JPS6280190A - 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 (Industrial Field of Application) The present invention is a device mainly suitable for bicycle transmissions, which can perform stepless transmission of speed by air feed meshing with internal ratchets. 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) The above-mentioned conventional device is provided with a speed increasing device using a ratchet and a pawl in two stages in order to increase the speed increasing ratio. However, this transmission device using ratchets and pawls has a large speed increasing ratio (it is difficult to do so, so even if it is two-stage, the speed increasing ratio may still be insufficient, and the drive range during speed increasing When relaying the load on the winter melon sequentially, if there is a gap between the tooth tips of the driving ratchet and the driven pawl, shock and noise will occur when the driven pawl changes due to the gap. There was a problem in that the amplification was further amplified when the device was constructed in two stages.

7 The present invention has been made to solve the above-mentioned problems, and its purpose is to increase the speed increasing ratio of this type of continuously variable transmission and to reduce relay shock and noise during speed increasing driving. Furthermore, even when this relay shock prevention mechanism is provided, reverse rotation of the pedals, which is peculiar to bicycles, can be tolerated without putting stress on each part.

(Means for Solving the Problems) In order to achieve the above-mentioned object, in the present invention, a plurality of rows of internally toothed ratchet rings are arranged in parallel on the inner periphery of the drive rotating member at the input end via a one-way clutch, Planetary rollers each having a large diameter portion and a small diameter portion are rotatably fitted to a plurality of circumferences of the drive rotating member, and an outer ring is fitted to the inner circumference of a fixed ring fixed to the frame via a one-way clutch. The large diameter portion of the planetary roller is pressed against the inner peripheral surface of the outer ring, and the small diameter portion of the planetary roller is pressed against the outer peripheral portion of the inner ring fitted into the stepped portion of the internally toothed ratchet ring. Each of the rings is frictionally joined to the internally toothed ratchet ring, and the bases of the plural rows of pawls that mesh with the internally toothed ratchet are pivotally supported on a carrier rotatably provided on an eccentric cam whose eccentricity can be freely adjusted with respect to the central axis. A continuously variable transmission device is constructed by combining a continuously variable transmission device made up of the following: and a planetary gear type speed increasing device.

(Function) As described above, in the present invention, a continuously variable transmission device using a ratchet and pawl is combined with a planetary gear type speed increasing device that can easily obtain a speed increasing ratio, so a continuously variable transmission device with a large speed increasing ratio is obtained. be able to.

In addition, continuously variable transmission devices using ratchets and pawls tend to generate shocks and noises, and especially when they are made into two stages like the conventional device described above, there is a risk that the shocks and noises will be amplified. According to , the first stage continuously variable transmission is equipped with a relay shock prevention mechanism using planetary rollers, and the second stage speed increasing device is a planetary gear type speed increasing device, which reduces relay shock and noise during speed increasing driving. can be significantly reduced.

Furthermore, in the present invention, the outer ring is fitted into the inner circumferential part of the fixed ring via a one-way clutch, and the large diameter part of the 't1M roller is pressed against the inner circumferential surface of this outer ring. When the pedal is reversed, the outer ring rotates freely due to the action of the one-way clutch. Therefore, there is no risk of stress being applied to each part of the device.

(Example) Hereinafter, an example in which the present invention is applied to a continuously variable transmission for a bicycle will be described with reference to the drawings.

In the figure, 1 is the bicycle frame chain stay, 1a is the rear claw,
2 is a rear wheel hub shaft fixed to the rear pawl 1a with a lock nut 3; 4 is a rear wheel hub rotatably fitted through 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 axle 2 on the right side in FIG. The outer eccentric cam 9 is rotatably fitted. 10 is a worm that meshes with this worm wheel 8, Ila is an inner wire fixed to this worm 8, and llb is its outer 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 fitted to the outer periphery of the outer eccentric cam 9 via the hair ring 13.

Further, 14 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 15, 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 one-way 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
The bases of the claws 22 and 23 in multiple rows (four in this embodiment) each meshing with the carrier 1a are connected to the carrier 1a.
They are arranged and pivoted alternately on the left and right sides via bins 24 (see FIG. 3(a)) on the outer circumference of the second cylindrical portion 12a. Also 2
5 always ratchets the tips of the claws 22 and 23 to the ratchets 20a and 21.
A transmission gear 28 has an internal gear 26 that is a spring for press-contacting the gear 12b of the carrier 12 and meshes with the gear 12b of the carrier 12, and has an internal gear 27 identical to the internal gear 26 integrally formed back to back. is rotatably provided concentrically with the inner eccentric cam 7 via a ring 29, and the internal gear 27
A continuously variable transmission is constructed by rotatably disposing a gear 30 meshing with the rear wheel hub shaft 2 via a hair ring 31.

In addition, as shown in FIGS. 1 and 3, notches are provided at multiple locations on the circumference (in this embodiment, three locations at three equal positions on the circumference) of the cylindrical portion 15 of the sprocket 15, which is the drive rotation member on the input side. A planetary roller 3 having a large diameter part 32 and a small diameter part 32 concentrically protruding from both sides of the large diameter part 32a.
2 are rotatably fitted into the notches 15b, respectively, and the outer ring 33 circumscribing the large diameter portion 32a of these Ef star rollers 32 is fitted into the inside of the fixed ring 35 through the one-way lathe and chi 34. , this fixing ring 35 is
As shown in the figure, it is fixed to the chain stay 1 via a fixing plate 35a.

The one-way Kura Nochi shown in FIGS. 1 and 3(a).
34, a spring steel wire is wound around the outer periphery of the outer ring 33 multiple times (twice in this embodiment), and one end portion 3
4a to the fixing ring 35 and the one-way clutch spring 3
4b is formed.

In this way, in FIG. 3(a), the outer ring 3
3 is prevented from rotating in the direction of arrow A, and rotation in the opposite direction to arrow A is allowed.

In addition, the one-way clutch notch shown in FIG.
A pawl 34c that engages with a ratchet 33a is pivotally supported on a fixing ring 35, and a spring 34d presses the pawl 34c against the ratchet 33a.

b Also in this case, rotation of the outer ring 33 in the direction of arrow A can be prevented, and rotation in the opposite direction can be allowed.

Further, in the case shown in FIG. 3(c), an elastic ring 34 made of an elastic material such as rubber is disposed between the outer ring 33 and the fixed ring 35.
e is press-fitted. In this case, the elastic ring 349 does not act as a complete one-way clutch, but the outer ring 349
3 in the direction of arrow A can be prevented to some extent by the frictional force Fj, and rotation in the opposite direction to arrow A can be allowed although there is some resistance. Therefore, depending on the case, it may be arranged as shown in FIG. 3(c).

In addition, the inner ring 36 is connected to the internal tooth ratchet ring 20.
．． At the same time, the outer peripheral surface of each internal tooth ring 36 is pressed against the small diameter part 32b of the planetary roller 32, and the large diameter part 32a of the planetary roller 32 is also fitted into the stepped part provided on the opposite side of the planetary roller 32. It is pressed against the inner peripheral surface of the outer ring 33 to constitute a relay shock prevention device.

Further, as shown in FIG. 1, the cylindrical portion 15a of the sprocket 150, which is the rotating member on the input side, is further extended to form an internal gear 37 (see FIG. 6) at the end of the extended cylindrical portion 15c. A plurality of (four in this embodiment) planetary gears 38 meshing with the internal gear 37 are rotatably supported by a shaft 39 on one side of the gear 30 as a 'M star carrier, respectively. A sun gear 40 that meshes with the rear wheel hub shaft 2 is rotatably provided to the rear wheel hub shaft 2 via a bearing 41 to constitute a planetary gear type speed increasing device.

Also number 1. ．． 7.8 shows a reverse input permitting device for the above-mentioned continuously variable transmission, in which a cylindrical pawl carrier 42 is integrally formed with the sun gear 40, and this pawl carrier 420 is integrally formed with the sun gear 40.
A notch 42a is provided in the cylindrical portion, and a pawl 43 is swingably supported within the notch 42a by a pin 44, and internal teeth are engaged with the outwardly projecting end of the pawl 43 when the bicycle rotates forward. A ratchet ring 45 having a ratchet 45a is fixed to the rear wheel hub 4, and a ring-shaped pawl spring 46 is fitted into an annular groove 42b provided on the outer peripheral surface of the pawl carrier 42, so that the outer end of the pawl 43 is always It is biased to engage with the internal ratchet 45a.

In addition, an irreversible cam 48 is fitted to the rear wheel hub shaft 2 on the left side of the sun gear 40 shown at t and -J in FIG. One end portion 49a of a substantially L-shaped lever claw 49 is engaged with the concave portion 48a, and the lever claw 49 is pivotally supported on the claw carrier 40 via a shaft 50, and the other end portion 49b of the lever claw 49 is engaged with the recessed portion 48a. is engaged with the inside of the inner end of the claw 43 to constitute a reverse input permitting device.

Next, the operation of the embodiment of the present invention constructed as described above will be explained. First, to explain the transmission sequence, a 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 throat 15 is controlled by an internal tooth latch J1 via a one-way clutch 19. '7 Trings 20 and 21, and then ratchets 20a and 21a, pawls 22 and 23, and pin 2.
4 to the carrier 12. When the carrier 12 rotates, the gear 12b rotates, and as shown in FIG. 4, the transmission gear 28 rotates via the internal gear 26 that meshes with the gear 12b, and as shown in FIG. The gear 30 rotates around the rear wheel hub shaft 2 by meshing with the gear 30.

1 to 5 show the case where the outer eccentric cam 9 is in the maximum eccentric state, but by rotating the worm 10 via the inner wire lla, the outer eccentric cam 9 is When the eccentric cam 9 is rotated by 180 degrees, the outer peripheral surface of the outer eccentric cam 9 becomes concentric with the rear wheel hub shaft 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 rotating in the direction of arrow B in the figure, each ratchet ring 20.21 and pawl 22.23 rotate integrally via the one-way clutch 19, so the gear ratio in this case is 1:1.

Further, when the outer eccentric cam 9 is brought to the maximum eccentric state as shown in the figure by operating the inner wire Ila, the rotation of the sprocket 15 in the direction of arrow B is transmitted to the internal toothed ratchet ring 20, 21 via the one-way clutch 19, and the ratchet ring 20 transmits rotation to the carrier 12 through the pawl 22, and the ratchet ring 21 transmits rotation to the carrier 12 through the pawl 23.
transmits rotation to.

If the outer eccentric cam 9 is eccentric, as shown in Fig. 3 (
Since the speed increase rate by the claws in the driving range C of a) (in this case, there are eight claws, the angle is 45 degrees divided into eight equal parts of 360°) is the highest, the carrier 12, which is a driven rotating body, is driven by this claw. The other pawls slide and rotate in the direction of the arrow with respect to each ratchet 20a, 21a of the ratchet ring 20.21.

Then, when the pawl moves out of the drive range C and the third pawl enters the drive range C, the speed is increased and driven via that pawl.
The transmission pawl is sequentially replaced by the succeeding pawl.

The gear ratio (speed increase ratio) in this case is the center 0 of the rear wheel hub axle 2.
．． It is the ratio of the angle θ1, which is the drive range of the pawl, with the center o2 of the outer eccentric cam 9 as the base point, and the angle θ2, which is the drive range of the pawl, with the center o2 of the outer eccentric cam 9 as the base point.

Next, the action of the N star roller 32 will be explained.

That is, when the sprocket 5, which is the rotating member on the input side, rotates in the direction of arrow B in FIG. 2, the planetary rollers 32 revolve in the direction of arrow A in FIG. The M star roller 32 rotates in the direction of arrow E due to the frictional resistance caused by the pressure contact between the portion 32a and the outer ring 33. In this case, the outer ring 33 is the one-way clutch 3
It is fixed to the fixing ring 35 by the action of 4. The revolution and rotation of the planetary roller 32
It is transmitted to the inner ring 36 via the small diameter portion 32b of No. 2. In this case, the rotation of the inner ring 36 is increased by about 1.5 times the rotation of the sprocket 15 at the input end, so
The internally toothed ratchet ring 20, 21 which is frictionally connected to the inner ring 36 also rotates at an increased speed. Therefore, at the time of the transmission relay of the driven pawls 22 and 23, the ratchet 20a,
Even if there is a gap between the tooth tips of the tooth tips 21a and the pawls 22.23, the ratchets 20a, 21a catch up with the pawls 22.23 immediately due to the accelerated rotation of the internally toothed ratchet ring 20.21, so that there is a gap between the tooth tips. The gap disappears.

Note that while the latches 7) 20a, 21a and the pawls 22, 23 are fully engaged and driven, the planetary roller 32 appropriately slips on each contact member and absorbs the speed difference between each member.

Next, as mentioned above, the gear 30, which is a planetary carrier,
When rotated in the direction of arrow F in FIG. 5, each planetary gear 38 revolves in the direction of arrow G in FIG. 6 via shaft 39. At this time, the internal gear 37 is also rotating in the direction of the arrow H slower than the revolution speed of the arrow G, together with the sprocket 15.
The planetary gear 38 rotates in the direction of the arrow (■). Therefore, the sun gear 40 rotates at an increased speed as shown by the arrow J due to the revolution of the planetary gear 38 in the direction of the arrow G and the rotation in the direction of the arrow (■). When the sun gear 40 rotates, the pawl carrier 42 integral therewith rotates in the direction of the arrow in FIG.
．． Pawl 43, internal ratchet 45a, ratchet ring 4
The bicycle travels by rotating the rear wheel hub 4 in the direction of the arrow via 5.

In this case, when the pawl carrier 40 rotates in the direction of the arrow, the irreversible cam 48 also rotates in the direction of the arrow M via the lever pawl 49.
This rotation is allowed by the action of the one-way clutch 47.

On the other hand, when the rear wheel hub 4 rotates in the direction of arrow N in FIG. 7 due to the bicycle moving backwards, that is, when a reverse input is applied, the ratchet ring 45 also rotates in the direction of arrow N. 43, pawl carrier 4 via pin 44
0 also tries to rotate in the direction of arrow N. Therefore, the irreversible cam 48 attempts to reverse in the direction of arrow 0 via the lever pawl 49, but this irreversible cam 48
As a result, the lever claw 49, in which the concave portion 48a of the irreversible cam 48 and one end portion 49a are engaged, rotates in the direction of arrow P in FIG. 49b pushes out the inner end of the pawl 43 against the pawl spring 46, so the outer end of the pawl 43 rotates in the direction of arrow Q in FIG. 8 and is removed from the internal ratchet 45a. Therefore, the rear wheel hub 4 can freely rotate in the direction of arrow N in FIG. Therefore, the reverse input is no longer transmitted to the speed increasing and changing transmissions.

In addition, on a bicycle, the rider often rotates the pedals in the opposite direction, but in the device of the present invention, the fixing ring 35
The outer ring 33 is connected to the inner circumference of the ring via a one-way clutch 34.
The large diameter portion 32a of the planetary roller 32 is pressed into contact with the inner circumferential surface of the outer ring 33. When the pedal is reversed, the sprocket 15 and its cylindrical portion 15a are aligned with the arrows in FIGS. 2 and 3. Even if it rotates in the direction R, the outer ring 33 is free to rotate in the direction of the arrow R due to the action of the one-way clutch 34, so it interlocks with the planetary roller 32 without difficulty.

Therefore, in the device of the present invention, even if the pedal is reversed, no large resistance is generated and stress is not applied to the various parts of the device, resulting in improved durability.

(Effects of the Invention) As described above, the present invention combines a continuously variable transmission device using a ratchet and pawl with a planetary gear type speed increasing device that can easily obtain a speed increasing ratio. The excellent effect of being able to obtain

In addition, continuously variable transmission devices using ratchets and pawls tend to generate shocks and noises, and especially when they are made into two stages like the conventional device described above, there is a risk that the shocks and noises will be amplified. According to the above, the first stage continuously variable transmission is equipped with a relay shock prevention mechanism using a TL star roller, and the second stage speed increasing device is a planetary gear type speed increasing device, thereby reducing relay shock and noise during speed increasing driving. This also has the effect of being able to significantly reduce.

Further, according to the device of the present invention, even when the bicycle pedals are rotated in the reverse direction, a large resistance is not generated and the device does not put stress on the various parts of the device, so that the durability of the device can be improved.

[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 showing a part of FIG. Figure 3 (b
) and (c) are partial sectional views showing other embodiments of the one-way clutch, FIG. 4 is a sectional view taken along IV-iV in FIG. 1, FIG. 5 is a sectional view taken along V-V in FIG. 1, and FIG. The figure is a cross-sectional view taken along the line ■-vr in FIG. 1, FIG. 7 is a cross-sectional view taken along the line ■-■ in FIG. 1, and FIG. 8 is an explanation of the operation V in FIG. 1... Chain stay 2... Rear wheel hub shaft (center shaft) 3
...Rock Nano l-4...41 Wheel/S 7'7・
...Inner eccentric cam 9...Outer eccentric cam 12.
...Carrier 15... Sprocket (driving rotating member at the input end) 18
...Che 7 19...One-way clutch 20
．． 21... Internal tooth ratchet ring 22.23...
Pawl 28... Transmission gear 30... Gear (planetary carrier) 32... Planetary roller 32a... Large diameter portion 32
b...Small diameter part 33...Outside link 34
... One-way clutch 35 ... Fixed link 36
...Inner ring 37...Internal gear 38...
・& Star gear 40... Sun gear Fig. 3 (b) (C) 20 (Inner eyelid 4 yF/Shoes Fig. 1 Fig. 2 Fig. 4 Fig. 5

Claims (1)

[Claims] 1. A planetary planet in which a plurality of rows of internally toothed ratchet rings are arranged in parallel on the inner periphery of a driving rotating member on the input side via a one-way clutch, and each of the driving rotating member has a large diameter portion and a small diameter portion at multiple locations on the circumference. A roller is freely rotatably fitted, an outer ring is fitted into the inner circumference of a fixed ring fixed to the frame via a one-way clutch, and the large diameter portion of the planetary roller is pressed against the inner circumference of this outer ring. , the small diameter portion of this planetary roller is pressed against the outer peripheral surface of the inner ring fitted to the stepped portion of the internally toothed ratchet ring to frictionally join the inner rings to the internally toothed ratchet ring, respectively, and mesh with the internally toothed ratchet. This is a combination of a continuously variable transmission in which the bases of multiple rows of pawls are rotatably supported by an eccentric cam whose eccentricity can be adjusted with respect to a central axis, and a planetary gear type speed increaser. Continuously variable transmission.