JPH01218992A - Stepless speedchanger for bicycle - Google Patents

Abstract

PURPOSE:To dissolve the pulsation of the force of transmission by providing rotatably a plurality of ratchet claws provided at one side of a rotary member on the side of input and at one side of a rotary member on the side of output through shock absorbing means consisting of hard elastic bodies and soft elastic bodies. CONSTITUTION:A hollow cylindrical case 12 is also rotated in one body due to the rotation of a crank shaft 5, and then, a ratchet gear 29 is rotated through ratchet claws, and a sprocket 32 which is in one body with the ratchet gear 29 rotates a rear wheel. At this time, the meshing load of ratchet claws 13 and the ratchet gear 29 moves backward claws 13 as the force of restitution is accumulated at the soft elastic bodies 17B of shock absorbing means SA1, and absorption is made. Next, when a wire reel 26 is turned along the annular flange of a fixed can 23 by the operation of a lever, the gear 29 is moved in eccentricity against the crank shaft 5, and the ratio of speed change changes steplessly, and claws 13 move backward as the force of restitution is accumulated at hard elastic bodies 17A by means of the meshing load of the gear 29 and claws 13 of this moment, and shock absorption is made. Thus, the pulsation of the force of transmission can be dissolved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial Field of Application] The present invention relates to a continuously variable transmission device for a bicycle, which is installed on a bicycle and is configured to continuously change speed according to the amount of eccentricity.

[Prior Art] Generally, this type of transmission is configured to continuously change speed transmission by wind feeding that meshes with a ratchet gear. A ratchet, so-called pulsation, occurs in the transmission force due to a gap between the tips of the teeth due to the speed difference between the plurality of ratchet pawls within the drive range.

Therefore, in order to reduce the pulsation,
Publication No. 92 has been proposed.

This reduces the pulsation of the transmission force by providing multiple sets of ratchet gears and ratchet pawls in parallel to greatly increase the number of ratchet pawls.

[Problems to be Solved by the Invention] In the above-mentioned conventional technology, it is necessary to provide multiple sets of ratchet gears and ratchet pawls in parallel, resulting in a large and complicated structure, which poses problems in terms of arrangement and cost. was.

SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a continuously variable transmission device for a bicycle that has a simplified configuration and can effectively prevent pulsation of the transmission force.

[Means for Solving the Problems 1] The present invention is configured such that a ratchet pawl is rotatably provided via a buffer means made of a hard elastic body and a soft elastic body.

[Example] Embodiments of the present invention will be described below with reference to the accompanying drawings.

Figures 1 to 11 show the first embodiment, and in Figures 1 to 7, 1 is the main pipe of the bicycle frame, 2 is the main pipe of the bicycle frame;
A vertical pipe, 3 a chainstay, 4 a bunker lug formed integrally with the bicycle frame, 5 a crankshaft, 6 a crank arm fixed to the crankshaft 5 via a nut 7, 8 a rear wheel, 9 1 is a rear wheel hub axle, 10 is a rear wheel sprocket, and 11 is a chain.

12 is a hollow cylindrical case which is an input side rotating member;
The center of the hollow cylindrical case 12 is fixed to the crankshaft 5 by the rotary nut 7, and the crank arm 6 is integrally formed with the hollow cylindrical case 12. In this case, the crank arm 6 and the hollow cylindrical gauge 12
may be formed separately, and the hollow cylindrical case 12 may be fixed to the crankshaft 5 via the crank arm 6. Reference numeral 13 denotes a ratchet pawl having a plurality of teeth 14, and six ratchet pawls 13 are arranged in parallel at equal intervals within a cylindrical portion 15 consisting of the hollow cylindrical gauge 12 and the benefit body 12A of the gauge 12. Each ratchet pawl 13 has a pivot 16 at the base end.
The spring 17 is wound around the pivot shaft 16 and is biased toward the center of the hollow cylindrical case 12 . Further, as shown in FIGS. 4 to 6, each of the pivot shafts 16 is loosely inserted into a long hole 13F provided in each ratchet pawl 13 in its length direction, and
1 out of 6! 'i 16A is externally packaged, and an annular hard elastic body 17A made of hard rubber or the like is attached to the outer circumferential surface of the outer cylinder 16A, and the outer circumferential surface of the hard elastic body 17A and the long hole 1
An annular soft elastic body 17B made of soft rubber or the like is fitted between the inner peripheral surface of 3F and constitutes a buffer means SA1. 17C is a concavo-convex fitting portion between the hard elastic body 17A and the outer cylinder 16A.

Case 12IPJ of tooth portion 14 of each ratchet pawl 13
A receiving surface 18 having no tooth portion 14 is formed in the @ portion, and this receiving surface 18 is a disk having a circular orbit 19A having the same diameter as a ratchet gear to be described later, which is integrally formed on the inner surface of the hollow cylindrical gauge 12. It is adapted to be guided by slidingly contacting the circumferential surface of the shaped guide portion 19. 20 is a retaining ring of a bearing 21 that rotatably supports the crankshaft 5 within the hanger lug 4, and a hanger retaining nut 22 is screwed onto this retaining ring 20. Reference numeral 23 denotes a disk-shaped fixed cam that is clamped and fixed between the end of the hanger lug 4 and the bunker locking nut 22. An eccentric cam 25 is arranged so as to be rotatable. Also, this eccentric cam 25
A wire reel 26 provided at one end of the cam holder 26A via a cam holder 26A is rotatably fitted into the annular flange portion 24. Further, the eccentric cam 25 is connected to the crankshaft 5.
The center hole 28 has a circular arc surface 27 centered on the point B, and rotates while being guided by the fixed cam 23 with a diagonally lower position on the rear side of the center A as the center B.
is formed in the eccentric cam 25, and the crankshaft 5 is inserted into the center hole 28. Reference numeral 29 denotes a ratchet y, which serves as an output side rotating member and is rotatably provided on a circular cam surface 30 formed on the outer periphery of the eccentric cam 25 via a bearing 31.
A sprocket 32 is screwed and fixed to the end of the ratchet gear 29 on the cam holder 26A side. 33 is a retaining ring of the bearing 31, 34 is a collar interposed between the tooth portion 29A of the ratchet gear 29 and the sprocket 32, and 36 is a circular regulating portion for guiding each ratchet pawl 13.

In addition, the cam presser 23A is provided with an eccentric amount adjuster 41i37.
are connected. In this example, the eccentric fi adjuster #
437 is a wire reel 40 having a manual operation lever 39 on a disc-shaped receiver 38 fixed to the upper side of the main vibrator 1.
is rotatably supported, one end of a pair of wires 41.42 is fixed to the top and bottom of this wire reel 40 via a bin 43.44, and the other end of the wire 41.42 is supported above and below the rear side of the wire reel 26. It is fixed via the bins 43A and 44A. These bins 43, 44, 43A, 44A have wire reels 26°40 with the wires 41 and 42 fixed.
It is fitted and fixed in the hole 45 of.

Furthermore, to explain the side path between the receiving surface 18 of the ratchet pawl 13 and the disc-shaped guide part 19, the disc-shaped guide part 19 has a circular orbit 19A having the same diameter as the ratchet gear 29, and is connected to the crankshaft 5. Hollow cylindrical gauge 12 in a concentric state
It is integrally formed on the inner surface of the housing or is fixed by screws or the like. On the other hand, the ratchet pawl 13 has a receiving surface 18 formed over the entire length on the inner side end of the hollow cylindrical case 12, and the receiving surface 18 is formed on the inner surface end of the hollow cylindrical case 12.
It has a tip receiving surface 18A that extends to the tip of 4.

Further, a circular regulating section 36 made of a ring body having approximately the same diameter as the ratchet gear 29 is integrally and concentrically fixed to the end of the ratchet gear 29 on the side of the disc-shaped guide section 19, and the drive range is The inner ratchet pawl 13 is the ratchet gear 2
9, the receiving surface 18 of the ratchet pawl 13 engages with the circular regulating portion 36 to regulate the depth of engagement between the teeth 14 of the ratchet pawl 13 and the teeth 29A of the ratchet gear 29. is formed.

Next, the operation of the apparatus of this embodiment configured as described above will be explained. First, when the crank arm 6, crankshaft 5, and hollow cylindrical case 12 rotate integrally via the crank pedal 46, the ratchet gear 29 is rotated via the ratchet pawl 13 attached to the hollow cylindrical case 12. A tin rocket 32 rotates integrally with the ratchet gear 29, and the rotation of this sprocket 32 is transmitted to the rear wheel 8 by the chain 11 via the rear wheel tin rocket 10.

FIGS. 8(A) and 8(B) show a case where the ratchet gear 29 is located at the center of the hollow cylindrical case 12 and the centering amount is 0. At this time, the ratchet gear 29 and the disc-shaped guide portion 19 are in a concentric state. Yes, all the ratchet pawls 13 are anastomosed to the ratchet gear 29, and the receiving surface 1 of the ratchet pawl 13 is
8 and the disk-shaped guide portion 19 on the side of the hollow cylindrical case 12, it is held at a constant inclination angle.

As a result, the gear ratio between the crankshaft 5 and the sprocket 32 is 1:1. In this state, crank pedal 4
The meshing load between the ratchet pawl 13 and the ratchet gear 29 that is applied when the hollow cylindrical case 12 is rotated through the shaft 6 causes the ratchet pawl 13 to move backward while accumulating restoring force in the soft elastic body 17B of the buffer means S A l. The meshing load is absorbed by the soft elastic body 17B. Therefore, pulsation of the transmission force in a state where the amount of eccentricity is 0 is effectively prevented. When the lever 39 is manually moved forward from this state, the wire reel 40 rotates clockwise via the disc-shaped receiver 38, and the pair of wires 41.42 and the bins 43, 44, 43A are rotated accordingly. , 44A, the wire reel 26 rotates clockwise along the annular flange portion 24 of the fixed cam 23. This allows the eccentric cam 25 to move integrally with the wire reel 26.
The ratchet gear 29 rotates around a point, and as a result, the ratchet gear 29, which is provided concentrically with the eccentric cam 25, rotates around the hollow cylindrical gauge 1.
2, that is, the crankshaft 5.

In this case, the eccentric cam 25 is guided with the circular arc surface 27 of the center hole 28 and the crankshaft 5 in sliding contact with each other, and the eccentric cam 25
The center A of the crankshaft 5 virtually obtained by the rotation of
The movement locus is an arc C from point A to point A°.

FIG. 9 (A>(B) shows the case where the eccentricity of the hollow cylindrical gauge 12 with respect to the two ratchet gears is at the maximum eccentricity state, and at this time the central cam 25 is centered on the center hole 28 with respect to the point B. The ratchet gear 29 rotates clockwise until the left end contacts the crankshaft 5, and moves integrally with the steel core cam 25.
, 13B. As a result, the ratchet pawl 13A
, 13B are engaged with the two ratchet gears by the biasing force of the spring 17, and the other ratchet pawls 13 are guided apart from the ratchet gear 29 by sliding contact between the receiving surface 18 and the disk-shaped guide portion 19.

And the ratchet pawls 13A and 13B within the drive range.
Since the speed increase rate is the maximum, the ratchet gear 29 is rotated at an increased speed by the ratchet pawls 13A and 13B, and the other ratchet pawls 13 are disengaged from the ratchet gear 29. The ratchet pawl 13A sequentially drives the ratchet gear 29 at an increased speed, such that when the ratchet pawls 13A and 13B move out of the driving range, the adjacent ratchet pawl 13 enters the driving range and drives the ratchet gear 29 at an increased speed.

13B takes over.

Mana, hollow cylindrical case 1 for ratchet gear 29
When the eccentricity of No. 2 is in the middle stage from O to the maximum, the three ratchet pawls 13A, 13B,
The angle of inclination of 13C is smaller than the angle of inclination of ratchet pawls 13A and 13B in FIGS. 8(A) and 8(B). That is,
A virtual gear is formed inside the hollow cylindrical case 12 by the ratchet pawls 13A, 13B, and 13C within the drive range, and the diameter of this gear is determined by the rotation of the eccentric cam 25 by the operation of the lever 39. ratchet pawl 13A,
The gear ratio (speed increasing ratio) of the ratchet gear 29 changes steplessly in response to changes in the inclination angles of the ratchet gears 13B and 13C.

When the face is centered as shown in FIG. 9, the ratchet pawls 13A and 138.13C in the drive range move rearward while accumulating restoring force in the hard elastic body 17A of the buffer means SA1 due to the meshing load with the ratchet gear 29. Then, the pivot 16 is located approximately in front of the elongated hole 13F. As the hollow cylindrical case 12, which is the input rotating member, rotates, the ratchet pawls 13A, 13B, and 13C within the drive range are sequentially replaced, but it is not until the ratchet pawl 13 enters the drive range that it engages with the ratchet gear 29. When they mesh, there is a possibility that the meshing load will be instantaneously transmitted to the hollow cylindrical gauge 12 and transmitted to the pedal side as pulsations. However, in this embodiment, since the buffer means SA+ is provided, the meshing load is not directly transmitted to the hollow cylindrical gauge 12 and the soft elastic body 1
It is absorbed by the hard elastic body 17A via the elastic body 7B, thereby effectively preventing pulsation of the transmission force. Furthermore, due to the speed difference between the plurality of ratchet pawls 13A, 13B, 13C within the drive range, a gap is created between the tooth tips of each ratchet pawl 13A, 13B, 13C, which may cause a shock during rotation. However, due to the buffering means SA+, the gear part is reduced to the ratchet pawl 1 through the elongated hole 13F.
It is absorbed by the movement of 3A, 13B, and 13C, and the above shock is well prevented.

Further, during the eccentric movement, the engagement and disengagement state of the ratchet pawl 13 and the ratchet gear 29 is shown in FIG. 8(A).
, ratchet pawls 13A and 13B within the drive range, as shown in FIG. 9 (A>).

13C is in a state where the receiving surface 18 and the circular orbit 19A are separated and the tooth portions 14 of the ratchet pawls 13A, 13B, and 13C are engaged with the ratchet cap 29, and the ratchet pawl 13 outside the drive range is in a substantially constant inclination angle state. At this point, the ratchet pawl 13 is released from the ratchet gear 29 with the receiving surface 18 and the circular orbit 19A being engaged and held. On the other hand, when the ratchet pawl 13 comes out of the drive range, the tip receiving surface 18A engages with the circular orbit 19A before the teeth 14 of the ratchet pawl 13 and the ratchet gear 29 separate, and the tip of the ratchet pawl 13 engages with the circular orbit 19A. is smoothly removed while being guided in the tangential direction of the two ratchet gears, and when entering the drive range, the ratchet pawl 13 is guided in the tangential direction of the ratchet gear 29 with the tip receiving surface 18A engaged with the circular track 19A. while smoothly interlocking.

Further, as shown in FIG. 7, when the ratchet pawl 13 is disengaged from the receiving surface 18 and the circular orbit 19A, and when the tooth portion 14 of the ratchet pawl 13 and the tooth 29A of the ratchet gear 29 shift to meshing, , the receiving surface 18 is brought into engagement with the circular regulating portion 36, thereby regulating the depth of engagement between the teeth 14.29A. That is, when both teeth 14.29A are in mesh, an appropriate clearance is always formed between the peak of tooth 14 and the valley of tooth 29A, and between the valley of tooth 14 and the peak of tooth 29A. Mutual friction can be suppressed well.

12 and 13 show a second embodiment, in which the same parts as in the above embodiment are denoted by the same reference numerals.A pivot 16 is loosely inserted into the elongated hole 13F of the ratchet pawl 13, and the pivot 16 is The outer cylinder 16A is sheathed, and an annular soft elastic body 17B is attached to the outer cylinder 16A.
A hard elastic body 17A is fitted between the outer peripheral surface of the long hole 13F and the inner peripheral surface of the elongated hole 13F to constitute a buffer means SA2. Then, when the ratchet pawl 13 enters the drive range in the eccentric state and is subjected to the meshing load with the ratchet gear 29 for the first time, the ratchet pawl 13 moves rearward while accumulating restoring force in the hard elastic body 17A, and the meshing load is Hard elastic body 17
Absorbed by A. Further, the caps on the tips of the ratchet pawls 13A, 13B, and 13C caused by the speed difference are similarly absorbed by the hard elastic body 17A, and pulsation of the transmission force is effectively prevented.

Further, even in a state where the amount of eccentricity is 0, the meshing load is absorbed by the soft elastic body 17B as in the above embodiment.

14 to 17 show a third embodiment, in which a pivot shaft 1 is provided in the elongated hole 13F of each ratchet pawl 13.
6 is loosely inserted, and the outer cylinder 16A is mounted on the pivot 16,
An annular hard elastic body 17A is attached to the outer circumferential surface of the outer cylinder 16A, and when the hard elastic body 17A is fitted to the outer circumferential surface of the long hole 13F, the inner circumference of the hard elastic body 17A is A C-shaped soft elastic body 17B is fitted between the surface and the inner circumferential surface on the inner end side of the elongated hole 13F to constitute a buffer means SA3.

Furthermore, in this embodiment, the two ratchet pawls 13.
' is rotatably provided, and these two ratchet pawls 1
The tooth portions 14 and 14' of 3°13' are formed by extending 1/2 pitch of each tooth. This lick above 1ffi means S
In addition to the pulsation prevention effect similar to that of the above embodiment, A3 also provides the following effects.

At the time of eccentricity as shown in FIG.
3.13' is one set, and its teeth 14.14' are one set.
The first lick is made up of 1/2 pitch of each tooth.
As shown in FIGS. 6 and 17, the tooth portion 14 of one of the two sets of ratchet pawls 13DR, 13°DR within the drive range and the tooth portion 29A of the ratchet gear 29. Normally meshed; when the other set is in the rope motion, the gap ru between the tooth portion 14° of the ratchet pawl 13'DR and the m portion 29A of the ratchet gear 29 is
jt/2.

Therefore, as shown in FIG. 16, the direction of trust of the ratchet gear 29 is set as a reference (0°) from the center of the hollow cylindrical gauge 12.
For this, the direction of rotation is (+) and the opposite is (
-), the driving range is as shown in Fig. 16.
The drive range is from 0° to 40° to -53° to 7° (
-) side, and the pulsation is improved accordingly.

Note that the present invention is not limited to the above-mentioned embodiments, and various modifications can be made within the scope of the gist of the present invention. For example, the material and shape of the elastic body may be selected appropriately;
The present invention can also be applied to various transmission devices mounted on the hub axle of the rear axle, such as No. 1, and in short, it can be applied to various transmission devices having a ratchet gear and a ratchet pawl.

[Effects of the Invention] Since the ratchet pawl of the present invention is provided so as to be rotatable via the buffer means made of a hard elastic body and a soft elastic body, the configuration is simplified and pulsation of the transmission force of the ratchet can be effectively prevented. We can provide a continuously variable transmission device for bicycles.

[Brief explanation of the drawing]

1 to 11 show a first embodiment of the present invention.
2 is a perspective view, FIG. 3 is an exploded perspective view, FIG. 4 is a partially cutaway front view of the ratchet pawl showing the buffer means, and FIG. 5 is a sectional view of the ratchet pawl. Figure 6 and 7
The figure is a sectional view of the main part, Figure 8 (A) (B) and Figure 9 (A
)(B) is a cross-sectional view showing changes in the amount of eccentricity, FIG. 10 is a perspective view showing the eccentricity adjustment mechanism, FIG. 11 is a usage state diagram,
2 and 13 show the second embodiment of the present invention, and the first embodiment
Fig. 2 is a partially cutaway front view showing the buffer means, Fig. 13 is a sectional view, Figs. A front view, FIG. 15 is a sectional view showing an eccentric state, and FIGS. 16 and 17 are front views of main parts. 12... Input side rotating member 13... Ratchet pawl 16... Pivot 17A... Hard elastic body 17B... Soft elastic body 29... Output side rotating member SA1, SA2, SA3... Low street means patent
Applicant Nippon Seiki Co., Ltd. Representative Patent attorney Ushiki Examination Patent attorney
Thin 1) Long 4 parts Fig. 1 Fig. 2 / Fig. 6 Fig. 7 Fig. 14

Claims (1)

[Claims] (1) An input side rotating member, an output side rotating member, and the above-mentioned input side,
A bicycle comprising a plurality of rows of ratchet pawls arranged on one side of an output side rotating member and each base side of which is rotatably provided, and the speed is changed by relatively eccentrically moving the input and output side rotating members. A continuously variable transmission for a bicycle, characterized in that the ratchet pawl is rotatably provided via a buffer means made of a hard elastic body and a soft elastic body.