JPS60146780A - Infinitely variable gear - 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 a continuously variable transmission device that is most suitable as a small-sized transmission for use in bicycles and the like.

Conventional small transmissions used in motorcycles include interchangeable chain types, gear type stepped transmissions, and belt type continuously variable transmissions, but belt types have large transmission losses and short shifting times. In addition, there are drawbacks such as the inability to change gears instantaneously in the event of an emergency, and gear type stepped transmissions require skill to change gears. The reality is that there are many unresolved issues such as dissatisfaction with the excessive or insufficient range of the gear ratio. We have filed an application for a continuously variable transmission (Special Application No.) that does not require any skill to operate the gears, can be changed continuously and in a short time, is small, lightweight, and has high transmission efficiency.

Figures 1 and 2 show an example of the continuously variable transmission device. ), 6 is the crank arm that fits on the crankshaft 5, ? is that rock nut.

To configure the continuously variable transmission, a disk-shaped eccentricity 8 is attached to the outer periphery of the drive shaft 5 eccentrically with respect to the drive shaft 5 and fixed to a hanger lug 4 of the bicycle frame, and a circuit for guiding a swinging bin (described later) is installed. Unlike forming the linked track 9 by recessing one side of the disk body, an eccentric shifter 10 having an eccentric hole 10a that fits into the eccentricity 8 is rotatably fitted to the outer periphery of the eccentricity '8. This makes it possible to freely adjust the amount of eccentricity of the circular orbit 0 with respect to the drive shaft 5.

That is, the groove 1ob (3
1! For example, by winding a wire (not shown) around the wire (see figure i) and manipulating this wire, the eccentric shifter IO can be rotated (maximum 180 degrees) with respect to the eccentricity 8, and the circular orbit 9 can be rotated. The amount of eccentricity with respect to the drive shaft can be adjusted freely.

In addition, an inner serration l' l concentric with this shaft 5 is fixed on the drive shaft 5 on the outside of the eccentricity 8, and an outer serration 1 that fits with this inner serration 1.1 is fixed.
form a disc-shaped carrier 18 having a central trap '2;
The bots 14 are provided in parallel with the outer serrations 12 at a plurality of locations on the same circumference of the carrier 18 (circumference quadrant 1 #1 in this embodiment), respectively.

It also has a pivot fitting hole 15a in the center, and forms a planetary core 15 consisting of a small diameter cylindrical part 15b and a large diameter cylindrical part 15c, and a ring-shaped planetary gear 16 is connected to this small diameter cylindrical part 15b via a one-way clutch. are fitted so that they can rotate in only one direction. The one-way clutch may be of any type, but for example, as shown in this embodiment, the ratchet 17 is formed on the inner peripheral surface of the planetary gear 16, and the ratchet 17 is formed on the small diameter cylindrical portion 15b of the planetary core 15. A spring 19 (see Fig. 1) is provided with a pawl IB that engages with it to prevent rotation in only one direction.
energizes the pawl 18 to engage with the ratchet 17.

Further, a swinging pin 20 that is parallel to the hole 15a is protrudingly provided at an eccentric position relative to the pivot fitting hole 15a on the inner surface of the large diameter cylindrical portion 15c of the planetary core 150. A planetary gear 16 is fitted to this planetary core 15 via a one-way clutch as described above, and a planetary gear 16 is fitted to each pivot 14 of the carrier 18, respectively.
5 mating 1. The swinging bins 20 of each of these planetary nuclei 15 are fitted into the circular orbits 9 of the eccentric shifter IO, and the outer serrations 12 are fitted into the inner serrations 11 to rotate the carrier 18 integrally with the drive shaft 5. Assemble as shown.

One driven gear 21 that meshes with each of the plurality (four in this embodiment) of the planetary gears 16 incorporated in the carrier 18 is formed integrally with the wheel 22 of the bicycle, and is connected via a bearing 28. The crank arm 6 is fitted to the drive shaft 5 on the outside thereof, and is fixed by tightening a lock nut.

Next, the operation of the continuously variable transmission device configured like Ueto will be explained. @ In figure 8. el is the eccentricity of the eccentricity 8 with respect to the drive shaft 5, and e2 is the eccentricity 'J4: of the circular orbit 9 of the eccentric shifter IO with respect to the eccentricity 8. And now i
If ll -gg, then the eccentricity iLj L of the circular orbit 9 with respect to the drive shaft 5 is at its maximum in the state shown in FIG.

From the state shown in FIG. 8, when the eccentric shifter IO is rotated 180 degrees as shown by arrow A to the state shown in FIG. 4, the deviation of the circular orbit 9 with respect to the drive shaft 5 becomes 0. That is, by arbitrarily operating the eccentric shifter lO within the range shown in FIGS. 8 and 4, the circular orbit 9
The amount of eccentricity with respect to the drive shaft 5 can be set steplessly to an arbitrary amount.

Figure 5 shows the drive shaft 6 and the circular orbit 9 in the state shown in Figure 4.
, the planetary core 15, the Bunsei Sonoruma 16, the rocking bottle 20,
It is an explanatory diagram showing the relationship with the driven gear failure 1. - In this state, when the drive I11]5 rotates in the direction of arrow B via the crank arm 6, the carrier 18 rotates integrally with the shaft 5 via the inner serrations 11 and outer serrations 12 shown in FIG. Result pivot): 1
4, each planetary core 15 and planetary gear 16 also rotate together with the carrier 18.

However, in this case, since the swing pin 20 protruding from the planetary core 15 rotates while being fitted in the circular orbit 9 concentric with the shaft 5, the planetary core 15 does not rotate at all with respect to the carrier 18.

However, since each planetary gear 16 meshes with the driven gear 21, each planetary gear 16 tries to rotate clockwise in FIG. 17 and a pawl 18. Therefore, the driven gear 21 is rotated integrally with the drive shaft 5 as shown by the arrow C in FIG. They rotate in the same direction. Therefore, the gear ratio in this case is l:l.

Next, shift the eccentric shifter 10 to the 2nd and 3rd positions by shifting the gear.
,6.7 Maximum i1. ii If you are in a state of mind,
As the drive shaft 5 rotates in the direction of arrow B, the carrier 18 rotates integrally with the shaft 5 as described above, and as a result, each planetary core 15 also rotates together with the pivot 14, but in this case, each swing Since the circular orbit 9 in which the pin 2o is fitted is eccentric with respect to the shaft 5, each free J-pencil 15 moves simultaneously with respect to the carrier 1B.

, that is, if the center of the drive shaft 5 is 0, the center of the planetary nucleus 15 is D, and the center of the swing bottle 2o is E, then ZODE
θ is always constant in the case of Fig. 5, but in Fig. 6 and 7
In the case of the figure, θ□, θ2°θ8. θ6. It changes like θ5. And between them θ1〈θ2〈θ8〈θ
, θ5 arises.

That is, rotation in the direction of arrow F shown in FIG. 216 occurs in the planetary gear 16 between θ and θ5, so this rotation in the direction of arrow F and the rotation of the planetary gear 16 around the axis 5 shown in FIG. As the gear 16 revolves in the direction of the arrow G, the driven gear 21 meshing therewith is rotated at an increased speed from the shaft 5 as shown by the arrow H in FIG. 2.6. In this case, since there are four planetary gears 16 in this embodiment, the rotational speed increasing area construction (
However, due to the action of the one-way clutch described above, among the four planetary gears 716, only one planetary gear 16, which is in the highest speed increasing range at that time, accelerates the driven gear z1. The remaining eight planetary gears 16 are driven by their driven gears 21 [thereby K to be rotated].
Become. In other words, the ratchet 17 of the float 16 slides against the pawl 18 and rotates.

In Figure 8, the ordinate shows the speed increasing gear ratio, and the abscissa shows the drive shaft 5.
This figure shows the speed increase characteristics of this continuously variable transmission based on the zero rotation angle problem.

As we will see, in order to minimize the variation in the gear ratio, it is better to use a large number of planetary gears 16. In this actual MLT example, four planetary gears 16 are used, so Angular range J (approximately 90°) shown in Figures 6 and 7
is the drive range of each planetary gear 16 with respect to the driven gear 21. Therefore, from the perspective of FIG.
Even during speed increase, rotational driving force with almost no pulsation can be obtained.

In addition, in the above explanation, the case where the speed increasing ratio is 0 and the case where the speed increasing ratio is the maximum speed increasing ratio are explained, but the eccentric shifter 100 rotation operation amount is
It is obvious that by setting the angle to an arbitrary 11° between FIG. 8 and FIG. 4, any speed ratio can be obtained steplessly with this continuously variable transmission.

Since the continuously variable transmission device of the prior application follows the above-mentioned approach, it does not require any skill to operate the gears, can continuously and steplessly change gears in a short time, and is small and lightweight with high transmission efficiency. The excellent effect of being able to provide a highly efficient continuously variable transmission is obtained.

However, in this device, when the circular orbit 9 is formed integrally with the eccentric shifter lO, the swing pin 20 slides and revolves without being strongly pressed against the side wall of the circular orbit 90 during driving, so that the friction loss during driving is reduced. In addition to the increased size, there is a problem in that the swing bottle 20 and the circular track 9 are also subject to increased wear.

The present invention has been made to solve the above-mentioned problems, and it further improves transmission efficiency by reducing friction loss during driving of this German continuously variable transmission, and also reduces wear of the swing pin and circular raceway. The purpose is to improve the durability of the device by reducing the amount of heat.

An embodiment of the present invention will now be described with reference to FIG. 9 and FIG. 1θ. In the figure, the same reference numerals as the above-mentioned reference numerals indicate equivalent parts.

In this embodiment, the circular orbit 9 is formed separately from the eccentric shifter lO by a ring 24 having a U-shaped cross section as shown in FIG. An annular groove 25 is formed into which the ring 24 is loosely fitted, and an inner circumferential wall surface 25a of the annular groove 25 and an inner circumferential surface 24a of the ring 24 are formed.
A rolling bearing consisting of a large number of steel balls 26 is inserted between the
A ring 24 is rotatably attached to the eccentric shifter 10.

Since the device 11 of the present invention is constructed as described above, when the swing pin 20 is fitted into the circular track 9 and rotates, the swing pin 20
0 and the ring 24 rotate almost integrally. In this case, since the ring 24 rotates with respect to the eccentric shifter IO by the rolling bearing 26, this rotational resistance is extremely small.

Further, since the sliding movement between the swing pin 2° and the circular raceway 9 of the ring 24 is slight, the wear of the swing pin 20 and the circular raceway 9 is almost eliminated.

As mentioned above, according to the present invention, this species 1.
This has the excellent effect of reducing friction loss during the drive of a step-change transmission, further improving transmission efficiency, and reducing wear on the swing pin and circular raceway, improving the durability of the device. .

[Brief explanation of the drawing]

Fig. 1 is an exploded perspective view of a continuously variable transmission to which the present invention is applied, Fig. M2 is a partial view showing the assembled state of its main parts, Figs. and the sixth
Fig. 7 is an explanatory diagram of the operation of the continuously variable transmission, Fig. 7 is an explanatory diagram of the speed increasing range by the continuously variable transmission, Fig. 8 is a diagram of its speed increasing characteristics, and Fig. 9 is a main part of the device 6 of the present invention. FIG. 1 is a perspective view showing a state in which the device is partially cut away; FIG. 4...Hanger lug 5...Crankshaft (drive shaft)
t8... Eccentric nucleus 9... Circular orbit 10... Eccentric shifter 11... Inner serration 12... Actor serration 18... Carrier 14... Pivot 15...
・Planetary core 16...Planetary gear 17...Ratchet
18...Claw 19...Spring 20...Swing pin 21...'Kmh's wheel 22...Chain wheel 2B
... Bearing 24 ... Ring 25 ... Annular groove 26 ... Steel ball (rolling bearing). Special 1'l - Applicant Brideston Cycle Co., Ltd. No. 2
Fig. 9 C Fig. 4 Fig. 7 Fig. 8 Soft angle of axis (degrees) 2 10

Claims (1)

[Claims] L A carrier is fixed to the drive shaft, and a plurality of planetary nuclei are rotatably supported on this carrier.A planetary wheel is fitted to these planetary nuclei via a one-way clutch so that it can rotate only in one direction. and an eccentric shifter having a circular orbit that guides a swinging bottle protruding from an eccentric position of the planetary core is provided with respect to the drive shaft so that the eccentricity W can be adjusted freely, and a driven gear meshes with each of the idler M gears. In the continuously variable transmission, the circular orbit is formed separately from the eccentric shifter, and the circular orbit is rotatably attached to the eccentric shifter via a rolling bearing. gear transmission.