JPH0526367Y2 - - Google Patents

Description

[Detailed description of the invention] (Industrial application field) The present invention relates to a continuously variable transmission device that changes rotation speed steplessly, and in particular, includes an intermediate pulley for speed change between a driving pulley and a driven pulley consisting of a V pulley. This paper relates to improved technology for pulley type devices.

(Prior Art) Conventionally, as a pulley-type continuously variable transmission equipped with this type of intermediate pulley, there has been known, for example, the one shown in Japanese Utility Model Publication No. 45-3212. That is,
This device consists of a driving pulley consisting of a V pulley supported by a driving shaft, a driven pulley consisting of a V pulley supported by a driven shaft parallel to the driving shaft, and a position between the driving and driven axes that is orthogonal to both axes. an intermediate pulley rotatably supported via an intermediate shaft at the intermediate portion of an arm rotatable in a plane; a pair of belts each wound between the driving and driven pulleys and the intermediate pulley; It is equipped with The intermediate pulley is slidably and rotatably supported by a pair of fixed sheaves facing each other in the axial direction, and an intermediate shaft between the two fixed sheaves, and a pair of pulleys is provided between the two fixed sheaves. By rotating the arm and moving the movable shaft in the axial direction by the tension of the belt, the pulley diameters of both pulley parts can be changed in opposite directions. The rotation speed between the driving and driven pulleys is changed by changing the rotation speed between the driving and driven pulleys.

However, this method has a problem in that the belt slips. Therefore, as an improved technique, disclosed in Japanese Utility Model Publication No. 45-14572, the pulley type continuously variable transmission described above is provided with a tension pulley that presses the slack side of one of the pair of belts. The tension pulley applies tension to the belt to suppress slippage.

(Problems to be Solved by the Invention) However, with this proposal, on the other hand, since the belt tension increases due to the pressure of the tension pulley, it is unavoidable that the operating force during the gear shifting operation increases.

The original purpose of the present invention is to reduce the operating force during gear shifting operations in a pulley-type continuously variable transmission device having an intermediate pulley as described above, by having the gear shifting structure of the intermediate pulley as described below. There is a particular thing.

That is, a plurality of connecting members extend axially through one fixed sheave of the intermediate pulley and have inner ends fixed to the movable sheave of the intermediate pulley, and a cam groove arranged around the intermediate shaft and extending spirally. and a cylindrical cam follower disposed around an intermediate shaft and slidably engaged with a cam groove of the cam; While connected to the outer end of the connecting member via a bearing,
The other is attached to a fixed body, and one of the cams or cam followers is rotated around the intermediate shaft to move the movable shaft in the axial direction, thereby switching the speed ratio between the drive shaft and the driven shaft.

By the way, in that case, in order to increase the gear ratio between the drive and driven shafts, it is necessary to increase the length of the two belts that are applied to the drive and driven pulleys and the pulley portion of the intermediate pulley. however,
As the belt becomes longer, idler pulleys, counter pulleys, etc. must be installed to take up the slack in the belt during gear shifting, which increases the bending fatigue of the belt and may shorten its lifespan. However, there was room for further improvement.

The present invention was developed in view of the above points, and its purpose is to reduce the operating force during gear shifting operations by improving the support structure of the intermediate pulley, and to reduce the need for idler pulleys and counter pulleys. The purpose of the present invention is to increase the gear ratio of a transmission while maintaining a long belt life by making it possible to remove belt slack without using a belt.

(Means for Solving the Problems) In order to achieve the above object, the solving means of the present invention makes it possible to move the intermediate pulley in the direction toward and away from the driving and driven pulleys.

In other words, the invention described in claim (1) includes a drive pulley supported by a drive shaft, a driven pulley supported by a driven shaft parallel to the drive shaft, and a drive pulley located substantially between the drive and driven shafts. An intermediate pulley supported on an intermediate shaft parallel to the axis and having first and second pulley parts, and a V-belt wound between the drive pulley and the first pulley part of the intermediate pulley. and a second belt consisting of a V-belt wound between the driven pulley and a second pulley portion of the intermediate pulley, and the intermediate pulley has first and second belts facing each other in the axial direction. A second pair of fixed sheaves are slidably and rotatably supported on an intermediate shaft between the two fixed sheaves, and between the first and second fixed sheaves, respectively.
and a movable shaft shaped like an acacia bead forming a pulley section, and by moving the movable shaft in the axial direction, the pulley diameters of both pulley sections can be varied in opposite directions, thereby controlling the rotation between the driving and driven pulleys. The premise is a continuously variable transmission that changes speed.

The intermediate shaft is attached to a moving member that is movable toward and away from both shafts along a plane orthogonal to the drive shaft and the driven shaft.

Further, a plurality of connecting members each extending axially through the first fixed sheave of the intermediate pulley and having an inner end fixed to the movable sheave, and a cam disposed around the intermediate shaft and extending spirally. A cylindrical cam having a groove, and a cylindrical cam follower disposed around an intermediate shaft and slidably engaged with the cam groove of the cam, one of the cam or the cam follower being disposed outside the connecting member. One end is connected via a bearing and an operating lever is attached, while the other end is integrally fixed to the moving member,
A speed change switching mechanism is provided which rotates one of the cam or the cam follower around an intermediate shaft by operating a control lever to move the movable shaft in the axial direction.

Further, in the device described in claim (2), specifically, the movable member is an arm that can swing around a rotation center parallel to the drive shaft and the driven shaft, and the intermediate shaft is fixed to the tip of the arm. do.

In addition, in the invention as set forth in claim (3), in order to prevent the operating portion of the operating lever from being largely displaced during gear shifting, the cam groove of the cam in the gear shift switching mechanism is adjusted to the cam or cam follower by operating the operating lever. The intermediate shaft is tilted so that when one of the two is rotated around the intermediate shaft, the intermediate shaft moves in a direction opposite to the moving direction of the operating portion of the operating lever.

(Operation) With the above configuration, the device according to claim (1),
When changing the gear ratio of a transmission, when the operating lever of the gear change switching mechanism is operated to rotate either the cam or the cam follower around the intermediate shaft, the spiral cam groove on the outer periphery of the cam and the cam follower rotate as the cam or the cam follower rotates. One of the cams or cam followers moves relative to each other in the axial direction due to engagement with the cam follower, and the movable sheave of the intermediate pulley, which is connected to this member via a bearing and a connecting member, moves in the axial direction. As the movable shaft moves in the axial direction, the pulley diameters of the first and second pulley portions increase or decrease in opposite directions, thereby variably adjusting the gear ratio between the drive and driven shafts in opposite directions. Ru. For example, when the movable sheave is moved to the first fixed sheave side, the pulley diameter of the first pulley section becomes larger than the second pulley section, and the rotation of the drive pulley is decelerated by the intermediate pulley, and the rotation of the driven pulley is reduced. It becomes a low speed state where it is transmitted.

In that case, in the above-mentioned speed change switching mechanism, the cam is moved in the axial direction by engagement of the outer periphery cam groove with the cam follower to drive the movable shaft, and the pulley diameters of the first and second pulley parts are increased or decreased. , the movable shift can be driven with a small force, reducing the operating force required during gear shifting operations. Moreover,
Since a bearing is interposed between the movable sheave and one of the cam or the cam follower, the resistance from the movable sheave when operating the operating lever is small, and the operating force can be further reduced.

Furthermore, as the pulley diameters of both pulley portions of the intermediate pulley change in opposite directions due to the movement of the movable sheave, the V-belt hooked on the pulley portion where the pulley diameter increases tends to tighten, and the pulley diameter decreases. On the other hand, the belt that is hooked on the pulley part tries to loosen, but because the intermediate shaft that supports the intermediate pulley is attached to a moving member that can move toward and away from the drive shaft and the driven shaft. , the intermediate pulley (intermediate shaft) is pulled by the belt on the tension side and approaches the driving or driven pulley on which the belt is hooked, and the movement of this intermediate pulley causes the belt on the slack side to be pulled. Each belt will be maintained at the proper tension. the result,
Even if the length of the belt is lengthened and the gear ratio of the transmission is set to a large value, belt loosening during gear shifting can be suppressed without the need for an idler pulley or counter pulley, thereby extending the life of the belt. can be maintained.

In the invention described in claim (3), when the cam groove of the cam in the speed change switching mechanism is rotated around the intermediate shaft by operating the operating lever, the intermediate shaft is connected to the operating lever. If the operating part of the operating lever is tilted so that it moves in the opposite direction to the moving direction of the operating part, even if the intermediate pulley moves during gear shifting, the operating part of the operating lever will move in the opposite direction. Since it does not move, its large displacement can be suppressed, which is advantageous for operating the operating lever.

(Example) Hereinafter, an example of the present invention will be described based on the drawings.

Figures 1 and 2 show the overall configuration of a continuously variable transmission A in which the present invention is applied to a combine harvester, which is one of the agricultural machines. 1 is an engine mounted on the combine, and this output shaft 2 is the The output shaft 2 is provided with a belt groove 3 having a substantially V-shaped cross section.
A drive pulley 3, which is a V-pulley having a diameter of 1.a, is rotatably and non-slidably attached. 4 is a rotatable transmission output shaft arranged parallel to the engine output shaft 2, and this output shaft 4 is connected to a drive mechanism (not shown) of a combine harvester. The output shaft 4 is provided with a belt groove 5a having a substantially V-shaped cross section at a position offset from the drive pulley 3.
A driven pulley 5, which is a V-pulley having a diameter, is integrally rotatable and non-slidably attached, and the pulley diameters of both pulleys 3 and 5 are set to be the same.

6 is the engine output shaft 2 and the transmission output shaft 4
The support arm is disposed between the output shafts 2 and 4, and its lower end is supported by a fixed body 7 (for example, the frame of a combine harvester) so as to be able to swing with a swing center parallel to both output shafts 2 and 4 through a bearing 8. There is. The upper end (swinging end) of this support arm 6 is located between the engine output shaft 2 and the transmission output shaft 4, and an intermediate shaft 9 extending parallel to both shafts 2 and 4 is rotatably attached to the upper end. Supported. Therefore, the support arm 6 constitutes a moving member that can move the intermediate shaft 9 in a direction toward and away from both shafts 2 and 4 along a plane orthogonal to the engine output shaft 2 and the transmission output shaft 4. ing.

An intermediate pulley 10 is supported on the intermediate shaft 9. As shown in enlarged detail in FIG.
A pair of fixed sheaves 11 and 12 are slidably and rotatably supported on an intermediate shaft 9 between the fixed sheaves 11 and 12, and first and second shafts are respectively provided between the fixed sheaves 11 and 12. 1 pair of pulley parts 1
4 and 15 (FIG. 3 is an enlarged cross-sectional view taken along the - line in FIG. 13 are shown in different positions). Further, the first fixed sheave 11 is provided with, for example, three rod insertion holes 16, 16... (only one shown) that pass through the vicinity of the boss portion 11a and are spaced at equal angular intervals in the circumferential direction. ing. A first belt 17 made of a V-belt is disposed between the first pulley section 14 and the belt groove 3a of the driving pulley 3, and a first belt 17 made of a V-belt is disposed between the second pulley section 15 and the belt groove 5a of the driven pulley 5. A second belt 18 similarly made of a V-belt is wound around each of the belts, and as the movable sheave 13 moves in the axial direction, both the first and second pulley portions 14, 1
The rotation speed between the driving and driven pulleys 3 and 5 is changed steplessly by increasing and decreasing the diameters of the pulleys 5 in opposite directions.

The movable sheave 13 of the intermediate pulley 10 is connected to a speed changing mechanism 19 that moves the movable sheave 13 in the axial direction and changes the speed of rotation between the driving and driven pulleys 3 and 5. The speed change switching mechanism 19 is
A substantially half-cylindrical cam 20 is provided at the upper end of the support arm 6 that supports the intermediate shaft 9 so as to surround the intermediate shaft 9. A pair of cam grooves 21, 21 (only one is shown) extending in a shape are formed to face each other in the horizontal direction.

Further, the movable sheave 13 is provided with the first fixed sheave 11 through its rod insertion holes 16 and 1.
For example, three rods 22, 22, . . . are fixed together at their inner ends as connecting members passing through the rods 22, 22, .
The outer end of the cam follower 23 is integrated into a ring portion 22a, and a cam follower 23 is supported on the ring portion 22a through a bearing 24 so as to be relatively rotatable and slidable. A roller 25 that fits into each of the 20 cam grooves 21 and rolls is rotatably supported via a shaft 26. Further, an operating lever 27 having an operating portion 27a at the upper end is attached to the upper outer circumference of the cam follower 23. By operating the operating lever 27, the cam follower 23 is rotated around the intermediate shaft 9, and the roller 25 is rotated. The movable shaft 13 connected to the cam follower 23 via the bearing 24 and the rods 22, 22, . It is designed to be moved.

Each cam groove 21 of the cam 20 is arranged so that when the operating lever 27 is operated and the cam follower 23 is rotated around the intermediate shaft 9, the intermediate shaft 9 moves in the opposite direction to the moving direction of the operating portion 27a at the upper end of the operating lever 27. Tilt to move in direction. That is, cam groove 2
1, when the operating lever 27 is rotated to the low speed position (Lo) on the driven pulley 5 side as shown in FIGS. 4 and 5, the lower side of the intermediate shaft 9 in FIG. As shown in FIG. The rotation is decelerated by the intermediate pulley 10 and transmitted to the driven pulley 5 to a low speed state, and the tension of the second belt 18 due to the increase in the pulley diameter of the first pulley portion 14 causes the intermediate pulley 10 to become a driving pulley. Move it to the 3rd side. On the other hand, when the operation lever 27 is reversely rotated to the high speed position (Hi) on the drive pulley 3 side, the movable shaft 13 is moved to the second fixed shaft position as shown in the upper part of the intermediate shaft 9 in FIG. 12 side, and the second pulley part 15
By making the diameter of the pulley larger than that of the first pulley part 14, the rotation of the driving pulley 3 is increased by the intermediate pulley 10 and is transmitted to the driven pulley 5 at high speed. It is configured to be moved toward the driven pulley 5 by the tension of the belt 17.

Incidentally, as shown in FIG. 3, the intermediate pulley 10
The boss portion 12a of the second fixed sheave 12 in
A bearing 28 on which the second belt 18 can ride is supported at a portion corresponding to the bottom of the belt groove of the second pulley portion 15.
7 to the neutral position (N) at the end on the driven pulley 5 side, as the movable sheave 13 moves to the stroke end on the first fixed sheave 11 side, the second belt 18 is moved to the bearing 28. the intermediate shaft 9 and the belt 18 or the driven pulley 5 are cut off.
The transmission A is brought into a neutral state.

Further, as shown in FIG. 2, the driven pulley 5
A tension pulley 29 that presses the back surface of the second belt 18 on the slack side by the tension spring force of the spring 30 is disposed between the second belt 18 and the intermediate pulley 10 .

Next, the operation of the above embodiment will be explained.

When switching the transmission A to a low speed state, move the operating lever 27 of the transmission switching mechanism 19 to the low speed position (Lo).
Positioned in By switching the operating lever 27, the cam follower 23 integrated with the lever 27 rotates counterclockwise in FIG. 2, and as a result of this rotation,
A roller 25 on the outer periphery of the cam follower 23 rolls within the cam groove 21 of the cam 20, and the cam follower 23 moves rightward in FIG. 4 along the axial direction. This movement of the cam follower 23 in the axial direction causes the cam follower 23 to be attached to the bearing 24 and the rods 22, 2.
2, intermediate pulley 10 connected via...
The movable sheave 13 approaches the first fixed sheave 11, and the pulley diameter of the first pulley portion 14 becomes larger than that of the second pulley portion 15. As a result, the rotation of the drive pulley 3 is decelerated and transmitted to the intermediate pulley 10, the rotation of the intermediate pulley 10 is decelerated and transmitted to the driven pulley 5, and the rotation of the engine output shaft 2 is decelerated and transmitted to the transmission. This is transmitted to the output shaft 4, and the transmission A enters a deceleration state.

At that time, by moving the movable sheave 13 toward the first fixed sheave 11, the first pulley portion 1
As the diameter of the pulley 4 becomes larger than that of the second pulley part 15, the first belt 17, which is hooked on the first pulley part 14 whose diameter increases, tries to tighten, and the pulley diameter becomes smaller. The second belt 18 hooked on the second pulley portion 15 tries to loosen, but the intermediate shaft 9 supporting the intermediate pulley 10 is attached to the upper end of the support arm 6 and the engine output shaft 2 and Since the intermediate pulley 10 (intermediate shaft 9) can approach and separate from the transmission output shaft 4, the intermediate pulley 10 (intermediate shaft 9) approaches the drive pulley 3 side under tension by the first belt 17, which is the tension side, and the intermediate pulley 10 As a result of this movement, the second belt 18 on the slack side is pulled, and the belt 18 is maintained at an appropriate tension.

On the other hand, when switching the transmission A to a high speed state, on the other hand, the operating lever 27 is positioned at the high speed position (Hi). By this switching operation, the cam follower 23 rotates in the clockwise direction in FIG.
Move to the left in the diagram. Due to this movement, the movable sheave 13 of the intermediate pulley 10 moves toward the second fixed sheave 12, and the pulley diameter of the first pulley portion 14 becomes smaller than that of the second pulley portion 15. As a result, the rotation of the drive pulley 3 is accelerated and transmitted to the intermediate pulley 10, and the rotation of the intermediate pulley 10 is increased.
The rotation of the engine output shaft 2 is increased in speed and transmitted to the driven pulley 5, the rotation of the engine output shaft 2 is increased in speed and transmitted to the transmission output shaft 4, and the transmission A is brought into a speed increasing state.

At that time, similarly to the above, as the pulley diameter of the second pulley part 15 of the intermediate pulley 10 becomes larger than the first pulley part 14, the second The belt 18 of the belt 18 tends to be tensioned, and the first belt 17 hooked on the first pulley portion 14 whose pulley diameter becomes smaller tends to loosen, so the intermediate pulley 10 is
The second belt 18 approaches the driven pulley 5 side, and as the intermediate pulley 10 moves, the first belt 17 on the slack side is pulled.
The belt 17 is kept under proper tension.

Further, when the operating lever 27 is positioned beyond the low speed position (Lo) to the neutral position (N), the cam follower 23 reaches its stroke end, the pulley diameter of the first pulley portion 14 becomes maximum, and the The pulley diameter of the second pulley portion 15 is the smallest. In this state, the second pulley portion 1
As the radius of
As a result of this belt 18 riding up, the rotation of the intermediate shaft 9 is no longer transmitted to the second belt 18, and as a result, power transmission between the drive and driven pulleys 3 and 5 is cut off, resulting in a neutral state.

Therefore, in this embodiment, even when the pulley portions 14 and 15 of the intermediate pulley 10 change in the opposite direction during gear shifting of the transmission A, each belt 17 and 18 is always maintained at an appropriate tension. Even if the lengths of the belts 17 and 18 are increased to set a large gear ratio of the transmission A, loosening of the belt during gear shifting can be suppressed without requiring an idler pulley or a counter pulley. It is possible to increase the gear ratio of the transmission A while increasing the service life of the transmission A.

Further, the cam 20 in the speed change switching mechanism 19
By the engagement of each cam groove 21 with the roller 25 of the cam follower 23, the movable shaft 13 is moved in the axial direction, and the first and second pulley portions 14, 1 are moved.
In order to change the pulley diameter of 5, the movable sieve 1
3 can be driven with a small amount of force, and the operating force required for shifting operations can be reduced. Moreover, since the movable sheave 13 and the cam follower 23 are connected via the bearing 24, the resistance from the movable sheave 13 when the cam follower 23 is rotated is small, and the operating force can be further reduced.

Furthermore, the cam 2 in the speed change switching mechanism 19
The cam groove 21 of No. 0 is configured such that when the operating lever 27 is operated to rotate the cam follower 23 around the intermediate shaft 9, the intermediate shaft 9 moves in the opposite direction to the moving direction of the operating portion 27a of the operating lever 27. Since it is inclined, when the operating part 27a moves during gear shifting, the intermediate pulley 10 moves in the opposite direction, and the operating part 27a of the operating lever 27 does not absolutely move, so that the large Displacement can be suppressed.

In the above embodiment, the cam 20 in the speed change switching mechanism 19 is fixed to the upper end of the support arm 6, and the cam follower 23 having the roller 25 that engages with the cam groove 21 of the cam 20 is connected to the movable shaft 13 of the intermediate pulley 10. However, conversely, the cam may be connected to the movable shaft 13 and the cam follower may be fixed to the support arm 6, and the same effects as in the above embodiment can be achieved.

Further, in the above embodiment, the intermediate shaft 9 supporting the intermediate pulley 10 is provided at the upper end of the support arm 6 that can swing around the rotation center parallel to the intermediate shaft 9. and provided on a movable member that can slide in a direction toward and away from the output shaft 4,
The intermediate pulley 10 may also be moved.

Furthermore, in the above embodiment, the tension pulley 2
9 is provided on the driven side, but it may be provided on the drive side.
However, in order to reliably cut off the power transmission in neutral and improve so-called clutch disengagement, it is preferable to provide it on the driven side as in the above embodiment.

Furthermore, the present invention can be applied not only to combine harvesters such as those in the above embodiment, but also to other agricultural machinery such as harvesters, and to transmission devices with relatively low load transmission capacity, such as transmission devices for lawn mowers and snow blowers. Needless to say.

(Effect of the invention) As explained above, according to the invention recited in claim (1), the driving and driven pulleys, the intermediate pulley disposed between both pulleys, and the pulley portions of the driving and driven pulleys and the intermediate pulley. In a pulley type transmission equipped with a pair of belts that are wound around In addition, by supporting the intermediate pulley on a moving member that can move toward and away from the driving and driven pulleys, it is possible to reduce the operating force when changing gears, and to By moving the intermediate pulley using a belt hooked on one of the intermediate pulleys and pulling the belt hooked on the other pulley, each belt can be maintained at an appropriate tension, and the length of the belt can be adjusted. Even if you increase the gear ratio of the transmission by making it longer,
Loosening of the belt during gear shifting can be suppressed without requiring an idler pulley or a rear tension pulley, and thus it is possible to both extend the life of the belts 17 and 18 and increase the gear ratio of the transmission A. can.

Further, according to the invention described in claim (3), when the cam groove of the cam in the speed change switching mechanism is rotated around the intermediate shaft by operating the operating lever, the intermediate pulley is rotated. If the control lever is tilted so that it moves in the opposite direction to the movement direction of the control lever's control section, the movement of the intermediate pulley and the movement of the control lever's control section will cancel each other out during gear shifting, so that large displacements of the control lever's control section will be avoided. can be suppressed, which is advantageous for operating the operating lever.

[Brief explanation of drawings]

The drawings show an embodiment of the present invention, in which Fig. 1 is a schematic plan view of the transmission, Fig. 2 is a schematic front view thereof, Fig. 3 is an enlarged sectional view taken along the line - - in Fig. 4, and Fig. 5 is a front view schematically showing the movement of the intermediate pulley as the operating lever is operated. FIG. A... Transmission, 2... Engine output shaft (drive shaft), 3... Drive pulley, 4... Transmission output shaft (driven shaft), 5... Driven pulley, 6... Support arm (moving member) , 9... Intermediate shaft, 10... Intermediate pulley, 11... First fixed shaft, 12... Second
Fixed sieve, 13...Movable sieve, 14...
...First pulley part, 15...Second pulley part, 1
7...First belt, 18...Second belt, 1
9... Speed change mechanism, 20... Cam, 21... Cam groove, 22... Rod (connection member), 23... Cam follower, 24... Bearing, 25... Roller, 27... Operation lever.

Claims (1)

[Claims for Utility Model Registration] (1) A drive pulley supported by a drive shaft, a driven pulley supported by a driven shaft parallel to the drive shaft,
an intermediate pulley located approximately between the drive and driven shafts and supported on an intermediate shaft parallel to both axes, and having first and second pulley parts; a first pulley part of the drive pulley and the intermediate pulley; a first belt made of a V-belt wound between the driven pulley and a second pulley portion of the intermediate pulley; The intermediate pulley is slidably and rotatably supported by a pair of first and second fixed sheaves facing each other in the axial direction, and an intermediate shaft between the two fixed sheaves, and and a roughly abacus-shaped movable shaft forming the first and second pulley sections, respectively, and by moving the movable shaft in the axial direction, the pulley diameters of both pulley sections are moved in opposite directions. In a continuously variable transmission device in which the rotation speed between the drive and driven pulleys is variable, the intermediate shaft is movable in a direction toward and away from both shafts along a plane orthogonal to the drive shaft and the driven shaft. a plurality of connecting members attached to the movable member, each extending axially through the first fixed sheave of the intermediate pulley, and having an inner end fixed to the movable sheave; a cylindrical cam having a cam groove extending in the shape of a cylindrical cam, and a cylindrical cam follower disposed around an intermediate shaft and slidably engaged with the cam groove of the cam, one of the cam or the cam follower having a cam groove extending in the shape of the cam; The outer end of the connecting member is connected via a bearing and has an operating lever attached thereto, while the other end is integrally fixed to the movable member, and by operating the operating lever, one of the cams or cam followers can be rotated around the intermediate shaft. A continuously variable transmission device characterized by being provided with a speed change switching mechanism that rotates and moves a movable shift in an axial direction. (2) The movable member is an arm that is swingable around a rotation center parallel to the drive shaft and the driven shaft, and has an intermediate shaft fixed to its tip. Continuously variable transmission. (3) The cam groove of the cam is designed so that when the operating lever is operated to rotate either the cam or the cam follower around the intermediate shaft, the intermediate shaft moves in the opposite direction to the direction of movement of the operating part of the operating lever. The continuously variable transmission according to claim 1 or 2, characterized in that the transmission is inclined.