JPH0337461A - V-belt continuously variable transmission - Google Patents

Abstract

PURPOSE:To reduce the deterioration of the transmission property, and to obtain a specific running performance and running feeling, by forming a tapered surface at the inner bore of the end of a variable sheave at the unfixed sheave side, and contacting the tapered surface to the rotary shaft side. CONSTITUTION:At the inner bore at the unfixed sheave side end of a bush 35, a tapered surface 35a of the inclining angle alpha is formed along the whole surface, and the tapered surface 35a is made contacted to the collar 31 of a crank shaft 4 in the operation. As a result, since a V-belt and the contact side are inclined to the outer side by the force acting from the V-belt 26 to a sheave 34, the tapered surface 35a of the unfixed sheave side end of the pressing-in bush 35 of the sheave 34 is pressed by the collar 31, and a phenomenon of lifting up the fixed sheave side end is generated. By the rotation of the sheave 34, the tapered surface 35a of the unfixed sheave side end is contacted to the collar 31 in order. However, since the contact of the both members is a surface contact, the friction of the end of the bush 35 can be reduced, and a specific transmission performance can be obtained even though the running distance is extended.

Description

[Detailed Description of the Invention] [Industrial Application Field] This invention relates to an endless V-belt continuously variable transmission used in motorcycles, etc., and more specifically, a V-held continuously variable transmission that can obtain 1+A- during proper gear shifting. This relates to transmissions.

[Prior Art] For example, as disclosed in Japanese Unexamined Patent Publication No. 60-252860, some motorcycles use a V-belt continuously variable transmission that changes the gear ratio steplessly. This V-belt continuously variable transmission has a fixed sheave fixed to a rotating shaft such as a crankshaft, and transmits power from a cam plate fixed to the rotating shaft to a movable sheave loosely engaged with the rotating shaft. and,
By operating the centrifugal weight placed between the movable sheave and the cam plate, the movable sheave is moved in the direction of the rotational axis according to the rotational speed, and the distance between the conical surfaces of the movable sheave and the fixed sheave is changed. There is one that changes the gear ratio by changing the locking position of the endless V-belt.

[Problem to be solved by the invention] For example, a bushing is press-fitted into the movable sheave, and the bushing is loosely connected to the rotating shaft via a collar. The bushing is made of, for example, a copper-based sintered alloy, and the collar is made of steel. A small gap is provided between the bush of the movable sheave and the collar to allow movement of the movable sheave.

Therefore, during gear shifting, the force acting on the movable sheave from the V-belt causes the movable sheave to open outward at the part where the V-belt makes contact, and the end of the bushing on the non-fixed sheave side is pressed against the collar, and the end of the bushing on the non-fixed sheave side is pressed against the collar. A phenomenon in which the edges lift up occurs. Therefore, when the movable sheave rotates, it moves in the axial direction due to the speed change operation, and a strong force is concentrated on the sliding surface end of the bushing on the non-fixed sheave side of the movable sheave due to the tension of the belt.
This rotates and makes line contact. At this time, the movable sheave flaps and the bushings wear out in this area, so the movable sheave opens outward from the predetermined setting state, and as the mileage increases, the predetermined shift You will no longer be able to obtain properties.

The present invention was made against the background of the above circumstances, and an object of the present invention is to provide a V-belt continuously variable transmission that can reduce deterioration of transmission characteristics and provide a predetermined running performance and running feeling.

[Means for Solving the Problems] In order to solve the above problems, the present invention fixes a fixed sheave to a rotating shaft, and engages a cam plate fixed to the rotating shaft to a movable sheave loosely engaged with the rotating shaft. The movable sheave is moved in the direction of the rotating shaft by the operation of a centrifugal weight placed between the movable sheave and the cam plate, and the cone between the movable sheave and the fixed sheave that sandwich the endless V-belt is A V-belt continuously variable transmission that changes the interval between surfaces, characterized in that a tapered surface is formed on the inner diameter of the end of the movable sheave on the non-fixed sheave side, and this tapered surface can come into contact with the rotating shaft side. There is.

[Operations] In this invention, ■ When a force to spread the movable sheave outward is applied from the heald to the movable sheave, the tapered surface provided on the movable sheave comes into contact with the rotating shaft side, resulting in a surface contact state. This reduces wear on the movable sheave, prevents the movable sheave from tilting outward, and reduces deterioration of transmission characteristics.

[Example] Hereinafter, an example of the present invention will be described in detail based on the accompanying drawings.

Figure 1 is a sectional view of a V-belt continuously variable transmission used in a motorcycle, Figure 2 is a sectional view of a starter device, Figure 3 is a sectional view of the drive side of the V-belt continuously variable transmission, and Figure 4 is a sectional view of the V-belt continuously variable transmission. A front view of the movable sheave, Fig. 5 is a sectional view taken along V-V in Fig. 4, and Fig. 6 is a
FIG. 7 is a front view of the spring receiving member, FIG. 8 is a cross-sectional view taken along the line -■ in FIG. 7, and FIG. 9 is a diagram showing the speed change characteristics.

In FIG. 1, reference numeral 1 indicates an engine, and this engine 1 is connected to a power unit case 2. As shown in FIG. A crankshaft 4 driven by a piston 3 and an axle 6 that suspends a rear wheel 5 are rotatably supported on the power unit case 2 .

A power generator m7 is provided at one end of the crankshaft 4, and a one-way starting clutch 8 is provided at the other end. As shown in FIG. 2, in this starting one-way clutch 8, a ring gear 9 meshes with a gear 10a of an intermediate shaft 10, and a gear 10b of this intermediate shaft 10 engages a starter motor 11.
The output shaft 11a is meshed with the output shaft 11a. This starter motor 1
1, the ring gear 9 is driven, the crankshaft 4 is forcibly rotated via the starting one-way clutch 8, and the engine 1 is started.

Further, this engine 1 is provided with a kick starter 12, and a kick lever 13 rotates a starter shaft 14. The starter shaft 14 is pivotally supported between the power unit case 2 and the cover case 15, and a drive lever 16 is fixed to the starter shaft 14. A gear portion 16a of the drive lever 16 is press-fitted into the cover case 15. It meshes with a gear 18a formed on a cylindrical body 18 that is loosely engaged with the support shaft 17. Further, a spring 19 is inserted through the starter shaft 14, and one end 19a is connected to the cover case 1.
5, and the other end 19b is the drive lever 1.
6, respectively, so that the starter shaft 14 always returns to its initial position. When the kick lever 13 rotates, the cylinder body 18 moves in the direction of the crankshaft 4 against the spring 21, and the pawl body 20 fixed to the cylinder body 18 engages with the pawl body 22 fixed to the crankshaft 4, causing the crankshaft to move. The shaft 4 is forcibly rotated to start the engine 1.

The driving force of the engine 1 is transmitted from the crankshaft 4 to the V-belt continuously variable transmission A, and is transmitted to the driven shaft 2 via the centrifugal clutch B.
3. The gear 24 of the driven shaft 23 is connected to the connecting shaft 25
gear 26 of the connecting shaft 25, and gear 26 of the connecting shaft 25.
7 meshes with the gear 28 of the axle 6, and the power of the driven shaft 23 is transmitted to the axle 6 via these gear mechanisms.

(2) The drive side of the belt continuously variable transmission A is constructed as shown in FIGS. 3 to 5.

A cam plate 30 is attached to the spline portion 4a of the crankshaft 4.
, collar 31, fixed sheave 32, and claw body 22 are inserted in this order and tightened and fixed with a nut 33, so that these rotate together with the crankshaft 4.

The fixed sheave 32 is disk-shaped, and a plurality of cooling fins 32b are integrally formed on the side opposite to the conical surface 32a, and air is sucked into the fixed sheave 32 by rotation.

A movable sheave 34 is loosely engaged with the collar 31 via a bushing 35, and the bushing 35 is press-fitted into the movable sheave 34 and is integrated with the movable sheave 34, and the conical surface 34a of the movable sheave 34 faces the conical surface 32a of the fixed sheave 32. The V heald 36 is then held between them. Movable sheave 3
An inwardly protruding guide 1 to 34b is integrally formed in the opening opposite to the conical surface 34a of the cam plate 30, and is engaged with the outer periphery of the cam plate 30 via a slider 37.

A recess 34c is formed in the movable sheave 34, and a slope 30a is formed in the cam plate 30 to face each other, and a centrifugal weight 38 is provided between the recess 34c and the slope 30a.
is provided.

The centrifugal weight 38 is guided by the recess 34c of the movable sheave 34 and the inclined part 30a of the cam plate 30 by the centrifugal force caused by the rotation of the crankshaft 4, and moves in the radial direction, thereby moving the movable sheave 34 in the direction of the crankshaft. , movable sheave 34
The speed is changed by changing the distance between the conical surfaces 34a and 32a of the fixed sheave 32.

A bushing 35 that supports the movable sheave 34 on the collar 31 is press-fitted into the shaft portion 34d of the movable sheave 34.While the collar 31 is made of steel, this bushing 35 is made of a copper-based sintered alloy, and the bushing 35 supports the movable sheave 34 on the collar 31. This allows the sheave 34 to move smoothly. The inner diameter of the non-fixed sheave side end of the bushing 35 has an inclination angle α as shown in FIGS. 3 and 5.
The collar 31 is formed with a tapered surface 35a over the entire circumference, and this tapered surface 35a is provided on the crankshaft 4 during operation.
It is possible to contact.

Therefore, when the speed is changed, ■ the movable sheave 3 is moved from the belt 36
4, the side that contacts the belt 36 becomes inclined outward. Therefore, the tapered surface 35a formed at the non-fixed sheave side end of the bush 35 press-fitted into the movable sheave 34 is pressed against the collar 31, and this causes a phenomenon in which the fixed sheave side end is lifted. Moreover, as the movable sheave 34 rotates, the bushes 3 on the non-fixed sheave side
The tapered surface 35a of the bushing 35 contacts the collar 31, but since the contact between the two is surface contact, wear on the end of the bushing 35 can be reduced, and predetermined speed change characteristics can be obtained even if the mileage increases. be able to.

Therefore, as shown in FIG. 9, even if the running distance is increased, this embodiment can suppress the deterioration of the shifting characteristics as shown by the dashed dotted line, compared to the conventional one shown by the dashed double dotted line. The speed change characteristics can be brought close to the settings shown by the solid line.

In this embodiment, the bushing 35 is press-fitted into the movable sheave 34 to integrate them, and the bushing 35 is also included in the movable sheave 34, and a tapered surface is formed on the inner diameter of the bushing 35. It is also possible to directly form a tapered surface on the inner diameter portion of the movable sheave 34 without using the sheave 35.

Figure 6 is a sectional view showing the driven side of the continuously variable transmission.
The upper half section shows the high speed state, and the lower half section shows the low speed state.

A support tube 50 is rotatably provided on the driven shaft 23 via a hair ring 5152, and a fixed sheave 5 is attached to the support tube 50.
3 is fixed. The support cylinder 50 is provided with a torque cam cylinder 54 whose inside is filled with grease, and a movable sheave 55 is fixed to the torque cam cylinder 54. A cam groove 56 is formed at a predetermined angle in the torque cam cylinder 54, and a cam pin 57 fixed to the support cylinder 50 is engaged with this cam groove 56. When changing gears using the torque cam cylinder 54, the movable sheave 55 is supplied with grease and is lubricated, and the movable sheave 55 rotates relative to the fixed sheave 53 while moving in the direction of the driven shaft. The torque cam cylinder 54 is provided with a spring seat 59 of the spring 58, and one end of this spring seat 59 has a flange 59a bent outward, and this rib 59a is provided in contact with the movable sheave 55. There is.

The spring 58 is compressed and provided between the movable sheave 55 and the clutch plate 60 of the centrifugal clutch B, and always urges the movable sheave 55 in the direction of the fixed sheave. This spring 58 is installed i-1 in the movable sheave 55 via a spring receiving member 61, and this spring receiving member 61 has an annular recess 61a as shown in FIGS. 7 and 8. The end portion 58a of the spring 58 is fitted and held in the recess 61a, and the spring 58 can be reliably centered with the spring receiving member 61. Furthermore, when the movable sheave 55 moves, it slides and rotates between the spring receiving member 61 or the spring seat 59, thereby smoothly rotating relative to the clutch plate 60. By making the spring receiving member 61 slidable in this way, the spring 58 is not caught, and the spring 58 is not twisted and expanded or contracted in the radial direction, so that the spring load can be adjusted as set. This stabilizes the shifting characteristics.

The clutch plate 60 of the centrifugal clutch B is spline-engaged with the support tube 50 and fixed by a nut 62, and rotates together with the fixed sheave 53. This clutch plate 60 is provided with a pair of clutch shoes 63, which are rotated by centrifugal force using a support pin 64 as a fulcrum, opened outward, and are pressed into contact with a fixed plate 65 to transmit power. . This fixed plate 65 is connected to the driven shaft 23.
A clutch is connected at a predetermined rotational speed to rotate the driven shaft 23 and transmit power to the rear wheels.

Note that the annular ring 61 may be provided on the clutch plate 60 side to support the end 58b of the spring 58, or may be further supported by both ends 58a and 58b.

[Effects of the Invention] As described above, in this invention, a tapered surface is formed on the inner diameter of the end of the movable sheave on the non-fixed sheave side, and this tapered surface can be brought into contact with the rotating shaft side. 1. On the movable sheave. ■When a force is applied to spread the movable sheave outward at the part where the belt contacts it, the movable sheave tilts and the tapered surface contacts the rotating shaft side, creating a surface contact state. Therefore, even if the movable sheave rotates and flutters due to the tension of the heald,
Pressure force is prevented from being concentrated on the non-fixed sheave side end and wear is reduced, which prevents the movable sheave from tilting outwards and improves the shifting characteristics even as the mileage increases. can reduce deterioration.

[Brief explanation of drawings]

Figure 1 is a sectional view of ■Held continuously variable transmission used in motorcycles, Figure 2 is a sectional view of the starter device, Figure 3 is a sectional view of the driving side of ■Held continuously variable transmission, and Figure 4 is A front view of the movable sheave, Fig. 5 is a sectional view taken along V-V in Fig. 4, and Fig. 6 is a
FIG. 7 is a front view of the stopper, FIG. 8 is a cross-sectional view taken along the line -■ in FIG. 7, and FIG. 9 is a diagram showing the speed change characteristics. In the drawings, reference numeral 1 is an engine, 4 is a crankshaft, 30 is a cam plate, 31 is a collar, 32 is a fixed sheave, 34 is a movable sheave, 35 is a bushing, 35a is a tapered surface, and 36 is a heald. Figure a Figure T Train Figure ■ G1 Figure ■ Figure 1 Car JV Figure Figure

Claims (1)

[Claims] A fixed sheave is fixed to the rotating shaft, and a cam plate fixed to the rotating shaft is engaged with a movable sheave loosely connected to the rotating shaft to enable power transmission, and the movable sheave is arranged between the movable sheave and the cam plate. V that moves the movable sheave in the direction of the rotation axis by operating the centrifugal weight and changes the distance between the conical surfaces of the movable sheave and the fixed sheave that sandwich the endless V-belt.
A V-belt continuously variable transmission, characterized in that a tapered surface is formed on the inner diameter of the end of the movable sheave on the non-fixed sheave side, and this tapered surface can come into contact with the rotating shaft side. .