JPS6374787A - Variable speed gear for bicycle - Google Patents

Abstract

(57) [Abstract] 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 transmission device provided on the crankshaft of a bicycle.

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

In addition to this, there are so-called internal transmissions that have both side gears built into the hub of the rear wheel, but they are not widely used.

Further, as a transmission device incorporating a planetary gear mechanism in a crankshaft portion, there is one disclosed in, for example, Japanese Utility Model Publication No. 1988-19.

(Problems to be Solved by the Invention) The present invention relates to a transmission device that incorporates a planetary gear mechanism in the crankshaft portion, similar to the transmission device of Utility Model Publication No. 1988-19, and solves the problems of the conventional device. The purpose of this invention is to provide an even better transmission.

In other words, the conventional device of Utility Model Publication No. 28-19 had problems in that it was limited to three-speed gearing due to the arrangement of the planetary gears, and its structure was complicated, making it difficult to commercialize. Ta.

(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, a plurality of shafts are arranged on the same circumference of a carrier integrated with the crank arm, and each shaft is provided with teeth. A planetary gear formed integrally with multiple rows of gears of different numbers is rotatably fitted, and a sprocket is formed on the outer periphery of an internal gear that meshes with one gear of each of these planetary gears to form a driven rotating body. The driven rotating body is fitted to the carrier via a one-way clutch, and three or more shafts are arranged on the same circumference of the carrier, and each of these shafts is connected to the driven rotating body. A roller supporting an inner circumferential surface is rotatably provided, a plurality of sun gears are provided around a crankshaft and mesh with each of the planetary gears, and a fixed bearing encloses the inner circumference of the sun gear and the crankshaft. A one-way clutch is provided between each of the parts, and one of these one-way clutches can be selectively connected to constitute a bicycle transmission.

(Function) Since the device of the present invention is configured as described above, multi-stage shifting of three or more stages is possible, and the entire transmission device can be structurally made thin without any practical problems. Therefore, according to the present invention, it is possible to easily put into practical use a bicycle transmission device having three or more gear stages, which does not require changing the chain.

In particular, in the present invention, three or more shafts are disposed on the same circumference of the carrier, and each of these shafts is rotatably provided with a roller that supports the inner peripheral surface of the driven rotary body. Support becomes reliable, and meshing and rotation between the internal gear and the tix gear becomes smooth.

(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 chain stay, 4 (see Fig. 1) is a hanger pipe, 5 is a fixed bearing portion that is screwed into the hanger pipe 4 and fixed integrally with the frame and serves as a bearing unit, and 6 is a fixed bearing portion that passes through the fixed bearing portion 5. A crankshaft that can rotate freely,
7 is the ball bearing, 8 is the crank arm fitted on the crankshaft 6, 9 is the nut, and 10 is the hanger pipe 4.
This is a retaining ring for fixing the fixed bearing part 5 screwed into the.

In this embodiment, as shown in FIG. 1, a disc-shaped carrier 11 is fitted in the center part with the boss part of the crank arm 8, and has a gear cover protrusion 11a formed in the outer peripheral part.
Attach the port 12a to the flange portion 8a of the crank arm 8.
(See FIG. 2), and a plurality of shafts 13 (four in this embodiment) are arranged parallel to the crankshaft 6 on the same circumference of the carrier 11 at positions equally divided around the circumference. That is, in this embodiment, protrusions 11b (see FIG. 2) are provided at appropriate heights at four locations on the inner surface of the carrier 11, respectively.
An annular ring plate 14 is applied to these protrusions 11b and fixed by a pole 12b (see FIG. 3), and the shaft 13 is provided to span between the ring plate 14 and the carrier 11.

Also, a plurality of teeth each having a different number of teeth (three in this example)
The planetary gears 15a, 15b, 15c are integrally formed, each of the planetary gears 15 is rotatably fitted to the shaft 13, and one of the planetary gears 15a, 15b, 15c meshes with one gear 15b. The gear 16a and the roller receiving portions 16b and 16C arranged on both sides thereof are integrally formed, and a sprocket 16d and a stepped cylindrical portion are provided on the outer periphery of the gear 16a, so that the driven rotating body 16 is integrally formed.

In this embodiment, in order to facilitate manufacturing, the sprocket 16d is formed separately from the internal gear 16a and the like, and then the two are integrally connected.

Further, a one-way clutch 17 is inserted between an inner stepped portion provided on the inner surface of the outer peripheral portion of the carrier 11 and a stepped cylindrical portion of the driven rotating body 16 facing thereto, so that the driven rotating body 16 can be moved to the carrier 11. Rotatably attached in only one direction.

That is, as shown in Fig. 2.4, 17a is a ratchet of the one-way clutch 17 formed on the stepped cylindrical portion of the driven rotor 16, 17b is a pawl pivotally supported on the carrier 11 side, and 17c is this pawl. This is a spring that biases the ratchet 17b in the direction of meshing with the ratchet 17b. This one-way clutch 17
Of course, other formats are also acceptable.

In addition, in order to support the inside of the driven rotating body 16, three or more (four in this embodiment) shafts 13a parallel to the crankshaft 6 are connected to the carrier 11 and the ring plate 14 on the same circumference. A small diameter roller 18a and a large diameter roller 18b are rotatably provided on each of these shafts 13a, and these rollers 18
a, 18b as the roller receiving stage portion 16b of the driven rotating body 16;
16c to rotatably support the driven rotating body 16.

In addition, a hollow cylindrical wind cylinder 19 is provided on the outer periphery of the fixed bearing portion 5 that encloses the crankshaft 6 with involute serrations 20.
(see FIG. 5), a speed change cylinder 21 is fitted to the outer periphery of this wind cylinder 19, and each gear 15a of the planetary gear 15 is fitted to the outer periphery of this speed change cylinder 21.

Sun gears 22.2 meshing with 15b and 15c, respectively.
3.24, and one-way clutches 25, 26.27 are provided between the inner periphery of these sun gears 22, 23, 24 and the outer periphery of the wind barrel 19, and each of these one-way clutches 25° 26 and 27 can be selectively connected.

That is, 25a, 26a, 27a (see FIG. 6) are the pawls of each one-way clutch 25, 26, 27, and these pawls 25a, 26a.

Each of the 27a is a set of two, and is pivotally supported in a concave notch provided on the outer periphery of the wind cylinder 19 with a phase difference of 180 degrees. FIG. 6(b) shows the one-way clutch 25 for the sun gear 22, FIG. 6(C) shows the one-way clutch 26 for the sun gear 23, and FIG. One-way clutch 27 for 24
This shows that. 25b, 26b, and 27b are ring-shaped springs that always urge the winter melon to rise;
5c, 26c, 27c are sun gears 22.23.24
This is a ratchet formed on the inner periphery of the

The claws 25a, 26a, and 27a are as shown in FIG. 6(b).
(cl, as shown in (d), each is pivotally supported on the outer periphery of the wind barrel 19 with a 60° phase difference.
a, 21b, and 21c are openings provided in the body of the speed change cylinder 21, respectively, where the opening 21a corresponds to the pawl 25a, the opening 21b corresponds to the pawl 26a, and the opening 21c corresponds to the pawl 27a. And these openings 21a, 21b,
21c is a structure in which the reference edges of each opening (clockwise edges a, b, c in FIG. 7 (al)) are arranged in the body of the transmission cylinder 21 with a 60° phase difference as shown in FIG. 7 (al). The lengths of the openings 21a, 21b, and 21c are sequentially longer as 21a < 21b < 21c.In this embodiment, if the opening length is expressed as an angle, 21a is 28 degrees. , 21b is 41°, 21c
is 51°.

In addition, 21d in FIG. 7 is a flange provided on one side (crank arm 8 side) of the speed change cylinder 21, 21e is an annular groove provided on the opposite side, and 21f is a flange on the end edge on the side of this annular groove 21e.
This is a notch recess provided at a location (180'' phase).

Furthermore, FIG. 8 shows details of the shift arm 28 that is integrally connected to the speed change cylinder 21 to perform speed change operations.
28a is a ring portion that fits into the body of the speed change cylinder 21;
Reference numeral b denotes tongues protruding from the inside of the ring portion 28a, and these two tongues 28b are fitted into the notch recesses 21f of the speed change cylinder 21, respectively. 28c is the ring portion 28
It is an arm part that protrudes laterally from the outer edge of a,
Reference numeral 28d denotes a wire guide portion that is continuous with the arm portion 28c and protrudes in the shape of a flange.

28e is a spring locking hole provided in the arm portion 28c, and 28f is a wire locking hole also provided in the arm portion 28c.

This shift arm 28 is shown in FIGS. 1, 3 and 6 (8).
1, the tongue piece 28b is fitted into the body of the speed change cylinder 21 so as to fit into the notch recess 21f, and
A retaining ring 29 is fitted into the annular groove 21e to integrally connect the speed change cylinder 2 and the shift arm 28.

As shown in FIG. 3, the end of the shift operation wire 30 is fixed to the shift arm 28 through the hole 28f, the locking fitting 31, and the set screw 32, and a bracket 33 protruding from the hole 28e and the chainstay 3 A return spring 34 is tensioned between.

Note that 35 shown in FIG. 1 is a washer inserted on the side surface of various rotating members, and 36 is a collar inserted between the carrier 11 and the sun gear 22.

Further, in this embodiment, various dustproof seals made of an elastic material such as soft vinyl chloride resin are provided to close the gaps between the rotating members of the device.

In other words, 37 is a ring-shaped seal that is fitted to the outer circumference of the driven rotating body 16 and whose end edge 37a is fitted into the annular groove 11c formed on the inner surface of the carrier 11; A ring-shaped seal that closes the gap with the driven rotating body 16; 39 a ring-shaped seal that closes the gap between the inner periphery of the ring plate 14 and the outer periphery of the ring portion 28a of the shift arm 28; 40, the fixed bearing portion 5; This is a ring plate-shaped seal that closes between the outer circumference of the shift arm 28 and the inner circumference of the ring portion 28a of the shift arm 28. Note that 41 is a chino that meshes with the sprocket 16d.

Next, the operation of the apparatus of the present invention constructed as described above will be explained. By operating the gear shift operating device (not shown) and pulling the operating wire 30 in the direction of arrow A in FIG. 6(bL) (C1° (d)) When the cylinder is rotated to the maximum counterclockwise direction, the openings 21a, 21b, and 21c provided in the body of the transmission cylinder 21 fit into the fixed bearing part 5. Three sets of six claws 25a provided on the wind barrel 19
, 26a, and 27a are as shown in FIG. 9(a). That is, in this case, the claws 25a, 26a, 27
Since all a are inside the speed change cylinder 21, the ratchet 25
There is no claw that engages with C125c, 27c. All sun gears 22, 23, 24 can therefore rotate freely in this case.

In this state, when the crank arm 8 is rotated in the direction of arrow B in FIG. 2 via a crank pedal (not shown),
A carrier 11 fixed to the crank arm 8 and a ring plate 14 integrally connected to the carrier 11 are connected to the second crank arm 8.
4. Rotate in the direction of arrow C in Figure 5. Therefore, due to the engagement between the pawl 17b of the one-way clutch 17 and the ratchet 17a, the driven rotating body 16 similarly rotates in the direction of arrow C. Therefore, the driven rotating body 16 and the sprocket 16d
Since the crank arm 8 rotates integrally with the crank arm 8 in the direction of arrow C, the bicycle travels by moving the chenno 41 in the direction of the arrow in FIG. 2 and driving the rear wheel (not shown). In this case, the gear ratio between the crankshaft 6 and the sprocket 16d is 1:1.

At this time, since the carrier 11 and the driven rotating body 16 rotate integrally, the planetary gear 15 also revolves integrally with the internal gear 16a meshing therewith.
The sun gears 22, 23, and 24 that are meshed with the gears 15a, 15b, and 15c rotate individually according to their respective tooth ratios, but all of these rotations are interrupted by one-way clutches 25, 26, and 27. It is allowed without any problem because it is in the state of .

The sun gears 22, 23, and 24 are loosely fitted to the outer periphery of the transmission cylinder 21, but in this embodiment, each sun gear is inscribed and meshed with four planetary gears, so the sun The gear does not need to be pivoted by a central axis.

Next, from the state shown in FIG. 9 (al), the operating wire 30
When loosened by one step in the direction of arrow E in Fig. 2, the shift cylinder 2
1 is rotated clockwise in FIG. 2.9 by the action of the return spring 34, and as a result, each opening of the transmission cylinder 21 moves from the state shown in FIG. 9(a) to the position shown in FIG. As a result, the tips of the pair of pawls 27a are exposed in the opening 21c, and as a result, the pawls 27a engage with the corresponding ratchets 27c as shown in FIG. 6(d) by the action of the spring 27b. A one-way clutch 27 between the fixed bearing portion 5 and the fixed bearing portion 5 is connected.

When the crank arm 8 is rotated in the direction of arrow B in FIG. 2 in this state, the planetary gear 15 revolves in the direction of arrow F in FIG. 5 via the carrier 11 and shaft 13.

However, in this case, since only the sun gear 24 is prevented from rotating in the direction of arrow F by the one-way clutch 27, the planetary gear 15 is rotated by the arrow F in FIG. It rotates in the direction of G.

Therefore, the internal gear 16a meshing with the medium diameter gear 15b of the planetary gear 15 rotates at increased speed in the direction shown by arrow H in FIG. 5 by revolution in the direction of arrow F and rotation in the direction of arrow G. This rotation causes the driven rotary body 16 and the sprocket l-16d to rotate together, so that the bicycle travels as described above.

In this case, the speed increasing ratio of the driven rotating body 16 to the crank arm 8 is approximately 1:1.4 in this embodiment.

In this case, the other sun gears 22, 23 are also meshed with the gears 15a, 15b of the planetary gear 15, so they rotate, but the one-way clutches 25, 26 of these sun gears 22, 23 are free. Due to the current situation, no problems will occur.

In this case, the arrow C of the carrier 11 in FIG.
Although the rotation of the driven rotor 16 in the direction of arrow H is faster than the rotation in the direction of
(see Figure 2.4).

Next, from the state shown in FIG. 9(b) described above, the operation wire 30 is
When loosened one more step in the direction of arrow E in FIG. 2, the speed change cylinder 21 further rotates and each opening moves from the state shown in FIG. 9(b) to the position fc) in FIG. 9. Therefore, since the second pawl 26a is also exposed from the opening 21b, the one-way clutch 26 by this pawl 26a is also connected.

In this state, when the crank arm 8 is rotated in the direction of arrow B in FIG. 2, the sun gear 23 is also prevented from rotating in the direction of arrow F in FIG. The gear 15 revolves in the direction of arrow F in FIG. 5 and also rotates in the direction of arrow G, and as a result, the internal gear 16a rotates in the direction of arrow H. However, since the rotation speed of the planetary gear 15 in the direction of arrow G in this case is faster than the rotation speed in the above case by the difference in the number of teeth,
Eventually, the speed increase ratio in this case becomes larger than the previous speed increase ratio.

In this case, the speed increasing ratio in this embodiment is approximately 1:1.6.

In this case, the pawl 27a inside the opening 21c is also attached to the ratchet 2.
7c, in this case the sun gear 24
Since the ratchet 27C rotates in the direction of getting over the pawl 27a, no problem occurs.

Next, as shown in FIG. 9 (from the state of C1, the operating wire 30
When the opening 21a is loosened one more step, the opening 21a becomes as shown in FIG.
1 or in the state shown in FIG. 6(b), the third claw 25a is also exposed from the opening 21a and engages with the ratchet 25c of the sun gear 22 as shown in FIG. 6tb>.

As a result, when the crank arm 8 rotates in the direction of arrow B, in this case, the internal gear 16a rotates in the direction of arrow H due to the revolution of the planetary gear 15 in the direction of arrow F in FIG. 5 and the rotation in the direction of arrow G. do. And in this case planetary gear 1
5 in the direction of arrow G is faster than the rotation speed of the planetary gear 15 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 1:1.9.
It is.

In addition, when decelerating, contrary to the speed increasing operation described above, pull the operating wire 30 in the direction of arrow A in FIG. (C1,
(b) and (a), the gear position is changed to 4.
-3-2-1.

The speed change effect of the speed change cylinder 21 having the openings 21a, 21b, and 21c as in this embodiment is such that when speeding up, three sets of pawls 25a, 26a, and 27a protrude outward from the openings one at a time and engage the corresponding ratchets. This is done by sequentially engaging each other, and during deceleration, the three sets of claws protruding outward from the opening are pulled into the opening one by one.

In other words, both speed change and deceleration can be achieved by simply moving one set of pawls in and out, and there is no need to synchronize and reversely operate the other clutch when operating one clutch, as was the case in the past. It has the advantage of being easy to operate and ensuring reliable operation, without causing slippage or simultaneous meshing.

Further, as shown in FIG. 10, the device of the present invention has a sun gear 22
If the one-way clutch 25 is removed and the collar 42 is fitted to the transmission cylinder 21 in place of the sun gear 22, the transmission function of the fourth stage among the aforementioned transmission stages disappears, and l: 1.1 :i, 4.1 :1.6 three-speed transmission.

Furthermore, as shown in FIG. 11G, if the sun gear 24 and the one-way clutch 27 are also removed and the collar 43 is fitted to the speed change cylinder 21 instead of the sun gear 24, two of the above-mentioned speeds can be set. 1st and 4th gear shifting functions are gone;
It can also be easily converted into a two-speed transmission of 1 and t:t, and 6.

(Effects of the Invention) As described above, the device of the present invention has a
Since only the internal gears 16a are provided, the driven rotating body 16
In addition, the driven rotating body 16 can be reliably supported by the rollers 18a, 18b, etc. Further, the planetary gear 15 includes multiple rows of gears 15a, 15b, and 15c.
It has a structure in which multiple rows of sun gears 22, 23, and 24 are formed integrally with each other and are pivotally supported by the shaft 13 and mesh with these gears 15a, 15b, and 15c, and are arranged around the crankshaft 6. Since the 15 shafts 13 are common, the structure is simplified, and since multiple (four in this example) shafts 13 can be arranged on the circumference, the load sharing between each planetary gear is reduced accordingly. As a result, the entire device can be made thinner, and the number of gears can be increased to three or more (four in this embodiment) without replacing the cheno 41, which is an excellent effect.

In addition, in the transmission system of each gear stage of the device of the present invention, the first stage is connected from the carrier 11 to the driven rotary body 16 via the one-way clutch 17.
The second stage has a sun gear 24, a planetary gear 15c,
The information is transmitted to the driven rotating body 16 via the internal gear 16a, and the third stage is the sun gear 23, the planetary gear 15b, and the internal gear 16a.
The fourth stage is transmitted to the driven rotor 16 via the sun gear 22, the planetary gear 15a, and the internal gear 16a. In other words, in any gear stage, power is transmitted through a linear transmission path orthogonal to the crankshaft 6, and each gear shaft has a dual support structure.
The transmission efficiency of each gear is excellent, and the structure is reasonable in terms of strength, so it is easy to manufacture and has excellent durability.

In particular, in the present invention, three
a roller bearing step portion 16b formed on the inner circumferential surface of the driven rotary body 16, in which more than one shaft 13a is arranged;
Since the rollers 18a and 18b supporting the rotor 16c are rotatably provided, the driven rotating body 16 can be supported reliably, and the internal gear 16a and the planetary gear 15 can mesh and rotate smoothly.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal cross-sectional view of the device of the present invention, Fig. 2 is a side view partially shown in section 1-1 and ■-■ in Fig. 1, and Fig. 3 is a partially cutaway side view. 4 is a partial sectional view along line 1-1 in FIG. 1, FIG. 5 is a sectional view taken along line nn in FIG. 1, and FIG. 6(a) is a main part of FIG. 1. Cross-sectional view, same figure (bl
is its mm-m cross-sectional view, the same figure (C) is its IV-IV cross-sectional view,
The same figure (dl is a V-V cross-sectional view, Figure 7 (al is a front view of the speed change cylinder, Figure (b) is its left side view, Figure (C) is a right side view, Figure 8 (al is a Front view of the shift arm (BL is a side view thereof, FIG. 9(a), (BL, (C1, (dl) is an explanatory diagram of the operation of the shift cylinder and pawl, FIGS. 10 and 11 are views of the present invention) It is a diagram of a modification of the device. 4... Hanger pipe 5... Fixed bearing part 6...
・Crankshaft 8...Crank arm 11...
・Carrier 13.13a...shaft 14...
Ring plates 15, 15a, 15b, 15c ・"Planetary gear 16
a...Internal gear 16b, 16c...Roller receiving part 16d...Sprocket 16...Followed rotating body 17...One-way clutch 18a...Small diameter roller 18b...Large diameter roller 19 ...Wind body 21・
... Speed change cylinder 22.23.24 ... Sun gear 25, 26.27 ... One-way clutch 28 ... Shift arm 29 ... Retaining ring 30 ... Operation wire 34 ... Return spring 37 , 38.39.40
...Seal 41...Chain Figure 1 Figure 4 Figure 8 (a) < Figure 9 (a) (Figure 10 (C) (d) Figure 10 Figure 11 Procedure Amendment January 17, 1985 Commissioner of the Patent Office Kuro 1) Akio Yu 1, Indication of the case 1988 Patent Application No. 218226 2, Name of the invention Bicycle transmission device 3, Person making the amendment Relationship with the case Patent application Person Brideston Cycle Co., Ltd. 4, Agent 1, "Ratchet) 17bJ" in the 4th line of page 7 of the specification.
Ratchet 17a". 2. On page 11, line 19, "Figure 2.3.6" is corrected to "Figure 2.3." 3. "Ratchet) 25c, 25c, 27cj" in the same page 12, lines 7-8.
Corrected to cJ. 4. Correct "Figure 6 (C)" in the attached drawing as shown in the attached correction diagram.

Claims (1)

[Claims] 1. A plurality of shafts are arranged on the same circumference of a carrier integrated with the crank arm, and planetary gears each having a plurality of rows of gears with different numbers of teeth are rotatably fitted to each of these shafts. , a sprocket is formed on the outer periphery of an internal gear that meshes with one of the planetary gears to form a driven rotating body, and this driven rotating body is fitted with the carrier via a one-way clutch. , three or more shafts are arranged on the same circumference of the carrier, and each of these shafts is rotatably provided with a roller that supports the inner circumferential surface of the driven rotating body, and meshes with each of the planetary gears. A plurality of sun gears are provided around the crankshaft, one-way clutches are provided between the inner circumferential portion of the sun gear and a fixed bearing portion surrounding the crankshaft, and one of these one-way clutches is provided. A bicycle transmission device characterized by being selectively connectable.