JPS60213590A - Continuous speed variation device for bicycle - 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]

The present invention relates to an f, -1 continuously variable transmission for a bicycle, which is most suitable as a transmission mounted on the crankshaft of a bicycle. As this type of continuously variable transmission, for example, Japanese Patent Application Laid-Open No. 54-9
There is a device disclosed in Japanese Patent No. 3754, which is installed on a rear wheel hub axle of a two-wheeled vehicle. However, since bicycles generally increase the speed of rotation of the crankshaft and transmit it to the rear wheel, the crank gear A7 has a large diameter and the rear wheel sprocket has a small diameter. However, when the above-mentioned transmission is installed on the rear wheel hub axle, the diameter of the rear wheel sprocket increases to a certain extent, and the diameter of the crank gear must also be increased accordingly, resulting in the problem of an increase in the size of the transmission device. There is. In addition, this continuously variable transmission uses a planetary gear device to increase speed, and the speed increase ratio depends on the diameter of the planetary gear and the diameter of the planetary gear.
! The transmission force is determined by the ratio of the diameters of the gears, and the transmission force has a property that the more planetary gears are used, the smaller the pulsation becomes. However, when all the planetary gears and sun gears are arranged on the same plane as in the continuously variable transmission, as shown in Fig. 15 (a).
) As shown in (b) and (c), if the number of planetary gears P is increased, the sun gear 317) 1'\! J: If the diameter of the planetary gear P is made larger than the diameter of the sun gear S to increase the speedup ratio, the number of planetary gears P will decrease. While the pulsation increases, ν
There is n. The present invention was made in order to solve the problems of Itidi, and it is possible to miniaturize the entire 1-no. 3j! By arranging the teeth 111 twice in relation to the crankshaft, the diameter of the center of the planetary gear is 1 increments larger than the diameter of the sun gear, increasing the speed-up ratio and increasing the number of planetary gears. It is said that the pulsation of the transmission force is reduced by 1. In order to achieve the above object, in the present invention, a key 11 leaf is fixed to the crankshaft of a bicycle, a plurality of 'lfI star nuclei are rotatably supported on this carrier1), and one planetary nucleus is attached to each of these planetary nuclei. If the idle gear is installed in the IN so that it can rotate only in one direction via a directional clutch, these Vi
W teeth i1j are arranged twice with respect to the crankshaft, and an eccentric shifter having a circular orbit for guiding a swing pin protrudingly installed at an eccentric position of the planetary nucleus is provided so as to freely adjust the amount of eccentricity with respect to the crankshaft. A continuously variable transmission for a bicycle is constructed by integrally forming a sun gear and a crank gear that mesh with each of the planetary gears, and outputting an output from the crank gear. An embodiment of the present invention will be described below with reference to the drawings. In the figure, 1 is the main pipe of the bicycle frame, 2 is a vertical pipe, 3 is a chain stay, 4 is a hanger lug, 5 is a crankshaft, 6 is a crank arm that fits on the crankshaft 5, and 7 is its lock nut. Further, 8 is a rear wheel, 9 is a rear wheel hub axle, 10 is a rear wheel sprocket I, and 11 is a chino. In this embodiment, a carrier 12 (1
A cover plate 2a is detachably attached to the carrier body using screws 12b, etc., and is fixed to the crankshaft 5 via the crank arm 6, and a plurality of (6 pieces in this embodiment) are installed in the carrier 12.
A stepped cylindrical planetary nucleus 13 is rotatably supported via a shaft 14 at positions equally distributed around the circumference. Note that 15 is the bearing. 3- In this case, the stepped cylindrical free irl nucleus 13 is arranged i such that its large diameter portion 13a and small diameter portion 13b are reversed by 180° at the intersection n between adjacent planetary nuclei. Then, when a ring-shaped Mm gear 16 is fitted to the outer circumference of the large diameter portion 13a of each of these planetary cores 130 via a one-way clutch so that it can rotate only in one direction, these planetary gears 16 can be cranked. They are arranged doubly in the axial direction of the shaft 5. That is, in this embodiment, three planetary gears 1G are arranged on the outer side of the carrier 12, and the remaining three planetary gears 16 are arranged so as not to interfere with the inner side of the rear 12. Although any type of one-way clutch may be used, in this embodiment, a ratchet 17 is formed on the inner circumferential surface of a ring-shaped idler gear 16 as shown in Fig. 5.6. , a pawl 18 that engages with the ratchet 17 in the large diameter portion 13a of the planetary core 13 and rotates only in one direction.
is provided so that the pawl 18 is attached to the ratchet 11 when the spring 19 is attached.
It is biased so that it meshes with the Also, each of the above Mtj-! A swing pin 20 parallel to the shaft 14 is provided protruding from one side of the core 13 (the inner fourth side in this embodiment) at an eccentric position with respect to the shaft 14 . The notch 12c provided in the cover plate 12a of the carrier 12 shown in FIG. 5 is for allowing 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. Also, a crank gear A724 having two circular steps 24a and 24b at the other end of the shaft cylinder 22.
It has a center hole 25a (see FIG. 4) that rotatably fits into this circular step 24a, and a gear 25 concentric with the crankshaft 5 is formed on the outer periphery.
An eccentric disk plate 26 which is eccentric with respect to the center hole 25a is provided protruding from one side of the plate, and an eccentric crosspiece plate 27 is integrally formed. Eccentric hole 2 that rotatably fits into this eccentric disk 26
8a (see Fig. 4), a gear 28b is formed on the outer periphery of the disk, and a plurality of screw holes 28c are provided on the same circumference to form an eccentric shifter 28. The two rings 29.30 are attached to the eccentric shifter 28 by screwing the screw 31 into the screw hole 28c through the screw insertion holes 29a and 30a provided respectively, and the inner periphery of the two rings 29.30 is screwed into the screw hole 28c. semicircular ball fitting grooves 29b, 30b at the joints of
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 this ball fitting groove 33a and the ball fitting grooves 29b and 30b. As shown in FIG. 2, each of the above-mentioned parts 1 includes a shaft cylinder 22 having a sun gear 23 and a crank gear 24 fitted to the crankshaft 5 via a bearing 21, and a circular stepped portion 24a thereof. An eccentric cedar plate 27 is fitted, and an eccentric shifter 28 with the above-mentioned ring 33 attached to the eccentric disc 26 is fitted, and each of the rings provided in the carrier 12 is fitted into the circular track 32 of the ring 33. Each of the swinging pins 20 protruding from the planetary core 13J is inserted, and the carrier 12 is selectively engaged with the outer circumference of the sun gear 23, so that each of the planetary gears 16 in the carrier 12 is meshed with the sun gear 23, respectively. Then, when the crank arm 6 is fitted to the rectangular tube portion 5a of the crankshaft 50, the crank arm 6 and the carry 712 are fixed, and the threaded portion 5b of the crankshaft 5 (see Fig. 3).
To []Tsutsukunara 1 ~ to screw together and tighten () J
: Combined with Riko's device) γteru. Further, the continuously variable transmission device m of the present invention has C cores of the IQ core operating device and the reverse input permitting device N during reverse rotation. 2.3 and 7 to 11 show an example of the single-center operation device/reverse input permitting device N shown in FIG. 1. That is, this device is shown in Figs. 2 and 3. ia (see Figure 3) is fixed to the crankshaft 5 by welding or the like,
This screw hole 3! 1 screw the 1-shaped support 1-3 to this support shaft 3G.
C-fit the end of 7 through the hole 37a, and 79--40 with a trowel-shaped cross section. The gear case 40 has a one-way clutch 41 on its inner periphery and meshes with the gear 25 of the eccentric cedar plate 21. A fixed side gear 42 is interposed. The one-way clutch 41 may be of any type, but for example, as shown in FIG. A pawl 41a is provided which engages with the radiator 42a to permit 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 that meshes with the stationary gear 42 is fitted onto the shaft 43 in the gear case 40, and the base of the lff1 movable arm 46 is fitted onto the shaft 43 protruding outside the gear case 40. 47. Further, a shaft 48 is protruded from the free end of the swinging arm 4 (i), and a moving side gear 49 meshes with the intermediate gear 45 and the gear 28b of the eccentric shifter 28.
are fitted in a rotatable manner. Note that this moving side gear 49 has the same number of teeth as the stationary side gear 42, and 50 indicates this gear 4.
The number 9 is a stopper. This device also includes, for example, the 10th
A spring 51 as shown in phantom lines is provided to bias the shaft 43 so as to always rotate counterclockwise in FIG. 10. Further, as shown in FIGS. 8 and 9, an operating wire 52 is wound around the wire reel 38 to drive it. 53 in FIG. 3 is an outer wire of the operating wire 52;
4 (see Figure 7) is the adjustment screw, and the bracket 3
7 and fixed with a lock nut 55. Next, the operation of the apparatus of the present invention constructed as described above will be explained. In FIG. 11, 11 is the amount of eccentricity of the eccentric disk 26 with respect to the crankshaft 5, and β2 is the eccentricity m of the circular orbit 32 of the eccentric shifter 28 with respect to the eccentric disk 26. Now, if β1=β2, then the eccentricity mβ of the circular orbit 32 with respect to the crankshaft θ5 in the state shown in FIG. 11 becomes β-2βl 5In7. From the state shown in FIG. 11, the eccentric shifter 28 is rotated in the direction of arrow A to the state shown in FIG. −
becomes 0. (2) The eccentric shifter 28 is arbitrarily operated within the range shown in Figs. The operation of the eccentric shifter 28 is performed in the following J: order.In other words, to change from the state of eccentricity ω0 shown in Fig. 10 to the eccentric state shown in Fig. 11, the eccentricity shifter 28 is operated in the state shown in Fig. t3. From tlH, operate the wire 52 in the direction of arrow B. When this J:
At the same time, the pinion 39 rotates in the direction of arrow 0 through arrow 8, and the shaft 43 of the sector gear 44 rotates as shown in arrow 1. As a result, the swinging arm 46 fixed to the shaft 43 rotates in the direction of arrow E. 17) Rotate in the 7'J direction. If the arm 46 rotates in the direction of the arrow E, the moving side gear 49 is engaged with the gear 281) of the eccentric shifter 28, so if the eccentric shifter 28 does not move, the gear 49 will rotate slightly as shown in FIG. As a result, the intermediate gear 45 rotates in the direction of arrow G, and the stationary gear 42 rotates 1° in the direction of arrow 1-1. In this case, one side clap 41 inside the gear 42
Since it slides with respect to the gear 42, the rotation of the gear 42 is not hindered. However, the rotational directions of the lever gears 49 and 42 are the same,
Since the number of teeth of both gears 49 and 42 is the same, the meshing point ■ between gears 49 and 281) and the meshing point J between gears 42 and 25
If the distance Ill I-+ does not change, the eccentricity detection plate 2
7 and the eccentric shifter 28 do not change, but when the sector gear 44 is in the state shown in FIGS. 8 to 9, the gear 4
9, 45, and 42 also change from the state shown in FIG. 10 to the state shown in FIG. 11, so the above-mentioned Ll changes to L2 in FIG. 11. - Therefore, this L'1-12 is the amount by which the eccentric shifter 28 is rotated relative to the eccentric detection plate 21 in the direction of the arrow 1 in FIG. Therefore, the eccentric shifter 28 changes from the state shown in FIG. 10 to the state shown in FIG.
Since it rotates relative to the eccentric detection plate 27 in the state shown in the figure, the center of the circular orbit 32 integrated with the eccentric shifter 28 is eccentric by β with respect to the center of the crankshaft 5. In addition, the eccentricity state in FIG. 11 is changed to the eccentricity state 11 in FIG.
- To return to the state, just operate the operation W-7:12 in Figs. 8 and 9 in the opposite direction (in the direction of arrow 1- in Fig. 9). In this case, as shown in FIG. 11, since the 1°C arm 4G rotates in the direction of the arrow M, (if the center shifter 211 does not move IJ, the gear 491.1 rotates in the direction of the arrow N. As a result, the gear 42 tries to rotate 16 times in the direction of the arrow 0, but the rotation in the direction of the arrow 0 is limited by the action of the one-way gear 41 fixed to the fixed shaft 3G. After all, the eccentric cedar plate 27 rotates I!, and the eccentric shifter 28 rotates in the direction of the arrow in FIG. 11, as shown in FIG. 10. IQ heart h10 state to 2. Next, the operation of the continuously variable transmission mechanism will be explained with reference to FIGS. 12 and 13.゛Figure 12 shows the crankshaft 5 in the states shown in Figures 6 and 10, the circular raceway 32, and l! if! Nuclear 13,
'Wi is an explanatory diagram showing the relationship between the star gear 16, the swing bin 20, and the sun gear 23. In this state, as the crankshaft 5 rotates in the direction of arrow P via the crank arm 6, the carrier 12 connected to the crank arm 6 rotates together with the crankshaft 5 as shown at 12- (not shown in FIG. 2). As a result, each M
The star core 13 and the planetary gear 16 also rotate together with the carrier 12. 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.

[Note that since each planetary gear 16 is meshed with the sun gear 23, the load resistance of this sun gear 23 is J
: Each planetary gear 16 rotates clockwise in FIG.
It is almost stopped by the action of the one-sided clutch consisting of 8. Therefore, the sun gear 23 rotates 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, by shifting the gear, the eccentric shifter 28 is moved to the 11th position.
When the eccentric state shown in FIG. The planetary core 13 also rotates like a rod 14, but in this case each swing pin 2
Since the circular orbit 32 in which 0 meets 1 and C is eccentric with respect to the axis 5, each planetary nucleus 13 moves 11.1 every moment with respect to the 1-17 rear 12. That is, the crank If we cover the center of the axis 5 as R and 1, the center of the free ψ nucleus 13 as S and 17.11, and the center of the moving pin 20 as -[, then 0, which is R8T, is always constant in the case of Fig. 12. However, in the case of Fig. 13, f changes as (B, 02° θ3), and between phases !
A relationship arises. That is, since rotation occurs in the planetary gear 16 between θ1 and θ3J in the J arrow U direction shown in FIG. The sun gear 23 meshes with this as it rotates in the direction.
is indicated by the arrow V in FIG. 13. In this case, since there are six planetary gears 16 in this embodiment, the gears 16 that are not in the rotation speed increasing range are not accelerated, but due to the action of the one-sided clutch described above, among the six planetary gears 16, at that time Only one planetary gear 16 in the highest speed increasing range drives the sun gear 23, and the remaining five planetary gears 16 are conversely rotated by the sun gear 23. That is, at this time, the ratchet 17 of the gear 16 rotates while sliding against the pawl 18. FIG. 14 shows the speed increasing characteristics of the device of the present invention, with the speed increasing gear ratio plotted on the ordinate and the rotation angle of the crankshaft 5 plotted on the abscissa. As we will see, in order to reduce the variation in the gear ratio, it is best to increase the number of planetary gears 16 used. In this embodiment, 16 of the 6 planetary teeth are used, so the angular range W (approximately 60°) shown in FIG. 13 is the drive range of each planetary gear 16 with respect to the sun gear 23. Therefore, as seen from FIG. 14, in this embodiment, a rotational driving force with almost no pulsation can be 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, according to the device of the present invention, any speed can be increased by 1 in 1 step without 15! -1 It is obvious that there is no need to explain. The above describes how to ride a bicycle using the continuously variable transmission device 6 of the present invention.
,? It is clear that when a bicycle equipped with this continuously variable transmission device A stops in the middle of a hill, for example, when the bicycle is stopped in the middle of a slope, the action of the Φ force causes a change in speed of 1031!1l-1r.
: Then, in Figure 1, the rear wheel 8 is indicated by the arrow X 17)
As a result of the rotation in the direction 7'J and the movement of the cheno 11 in the direction of the arrow Y, the crank gear A of the continuously variable transmission of the present invention
724 5. When this reverse input acts, the device of the present invention will self-lock due to its mechanism when the gear ratio is high and will not be able to reverse, causing unreasonable force to be applied to each part of the device. Therefore, in order to put the device of the present invention into practical use, a device for allowing reverse input at the time of reverse rotation is required. Since the aforementioned eccentric operating device also serves as this reverse entry permitting device, its operation will be explained below. That is, in FIGS. 10 and 11, the arrow α indicates the rotation direction C of the carrier 12 during forward rotation, and the arrow β indicates the rotation direction of the carrier 12 during reverse rotation. When the contact wheel 8 mentioned above is reversed, as shown in FIG.
When the rotation in the direction of arrow β is transmitted to each planetary gear 16, each planetary gear 16 tries to rotate in the direction of arrow γ, but this rotation is blocked by the one-sided clutch consisting of the ratchet 11 and pawl 18. The planetary gear 16 rotates together with the carrier 12 in the direction of arrow β. In this case the first
As shown in FIG. 0 and FIG. 12, when the eccentricity of the circular orbit 32 with respect to the crankshaft 5 is 0, the swing pin 20 integrated with the planetary core 13 in the planetary gear 16 rotates within the circular orbit 32. Therefore, the above-mentioned self-locking phenomenon does not occur, but the circular raceway 32 is in the first position relative to the crankshaft 5.
When eccentric as shown in FIGS. 1 and 13, the planetary core 13 must rotate to some extent in order for the swing pin 20 to pass within the circular orbit 32. However, as described above, since the rotation of the planetary gear 16 is blocked during reverse rotation, the planetary core 13 cannot also rotate freely. Because of this, self-locking occurs (in the device of the present invention, when this lever is activated, the ring 33 forming the circular track 32 is connected to the eccentric shifter 28 integral therewith). −1−!?Lee] 12 rotates in the direction of the arrow β. Then, when the eccentric shifter 28 rotates, the gear 2 old+, 49.4!i, 42.25
The eccentric laminated plate 27 also moves in the direction of the arrow β through the same tdP number -J.
Because it rotates, the entire transmission ends up being a crank gear X721.
It will rotate in the same direction as 1. Therefore, this operation can sufficiently absorb the above-mentioned self-lock. During this reverse rotation, both the eccentric stacked plate 27 and the eccentric shifter 28 rotate by the same amount IJ in the same direction as described above, and the mutual phase does not change, so the gear ratio does not change either. Next, the effects of the device of the present invention will be explained. As mentioned above, the continuously variable transmission of the present invention is installed on the crankshaft of the bicycle instead of on the rear wheel hub axle.
The diameter ratio to the sprocket 1 can be made as large as possible, and the overall size of the transmission device is not increased. In addition, this type of continuously variable transmission uses a planetary gear system to increase speed, and the speed increase ratio is determined by the ratio of the diameter of the planetary gear and the diameter of the sun gear, and the transmission force is determined by the ratio of the diameter of the planetary gear and the diameter of the sun gear. There is a property that the larger the number used, the smaller the pulsation becomes. However, like the known continuously variable transmission,
When placing the planetary gear and sun gear in Nizube, use the 15th
As shown in Figures (a), (b), and (c), if the number of planetary gears P is increased, the diameter of the sun gear S becomes larger and the speed increasing ratio becomes smaller. If the speed increase ratio is increased by increasing the diameter of S, there is a problem that the number of planetary gears P decreases and pulsation increases. However, in the continuously variable transmission of the present invention, by arranging the planetary gear device twice with respect to the crankshaft, the diameter of the planetary gear P can be adjusted to the diameter of the sun gear S as shown in FIG.
Not only can the speed increasing ratio be increased by increasing the diameter of the planetary gear P, but also the pulsation of the transmission force can be reduced by increasing the number of planetary gears P.

[Brief explanation of drawings]

Figure 1 is a side view of the device of the present invention during rotation at f/11 degrees, Figure 2 is a longitudinal sectional view of the device of the present invention, Figures 3 to 5 are exploded perspective views thereof, and Figure 6 is the device of the present invention. A partially cutaway view of the 7th part of the device, Figure 7 is an exploded perspective view of the eccentric operating neck and reverse human force permitting device, Figures 8 to 11 are its operation; , FIG. 12 and FIG. 13 are explanatory diagrams of the operation of the device of the present invention, and FIG. 14 is an illustration of the device of the present invention when the speed is increased.
The figure shows various combinations of planetary gears and sun gears.
It is an explanatory diagram. 5... Crankshaft 6... Crank arm 12...
・Carry\713...'ti star nucleus 14...Axis 16
... Planet gear 17 ... Ratchet 1-18 ... Pawl 19 ... Spring 20 ... Swing pin -20- 23 ... Sun gear 24 ... Crank gear 27 ...
- Eccentric stacked plate 28...Eccentric shifter 32...Circular orbit 33...Ring. Patent Applicant: Brideston Cycle Co., Ltd. Figure ti Figure 1 - Figure 16 (C)

Claims (1)

[Claims] 1. Fix the carrier to the crankshaft of the bicycle, and attach this key 1? A plurality of 3WW nuclei are rotated to the left and right in the direction 7, and each of these 'IIl star nuclei is -1) played via a direction clutch!
Teeth ilj only in one direction I! , one-turnable sea urchin fitting J
Then, these planetary gears are placed two times against the crankshaft!
Md to 0, and the eccentric shifter that guides the swing pin protruding from the eccentric position of the front HI1 free W nucleus is set in 1 to adjust the eccentricity with respect to the crankshaft. (a) a sun gear meshing with each of the planetary gears;
This is a continuously variable transmission decoy for bicycles, which is characterized by integrally forming a gear wheel and extracting output from the crank gear.