JPH0156027B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Technical Field) The present invention relates to a speed change operating device and a reverse input permitting device for a continuously variable bicycle transmission installed on the crankshaft of a bicycle.

(Prior Art) The present applicant previously developed a planetary gear type continuously variable transmission suitable as a continuously variable transmission for bicycles (Japanese Patent Application No. 1983-
No. 245239, Patent Application No. 1983-69906)
139953, Japanese Patent Application Laid-open No. 60-213590), these devices have the following as ancillary equipment:
A gear shift operating device and a reverse input permitting device are required.

(Objective) The present invention has been made from the above-mentioned viewpoint, and it is an object of the present invention to enable the practical use of the above-described planetary gear type continuously variable transmission by providing a speed change operating device that can also be used as a reverse input permitting device. The purpose is to

(Structure) In order to achieve the above-mentioned object, in the present invention,
A carrier is fixed to the crankshaft of a bicycle, multiple planetary nuclei are rotatably supported on this carrier, and a planetary gear is fitted to each of these planetary nuclei via a one-way clutch so that it can rotate in only one direction. An eccentric shifter having a circular orbit for guiding a rocking pin protruding from an eccentric position of the planetary core and having a gear formed on its outer periphery is connected to the eccentric shifter through an eccentric core plate having a gear concentric with the crankshaft formed on its outer periphery. A sun gear and a crank gear are integrally formed so that the amount of eccentricity can be freely adjusted with respect to the crankshaft and meshes with each of the planetary gears, respectively,
In a bicycle equipped with a continuously variable transmission that outputs output through a crank gear, a support shaft is fixed to the bicycle frame parallel to the crankshaft, and the end of the bracket is fitted onto this support shaft. , a wire reel and a pinion integrally formed, and one end of the gear case are fitted onto the support shaft 36, and the gear case has a one-way clutch on its inner periphery and is fixed to mesh with the gear of the eccentric core plate. A side gear is inserted, and a sector gear that meshes with the pinion is fixed to one end of a shaft passing through the other end of the gear case, and an intermediate gear that meshes with the stationary side gear is rotatably fitted to the shaft inside the gear case. The base of the swinging arm is fitted and fixed to the shaft protruding outside of the gear case, and a shaft is provided protruding from the free end of the swinging arm, and the shaft meshes with the intermediate gear, and the eccentric A moving gear that meshes with a shifter gear is rotatably fitted, the shaft is urged by a spring force to rotate toward the continuously variable transmission, and an operating wire is wound around the wire reel. The present invention constitutes a speed change operating device and a reverse input permitting device of a continuously variable bicycle transmission.

(Example) An example of the present invention will be described below with reference to the drawings. In the diagram, 1 is the main pipe of the bicycle frame, 2
A vertical pipe, 3 a chain stay, 4 a hanger lug, 5 a crankshaft, 6 a crank arm fitted onto the crankshaft 5, and 7 its lock nut. Further, 8 is a rear wheel, 9 is a rear wheel hub axle, 10 is a rear wheel sprocket, and 11 is a chain.

In this embodiment, a hollow disk-shaped carrier 12 (12a is a lid plate that can be attached to and detached from the carrier body using screws 12b, etc.) is fixed to the crankshaft 5 via the crank arm 6, and a plurality of ( In this embodiment, six (6) stepped cylindrical planetary nuclei 13 are rotatably supported via a shaft 14 at equally spaced positions on the circumference. Note that 15 is the bearing.

In this case, the stepped cylindrical planetary nuclei 13 are arranged such that their large diameter portions 13a and small diameter portions 13b are alternately reversed by 180° between adjacent planetary nuclei. A ring-shaped planetary gear 16 is fitted onto the outer periphery of the large diameter portion 13a of each of these planetary cores 13 via a one-way clutch so that it can rotate in only one direction, and these planetary gears 16 are connected to the crankshaft. 5 in the axial direction.

That is, in this embodiment, three planetary gears 1
6 is disposed on the outer side of the carrier 12, and the remaining three planetary gears 16 are disposed on the inner side of the carrier 12 so as not to interfere with each other.

Further, the one-way clutch may be of any type, but in this embodiment, as shown in FIGS. 5 and 6, a ratchet 17 is formed on the inner peripheral surface of the ring-shaped planetary gear 16, and Large diameter part 1
3a is provided with a pawl 8 that engages with the ratchet 17 to prevent rotation in only one direction, and is biased by a spring 19 so that the pawl 18 engages with the ratchet 17.

Further, a swing pin 20 parallel to the shaft 14 is provided protruding from one side surface (in this embodiment, the inner surface) of each planetary nucleus 13 at an eccentric position with respect to the shaft 14 . The notch 12c provided in the cover plate 12a of the carrier 12 in FIG.
This is to allow each of the swing pins 20 to protrude to the outside of the carrier 12 and to allow the swing pins to swing.

Further, as shown in FIGS. 2 and 3, a sun gear 23 that meshes with each of the planetary gears 16 is formed at one end of a shaft tube 22 that is rotatably fitted to the crankshaft 5 via a bearing 21. With,
Two circular stepped portions 24a, 24 are provided at the other end of the shaft tube 22.
A central hole 25a that forms a crank gear 24 having a diameter b and rotatably fits into this circular stepped portion 24a.
(see Fig. 4), a gear 25 concentric with the crankshaft 5 is formed on the outer periphery, and a gear 25 is formed concentrically with the crankshaft 5.
An eccentric disk 26 that is eccentric with respect to the center hole 25a is provided protruding from one side of the core plate 5, and an eccentric core plate 27 is integrally formed.

It has an eccentric hole 28a (see FIG. 4) that rotatably fits into the eccentric disk 26, a gear 28b formed on the outer periphery of the disk, and a plurality of screw holes 28c on the same circumference. is provided to form an eccentric shifter 28, and a screw 31 is inserted into the screw hole 28 through screw insertion holes 29a and 30a provided with two rings 29 and 30, respectively.
The semicircular ball fitting grooves 29b, 3 are attached to the inner periphery of the two rings 29, 30 at their joints.
0b, and a circular track 32 into which each of the swing pins 20 is slidably fitted is formed by recessing one side of the ring 33, and a semicircular ball fitting groove 33a is formed on the outer peripheral surface of the ring 33. The ring 33 is rotatably attached to the eccentric shifter 28 by inserting a large number of balls 34 between the ball fitting groove 33a and the ball fitting grooves 29b, 30b.

As shown in FIG.
3 and a crank gear 24, and an eccentric core plate 2 is fitted on the circular stepped portion 24a.
7 is fitted, and the eccentric shifter 28 having the ring 33 described above attached to the eccentric disk 26 is fitted, and within the circular orbit 32 of this ring 33, a projection from each planetary nucleus 13 provided in the carrier 12 is fitted. The provided swing pins 20 are fitted, and the carrier 12 is fitted to the outer circumference of the sun gear 23.
Each of the planetary gears 16 in the inner mesh is meshed with the sun gear 23, and the crank arm 6 is fitted into the rectangular tube portion 5a of the crankshaft 5, and the crank arm 6 and the carrier 12 are fixed. This device is assembled by screwing and tightening the lock nut 7 into the portion 5b (see FIG. 3).

Further, this continuously variable transmission requires a speed change operation device and a reverse input permitting device at the time of reverse rotation. 2 and 3 and 7 to 11 show an example of the speed change operating device/reverse input permitting device.

That is, in this device, as shown in FIGS. 2 and 3, a shaft cylinder 35 having a screw hole 35a (see FIG. 3) is fixed to the vertical pipe 2 in parallel to the crankshaft 5 by welding or the like. A bolt-shaped support shaft 36 is screwed onto the support shaft 36, and the end of the bracket 37 is fitted to the support shaft 36 through a hole 37a, and a wire reel 38 and a pinion 39 are integrally formed. A gear case 40 having a U-shaped cross section is fitted onto the support shaft 36 through a hole 40a provided at one end thereof, and the gear case 40 has a one-way clutch 41 on its inner periphery and the eccentric core plate 27. Fixed side gear 42 meshing with gear 25 of
Interpose.

The one-way clutch 41 may be of any type, but for example, as shown in FIGS. A pawl 41a is provided that meshes and allows rotation in only one direction. Note that this one-way clutch 41 is fixed to the support shaft 36.

A hole 40b is provided at the other end of the gear case 40, and a sector gear 44 that meshes with the pinion 39 is fixed to one end of a shaft 43 passing through the hole 40b. The intermediate gear 45 meshing with the pin 47 is rotatably fitted, and the base of the swinging arm 46 is fitted onto the shaft 43 protruding outside the gear case 40.
Fix it by.

Further, a shaft 48 is provided protruding from the free end of the swing arm 46, and a movable gear 49, which meshes with the intermediate gear 45 and also meshes with the gear 28b of the eccentric shifter 28, is rotatably fitted onto the shaft 48. do. Note that the moving side gear 49 has the same number of teeth as the stationary side gear 42. 50 is a stopper for this gear 49. Further, this device is provided with a spring 51 as shown by the imaginary line in FIG.
In the figure, it is always biased to rotate counterclockwise.

Further, as shown in FIGS. 8 and 9, an operating wire 52 is wound around the wire reel 38 to drive it. In FIG. 3, 53 is an outer wire of the operating wire 52, and 54 (see FIG. 7) is its adjustment screw, which is inserted into the screw hole 3 provided in the bracket 37.
7b and fixed with a lock nut 55.

(Operation) Next, the operation of the apparatus of the present invention configured as described above will be explained. In Fig. 11, l ₁ is the eccentric disk 2
6 with respect to the crankshaft 5, and _l2 is the eccentricity of the circular orbit 32 of the eccentric shifter 28 with respect to the eccentric disc 26. And now if l ₁ = l ₂ ,
The eccentricity l of the circular orbit 32 with respect to the crankshaft 5 in the state shown in FIG. 11 is l=2l ₁ sin θ/2. When the eccentric shifter 28 is rotated in the direction of arrow A from the state shown in FIG. 11 to the state shown in FIG. 10, the amount of eccentricity of the circular orbit 32 with respect to the crankshaft 5 becomes O. That is, eccentric shifter 2
8 within the range shown in FIGS. 10 and 11, the amount of eccentricity of the circular raceway 32 with respect to the crankshaft 5 can be set steplessly to an arbitrary amount.

The eccentric shifter 28 is operated as follows. That is, in order to change from the state of eccentricity O shown in FIG. 10 to the eccentric state shown in FIG. 11, the wire 52 is operated in the direction of arrow B from the state shown in FIG. In this way, the pinion 39 rotates in the clockwise direction of arrow C via the reel 38, and the sector gear 44 and shaft 43 rotate as shown by arrow D. As a result, the shaft 43
A swinging arm 46 fixed to rotates in the direction of arrow E. If the arm 46 rotates in the direction of arrow E,
The moving gear 49 is the gear 28b of the eccentric shifter 28.
If the eccentric shifter 28 does not move, the gear 49 will rotate slightly in the direction of arrow F in FIG. 10, and as a result, the intermediate gear 45 will rotate in the direction of arrow G, and the fixed side gear 42 rotates in the direction of arrow H. In this case, the one-way clutch 41 inside the gear 42 slides against the gear 42 and does not interfere with the rotation of the gear 42.

However, since the rotational directions of the lever gears 49 and 42 are the same and the number of teeth of both the gears 49 and 42 is also the same, the meshing point I between the gears 49 and 28b and the gear 42 are the same.
If the distance L ₁ between the meshing point J and 25 does not change, the relative phase between the eccentric core plate 27 and the eccentric shifter 28 will not change. Then, since the gears 49, 45, and 42 also change from the state shown in FIG. 10 to the state shown in FIG. 11, the above-described L ₁ changes to L ₂ in FIG. 11. Therefore, this L ₁ −L ₂ moves the eccentric shifter 28 to the eccentric core plate 2.
7 in the direction of arrow K in FIG.

Therefore, the eccentric shifter 28 rotates relative to the eccentric core plate 27 from the state shown in FIG. 10 to the state shown in FIG. It will be eccentric by l with respect to.

In addition, the eccentricity state in Fig. 11 is changed to the eccentricity amount O in Fig. 10.
To return to the state shown in FIG.
9 in the opposite direction (direction of arrow L in FIG. 9).

In this case, the arm 46 in FIG.
Therefore, if the eccentric shifter 28 does not move, the gear 49 will rotate in the direction of arrow N.
As a result, the gear 42 tries to rotate in the direction of the arrow O, but the gear 42 is prevented from rotating in the direction of the arrow O by the action of the one-way clutch 41 fixed to the fixed shaft 36. The plate 27 does not rotate, and the eccentric shifter 28 rotates in the direction of the arrow A in FIG. 11 by the difference L ₁ -L ₂ to reach the state of eccentricity O shown in FIG. 10.

Next, the operation of the continuously variable transmission mechanism will be explained with reference to FIGS. 12 and 13.

FIG. 12 shows the crankshaft 5, the circular orbit 32, and the planetary nucleus 13 in the states shown in FIGS. 6 and 10.
FIG. 2 is an explanatory diagram showing the relationship among the planetary gear 16, the swing pin 20, and the sun gear 23.

In this state, when the crankshaft 5 rotates in the direction of arrow P via the clamp arm 6, the carrier 12 connected to the clamp arm 6 is rotated as shown in FIG.
rotates together with the crankshaft 5, and as a result, the shaft 14
Each planetary core 13 and planetary gear 16 also rotate together with the carrier 12 via. However, in this case, since the swing pin 20 protruding from the planetary core 13 rotates while being fitted in the circular orbit 32 concentric with the shaft 5, the planetary core 13 does not rotate at all with respect to the carrier 12. .

However, since each planetary gear 16 meshes with the sun gear 23, each planetary gear 16 tries to rotate clockwise in FIG. 12 due to the load resistance of this sun gear 23, but this rotation and a one-way clutch consisting of a pawl 18. Therefore, the sun gear 23 is rotated integrally with the crankshaft 5 in the same direction as the arrow Q in FIG. 12 by the planetary gear 16 which rotates integrally with the carrier 12. Therefore, the gear ratio in this case is 1:1.

Next, when the eccentric shifter 28 is placed in the eccentric state shown in FIGS. 11 and 13 by a gear change operation, as the crankshaft 5 rotates in the direction of the arrow P, the carrier 12 is brought into contact with the shaft 5 as described above. As a result, each planet core 13 also rotates together with the shaft 14, but in this case, since the circular orbit 32 in which each swing pin 20 is fitted is eccentric with respect to the shaft 5, each planet core 13 rotates together with the shaft 14. The core 13 also rotates with respect to the carrier 12 from time to time.

That is, if the center of the crankshaft 5 is R, the center of the planetary nucleus 13 is S, and the center of the swing pin 20 is T, θ, which is ∠RST, is always constant in the case of FIG. In the case of the figure, θ ₁ and
It changes like θ ₂ and θ ₃ . And between them θ ₁ <
The relationship θ ₂ <θ ₃ arises.

That is, since the planetary gear 16 between θ ₁ and _{θ 3} undergoes rotation in the direction of arrow U shown in FIG. By the revolution in the direction, the sun gear 23 meshing with the sun gear 23 is rotated at an increased speed from the shaft 5 as shown by the arrow V in FIG. 13. In this case, since there are six planetary gears 16 in this embodiment,
Gears 16 that are not in the rotational speed increasing range are not speeded up, but due to the action of the one-way clutch described above, only one planetary gear 16 that is in the highest speed increasing range at that time out of the six planetary gears 16 is in the speed increasing range. The remaining five planetary gears 16 drive the sun gear 23.
It can be rotated by . That is, at this time, the ratchet 17 of the gear 16 rotates slidingly relative to the pawl 18.

FIG. 14 shows the speed increasing characteristic of this transmission, with the ordinate representing the speed increasing gear ratio and the abscissa representing the rotation angle of the crankshaft 5.

As can be seen from this, in order to minimize variation in the speed ratio, it is preferable to use a large number of planetary gears 16. In this embodiment, six planetary gears 16 are used, so the angular range W (approximately 60 degrees) shown in FIG.
This is the drive range for 3. Therefore, it can be seen from FIG. 14 that in this embodiment, a rotational driving force with almost no pulsation is obtained even during speed increase.

Furthermore, in the above explanation, the case of the speed increase ratio O and the case of the maximum speed increase ratio have been explained, but it is also possible to set the rotational operation amount of the eccentric shifter 28 to an arbitrary amount between the values shown in FIGS. 10 and 11. Therefore, it is obvious that with this transmission, any speed ratio can be obtained steplessly.

The above is an explanation of the operation of this continuously variable transmission when the bicycle is running (forward rotation), but when a bicycle equipped with this continuously variable transmission stops, for example, in the middle of a slope, it will move backwards due to the action of gravity. Assuming this, the rear wheel 8 rotates in the direction of arrow X in FIG. 1, and the chain 11 moves in the direction of arrow Y, resulting in a reverse input acting on the crank gear 24 of the continuously variable transmission. Become.

When this reverse input is applied, this continuously variable transmission becomes mechanically self-locked when the gear ratio is high and cannot be reversed, and unreasonable force is applied to each part of the device, making it difficult to put this transmission into practical use. For the time being,
A reverse input permitting device is required during this reverse rotation.

Since the above-mentioned speed change operating device also serves as this reverse input permitting device, its operation will be explained below.

That is, in FIGS. 10 and 11, the arrow α is the rotation direction of the carrier 12 during forward rotation, and the arrow β is the rotation direction of the carrier 12 during reverse rotation.

When the rear wheel 8 is reversed as described above, as shown in FIG. tries to rotate in the direction of the arrow γ, but this rotation is prevented by the one-way clutch consisting of the ratchet 17 and pawl 18, so the planetary gear 16 is rotated by the carrier 12.
and rotate in the direction of arrow β. In this case the first
As shown in FIGS. 0 and 12, the circular orbit 32
When the amount of eccentricity with respect to the crankshaft 5 is O, the swing pin 20 integrated with the planetary core 13 in the planetary gear 16 can rotate within the circular orbit 32, so the above-mentioned self-lock phenomenon does not occur. , the circular raceway 32 is connected to the crankshaft 5 in FIGS. 11 and 1.
If it is eccentric as shown in Figure 3, swing pin 2
In order for 0 to pass within the circular orbit 32, the planetary nucleus 1
3 must rotate to some extent. However, as mentioned above, during reverse rotation, the planetary gear 1
6 is prevented from rotating, the planetary nucleus 13 also cannot rotate freely.

This causes self-lock,
In the device of the present invention, when this self-lock occurs, the ring 33 forming the circular track 32, together with the eccentric shifter 28 integral therewith, rotates integrally with the carrier 12 in the direction of the arrow .beta.. When the eccentric shifter 28 rotates, the gears 28b, 49, 4
5, 42, and 25, the eccentric core plate 27 also rotates by the same amount in the direction of the arrow β, so that the entire transmission ultimately rotates in the same direction together with the crank gear 24. Therefore, this operation can sufficiently absorb the aforementioned self-lock.

Note that during this reverse rotation, the eccentric core plate 27 and the eccentric shifter 28 both rotate in the same direction and by the same amount as described above, and the mutual phase does not change, so the gear ratio does not change either.

(Effects) Next, the effects of the device of the present invention will be explained. Since the speed change operating device and reverse input permitting device of the continuously variable bicycle transmission of the present invention is as described above, the continuously variable transmission described above can be put into practical use for the first time. Furthermore, since this speed change operating device can be used as it is as a reverse input permitting device, it is possible to reduce the weight and size of the device as a whole.

[Brief explanation of drawings]

Fig. 1 is a side view of a bicycle equipped with a continuously variable transmission, Fig. 2 is a vertical sectional view of the continuously variable transmission equipped with the device of the present invention, Figs. 3 to 5 are exploded perspective views thereof, and Fig. The figure is a partially cutaway view of the carrier section of the continuously variable transmission, FIG. 7 is an exploded perspective view of the speed change operating device and reverse input permitting device of the present invention, and FIGS. 8 to 11 are explanations of its operation. 12 and 13 are explanatory diagrams of the operation of the continuously variable transmission, and FIG. 14 is a speed increase characteristic diagram of the transmission. 5...Crankshaft, 6...Crank arm, 12...
Carrier, 13... Planetary nucleus, 14... Shaft, 16... Planetary gear, 17... Ratchet, 18... Pawl, 19... Spring, 20... Rocking pin, 23... Sun gear, 24... Crank gear, 25... Gear, 27... Eccentric nuclear plate, 28
...Eccentric shifter, 28b...Gear, 32...Circular orbit, 33...Ring, 36...Support shaft, 37...Bracket, 38...Wire reel, 39...Pinion, 4
0... Gear case, 42... Fixed side gear, 43... Shaft,
44... sector gear, 45... intermediate gear, 46... rocking arm, 48... shaft, 49... moving side gear, 51... spring, 52... operating wire.

Claims (1)

[Claims] 1. A carrier 12 is fixed to the crankshaft 5 of the bicycle, a plurality of planetary nuclei 13 are rotatably supported on the carrier 12, and a planetary gear 16 is coupled to each of these planetary nuclei 13 in one direction via a one-way clutch. a circular orbit 32 that guides the swing pin 20 that is fitted so as to be rotatable and that is protruded from the eccentric position of the planetary core 13;
An eccentric shifter 28 having a gear 28b formed on the outer periphery is provided so as to be able to freely adjust the amount of eccentricity with respect to the crankshaft 5 via an eccentric core plate 27 having a gear 25 concentric with the crankshaft 5 formed on the outer periphery. In a bicycle equipped with a continuously variable transmission in which a sun gear 23 and a crank gear 24, which mesh with the planetary gear 16, respectively, are integrally formed, and output is taken out by the crank gear 24, a support shaft 36 is mounted parallel to the crankshaft 5. is fixed to the frame of the bicycle, and the end of the bracket 37 is fitted to the support shaft 36, and the wire reel 38 and pinion 39 are
and a fixed side that has one end of the gear case 40 fitted onto the support shaft 36, has a one-way clutch on the inner periphery inside the gear case 40, and meshes with the gear 25 of the eccentric core plate 27. gear 42
interposed therein, a sector gear 44 that meshes with the pinion 39 is fixed to one end of a shaft 43 that passes through the other end of the gear case 40, and an intermediate gear that meshes with the fixed side gear 42 on the shaft 43 inside the gear case 40. 4
5 is rotatably fitted, the base of a swinging arm 46 is fitted and fixed to a shaft 43 protruding outside the gear case 40, and a shaft 48 is provided protruding from the free end of the swinging arm 46. A movable gear 49 that meshes with the intermediate gear 45 and the gear 28b of the eccentric shifter 28 is rotatably fitted to the shaft 48, and the shaft 4
3 is urged to rotate toward the continuously variable transmission side by a spring force, and the operation wire 52 is wound around the wire reel 38 to drive the continuously variable transmission for a bicycle. Device and reverse input permitting device.