented, but rotation in the direction opposite to arrow M is allowed.

Therefore, in this case as well, rotation of the sprocket 15, which is a driving rotation member on the input side, in the direction of the arrow M causes the planetary roller 32 to revolve and rotate, thereby transmitting accelerated rotation to each of the internally toothed ratchet rings 20 and 21. can.

The other functions are the same as those of the previous embodiment, so the explanation will be omitted.

(Effects of the Invention) As described above, the device of the present invention rotates each internally toothed ratchet ring at an increased speed by the friction transmission of the cylindrical planetary roller that revolves and rotates on its own axis by friction transmission. It is possible to prevent relay shock from occurring when changing the claws. Therefore, according to the present invention, it is possible to provide a continuously variable transmission device that provides smooth rotation with little relay shock.

[Brief explanation of drawings]

FIG. 1 is a cross-sectional plan view of the device of the present invention, FIG. 2 is a side view taken along the line A-A in FIG. 1, FIG. 3 is a cross-sectional view taken along the line B-B in FIG. 1, and FIG. 1, FIG. 5 is a sectional view taken along line D-D in FIG. 1, FIG. 6 is a cross-sectional plan view of the second embodiment, FIG. 9 is a cross-sectional view of the third embodiment, FIG. 9 is a cross-sectional view of the fourth embodiment, FIG. 10 is a cross-sectional view of the fourth embodiment, and FIG. 11 is a cross-sectional view of the fourth embodiment. 1-Chain stay-2-Rear wheel hub axle 3--Lock nut 4-Rear wheel hub inner eccentric cam 9--Outer eccentric cam 10-Operation wire
12--Carrier 15- Sprocket
18-・Che 719-11 One-way clutch 20.21・-Internal tooth ratchet ring 22.23・-Claw 28-・Transmission gear 30・
- Gear 32 - Planetary roller 32a - Large diameter part 32b - Small diameter part 33 - Fixing ring
34.-Speed-up ring 35...O-link 36...
Separate ring 37... One-way clutch spring 38... Elastic ring 39... Outer ring 4
0... One-way clutch spring Fig. 1 IQ (4r direction club + 2 Fig. 2 Fig. 3 Fig. 5 Fig. 6 Fig. 7 Fig. 8 Fig. 10 Country

Claims (1)

[Scope of Claims] 1. A plurality of rows of internally toothed ratchet rings are arranged in parallel on the inner periphery of the input-side drive rotation member via a one-way clutch, and cylindrical ratchet rings are provided at multiple locations on the circumference of the drive rotation member. A planetary roller is rotatably fitted loosely, and this planetary roller is interposed between the inner circumferential surface of a fixed ring fixed to the frame and the internally toothed ratchet ring, so that it revolves and rotates on its own axis by friction transmission. The internally toothed ratchet ring is rotated by frictional transmission caused by the operation of the roller, and the bases of multiple rows of pawls that mesh with this internally toothed ratchet are rotatably mounted on an eccentric cam whose eccentricity can be freely adjusted with respect to the central axis. A continuously variable transmission that extracts output by pivoting on a rotating body. 2. Fit the O-ring into the stepped part of the internal ratchet ring,
2. The continuously variable transmission device according to claim 1, wherein a speed increasing ring is fitted to the outer periphery of the O-ring, and a cylindrical planetary roller is pressed against the outer periphery of the speed increasing ring. 3. Wrap a spring steel wire multiple times around the stepped part of the internally toothed ratchet ring, and lock one end of the wire to the internally toothed ratchet ring to form a one-way clutch spring. 2. The continuously variable transmission according to claim 1, wherein a speed increasing ring is fitted and a cylindrical planetary roller is pressed against the outer periphery of the speed increasing ring. 4. A patent in which an elastic ring made of an elastic material is fitted into the inner periphery of a fixed ring, an outer ring is fitted into the inner periphery of this elastic ring, and a cylindrical planetary roller is pressed against the inner periphery of this outer ring. A continuously variable transmission according to claim 1. 5. Wrap a spring steel wire multiple times around the outer periphery of the outer ring and lock one end of the wire to a fixed ring to form a one-way clutch spring, and install a cylindrical planetary roller around the inner periphery of the outer ring. The continuously variable transmission according to claim 1, wherein the transmission is brought into pressure contact.