JPH10184835A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission which is simple in structure, transmits comparatively large torque, possesses sufficient strength and a life, and complies with wide gear shift ratio range. SOLUTION: A drive side external tooth gear 14 is arranged in a driving shaft 2, one end of an arm member 16 is supported in the driving shaft 2 rotationally, while in the other end of the arm member 16, a controlling external tooth gear 20 is installed in a pin 18 parallel to the driving shaft 2, and the gear 20 gears with the gear 14. A movable half part 34 of an interval variable V-pulley 30 arranged in a driven shaft 4 is energized in the direction in which it is brought close to a fixed half part 32 along a spline 33 by means of a compression coil spring 44. In the gear 20, a slanting face 21 touching a V- groove in the V-pulley 30 is formed. The arm member 16 is rotated around a driving shaft rotation center 2a, and a diameter directional distance from a driven shaft rotation center 4a to the position, in which the slanting face 21 of the gear 20 is brought into contact with the V-groove in the V-pulley 30, is varied, and as a result, a gear shift ratio can be continuously varied.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission technology for changing the number of revolutions of a rotary shaft, and more particularly to a continuously variable transmission capable of continuously changing the speed with a simple structure. INDUSTRIAL APPLICABILITY The continuously variable transmission according to the present invention can be effectively used, for example, as a transmission in a driving force transmission path of an automobile or various power machines.

[0002]

2. Description of the Related Art As a conventional continuously variable transmission having a simple structure, a V belt and a V pulley are generally used.

However, since such a conventional continuously variable transmission continuously deforms a V-belt made of rubber or the like, it cannot transmit a large torque, is easily damaged, and is sufficiently satisfactory in strength and life. Can not. Further, since the deformation of the V-belt is limited, it is difficult to widen the speed ratio range.

Therefore, an object of the present invention is to provide a simple structure,
It is an object of the present invention to provide a continuously variable transmission capable of transmitting a relatively large torque. Another object of the present invention is to provide a continuously variable transmission having sufficient strength and life. Still another object of the present invention is to provide a continuously variable transmission capable of a wide speed ratio range.

[0005]

According to the present invention, in order to achieve the above object, a drive-side external gear is attached to a drive-side rotary shaft, and one end of an arm member is connected to the drive-side rotary shaft. An external gear for control is supported so as to be rotatable around a rotation center, and is rotatable around a rotation center parallel to the rotation center of the drive side rotation shaft at the other end of the arm member. The control external gear is meshed with the drive-side external gear, and a V-groove is formed on the driven-side rotary shaft by a pair of halves having variable axial spacing. A V-pulley is attached, and the pair of halves of the V-pulley are urged by urging means in a direction approaching each other in an axial direction.
A contact portion that contacts the V groove of the pulley is formed, and by rotating the arm member about the rotation center of the drive-side rotation shaft, the contact portion of the external gear for control becomes A continuously variable transmission, wherein a speed ratio is continuously changed by changing a radial distance of a position where the pulley comes into contact with a V-groove from a rotation center of a driven-side rotary shaft.
Is provided.

In one aspect of the present invention, the V-pulley can reciprocate at least one of the pair of halves in the axial direction with respect to a spline fixedly arranged with respect to the driven-side rotation shaft. It is attached in such a way.

In one embodiment of the present invention, the urging means uses the elastic force of a spring.

In one embodiment of the present invention, the urging means uses fluid pressure.

In one aspect of the present invention, the contact portion of the external gear for control is a slope adapted to the V groove of the V pulley.

In one aspect of the present invention, the control external gear is mounted on the arm member so as to be reciprocable in the axial direction.

In one embodiment of the present invention, a fluid pressure driving means is used to rotate the arm member around a rotation center of the driving side rotation shaft.

In one embodiment of the present invention, an electric driving means is used to rotate the arm member around a rotation center of the driving-side rotation shaft.

The present invention also includes a continuously variable transmission configured by exchanging the drive side and the driven side of the above-described continuously variable transmission.

According to the present invention, in order to achieve the above object, a driving-side external gear is attached to a driving-side rotary shaft, and a final driven side coaxially arranged with the driving-side rotary shaft. A final driven external gear is attached to the rotating shaft,
One end of an arm member is supported so as to be rotatable around the rotation center of the drive-side rotation shaft and the final driven-side rotation shaft, and the other end of the arm member is provided with the drive-side rotation shaft and the final driven side. A first control external gear and a second control external gear are mounted so as to be rotatable around first and second rotation centers parallel to the rotation center of the rotation shaft, respectively. The external gear for control and the second external gear for control mesh with the drive-side external gear and the final driven-side external gear, respectively, and the intermediate rotation shaft has a variable axial interval.
First and second V-pulleys are provided so as to form a V-groove by the pair of halves, and the pair of halves of each of the first and second V-pulleys is biased by biasing means. The first control external gear has a contact portion that contacts the V-groove of the first V-pulley. A contact portion that contacts the V groove of the second V pulley is formed on the external gear for use, and the arm member is rotated around the rotation center of the drive side rotation shaft and the final driven side rotation shaft. As a result, the contact portion of the first control external gear is moved to the first V
The radial distance from the center of rotation of the intermediate rotary shaft at the position where the pulley contacts the V groove is changed, and the contact portion of the second control external gear contacts the V groove of the second V pulley. By changing the radial distance of the position from the center of rotation of the intermediate rotating shaft,
A continuously variable transmission, wherein the speed ratio is continuously changed.

In one embodiment of the present invention, the first and second rotation centers rotate the arm member around a rotation center of the driving-side rotation shaft and the final driven-side rotation shaft within an appropriate range. When the radial distance from the center of rotation of the intermediate rotation shaft at the position where the contact portion of the first control external gear contacts the V groove of the first V pulley increases, the second control The radial distance from the center of rotation of the intermediate rotary shaft at the position where the contact portion of the external gear for contact abuts on the V groove of the second V pulley decreases, and the contact portion of the first external gear for control is reduced. When the radial distance from the center of rotation of the intermediate rotary shaft at the position where it contacts the V groove of the first V pulley decreases,
It is set such that the radial distance from the rotation center of the intermediate rotation shaft at the position where the contact portion of the control external gear contacts the V groove of the second V pulley increases.

In one embodiment of the present invention, the first V
The urging means of the pulley and the urging means of the second V pulley are shared.

In one embodiment of the present invention, the first V
One of the pair of halves of the pulley is formed on a common member with one of the pair of halves of the second V-pulley.

In one embodiment of the present invention, the first and second V-pulleys move at least one of the pair of halves axially with respect to a spline fixedly arranged with respect to the intermediate rotation shaft. It is attached so that it can reciprocate.

In one embodiment of the present invention, the first and second control external gears are mounted on the arm member so as to be reciprocally movable in the axial direction.

[0020]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 is a perspective view showing a first embodiment of a continuously variable transmission according to the present invention, and FIGS. 2 and 3 are schematic sectional views thereof.

In these figures, reference numeral 2 denotes a drive-side rotary shaft (hereinafter, simply referred to as a "drive shaft"), and reference numeral 2a denotes the center of rotation. Reference numeral 4 denotes a driven rotation shaft (hereinafter, simply referred to as a "driven shaft"), and reference numeral 4a denotes a rotation center thereof. The drive shaft rotation center 2a and the driven shaft rotation center 4a are parallel to each other.

A motor (electric motor or internal combustion engine) 1 is connected to one end of the drive shaft 2, and the drive shaft 2 is driven and rotated by the motor 1. A spline 12 is formed on the drive shaft 2.
2, a drive-side external gear 14 is provided. The drive-side external gear 14 has a spline hole that meshes with the spline 12. The drive shaft 2 has
One end of an arm member 16 is mounted on both axial sides of the spline 12 so as to be rotatable around a drive shaft rotation center 2a via bearings. The arm member 1
A pin 18 parallel to the drive shaft rotation center 2a is attached to the other end of the motor 6, and a control external gear 20 is attached to the pin 18 so as to be rotatable via a bearing. 20a is a rotation center of the control external gear 20;
The rotation center 20a is parallel to the drive shaft rotation center 2a.
The control external gear 20 meshes with the driving side external gear 14.

At the center of the arm member 16, a branch 1
7, a pin 22 parallel to the drive shaft rotation center 2a is attached to the tip of the branch portion 17, and one end of a connecting member 24 is rotatably attached to the pin 22. A pin 26 parallel to the drive shaft rotation center 2a is rotatably attached to the other end of the connecting member 24. One end of a control rod 28 is fixed to the pin 26. The other end of the control rod 28 is connected to a control drive unit (not shown) capable of reciprocating the rod over a predetermined stroke (for example, an electric drive using a fluid pressure drive unit such as a hydraulic cylinder or a step motor). Means) are connected. Reference numeral 29 denotes a slide holding member for holding the control rod 28 so that it can reciprocate.

On the other hand, the driven shaft 4 has
0 is attached. The V pulley 30 is axially movable with respect to the fixed half 32 via a fixed half 32 fixed to the driven shaft 4 by a key connection and a spline 33 formed in the fixed half 32. And a movable half 34 attached to the main body. One end in the axial direction of the fixed half 32 is restricted from moving in the axial direction by a nut 36 adapted to a male screw formed on the driven shaft 4. The other end of the fixed half 32 in the axial direction is restricted from moving in the axial direction by the nut 42 via the locking member 38 and the cover member 40. The nut 42 is adapted to an external thread formed on the driven shaft 4. The locking member 38
A compression coil spring 44 having an extension force in the axial direction is interposed between the movable half 34 and the movable half 34, and thus the cone of the movable half 34 forming one half of the V groove of the V pulley 30 is formed. The surface is axially biased toward the conical surface of a fixed half 32 that forms the other half of the V-groove of V-pulley 30. The cover member 40 forms a space between the movable half portion 34 and the compression coil spring 44 in the space.
Is housed. As means for urging the two halves of the V-groove of the V-pulley 30 in the axial direction so as to be close to each other, other than a means using a spring elastic force such as the coil spring 44 or the like, a hydraulic or pneumatic It is also possible to employ a fluid pressure such as that described above.

An inclined surface (contact portion) 21 corresponding to the inclination of the V-groove of the V-pulley 30 is formed on the side surface of the outer peripheral portion of the external gear 20 for control. By contacting the conical surfaces of the fixed half portion 32 and the movable half portion 34 that form the V groove of the V pulley 30, torque is transmitted by frictional force. A groove extending in the circumferential direction can be formed on the inclined surface 21. The contact portion may be somewhat rounded so that the contact portion and the V groove of the V pulley 30 are in line contact.

In FIGS. 2 and 3, two different states are shown at the same time for explaining the operation of this embodiment. The operation will be described below mainly with reference to FIGS.

When the drive shaft 2 is driven and rotated by the prime mover 1, the drive-side external gear 20 spline-coupled to the drive shaft 2 rotates, and the control gear meshed with the drive-side external gear 20. V rotates around the rotation center 20a, and is in contact with the inclined surface 21 of the control gear 20.
The pulley 30 rotates, thus rotating the driven shaft 4 keyed to the fixed half 32 of the V-pulley 30.

FIG. 2 shows a first state (A) in which the inclined surface 21 of the control external gear 20 has entered the deep portion of the V groove of the V pulley 30 in a portion below the driven shaft rotation center 4a. In addition, the second state (B) in which the inclined surface 21 of the control external gear 20 enters only into the shallow portion of the V groove of the V pulley 30 in a portion above the driven shaft rotation center 4a is shown.
These two states (A) and (B) are also shown in FIG.

In the first state (A), as shown in FIG. 3, the control rod 28 is slid upward with respect to the slide holding member 29, and the rotation center of the drive shaft 2 and the driven shaft 4 and the rotation center of the control external gear 20 are located on the same plane.

In this state, as shown in FIG.
The movable half 34 of the V-pulley 30 is moved to the right in the axial direction along the spline 33 of the fixed half 32 against the compressive force of the coil spring 44. Driven shaft 4 rotates at a high rotational speed R _1.

On the other hand, in the second state (B), as shown in FIG. 3, the control rod 28 is slid downward with respect to the slide holding member 29, and
The rotation center of the control external gear 20 is located away from a plane formed by the rotation center of the driven shaft 4 and the rotation center of the driven shaft 4.

In this state, as shown in FIG.
As the control external gear 20 moves radially outward from the first state in the V groove of the V pulley 30, the movable half portion 34
The control gear 20 is moved to the left by a distance S from the first state in the axial direction along the spline 33 of the fixed half 32 based on the compressive force of the coil spring 44. The driven shaft 4 rotates at a low rotation speed R ₂ (<R ₁ ).

In the state between the first state (A) and the second state (B), the control rod 28, the control external gear 20, the coil spring 44, and the V pulley movable half 34
Take a state between the first state (A) and the second state (B), respectively.

As described above, in this embodiment, in order to control the gear ratio, the control external gear 20 is connected to the variable distance V pulley 3.
The amount of pushing into the zero V groove is changed. Since the drive-side external gear 14 and the control external gear 20 are always meshed with each other, there is no loss in driving force transmission at this portion.

Further, in this embodiment, since all the members involved in the transmission of the driving force do not deform during transmission of the driving force, they can be made of a high-strength material, for example, a metal. Thus, in addition to being able to transmit a relatively large torque, it is also possible to widen the speed ratio range, so that a sufficient strength and a sufficient life can be obtained.

Then, the control external gear 20 can be further retracted from the V groove of the V pulley 30 from the second state. In this case, since the connection between the control external gear 20 and the V pulley 30 can be released to interrupt the transmission of the driving force, the clutch also has the function of a clutch.

In the above embodiment, the continuously variable transmission according to the present invention is also constituted by exchanging the driving side and the driven side. Of course, in this case, the prime mover is transferred to the replaced prime mover.

FIGS. 4 and 5 are schematic sectional views showing a second embodiment of the continuously variable transmission according to the present invention. These sections correspond to FIGS. 2 and 3 of the first embodiment. It shows. 4 and 5, FIGS.
Members having the same functions as those in are denoted by the same reference numerals.

In this embodiment, the driving shaft 2 and the driving gear 1
4 are key-connected. The variable interval V pulley 30
The two movable halves 32 ′ and 34 are respectively engaged with splines 33 ′ of the driven shaft 4, and the compression coil springs 32 ″ and 44 are respectively engaged.
By biasing toward each other. The coil springs 32 ", 44 are respectively provided with nuts 36, 42.
It is locked by. In addition, the control rod 28 ′
The pin 22 ′ attached to the arm member 16 is engaged with the pin 22 ′ by being accommodated in the vertical cam slot 28 ″, and the control rod 28 ′ is moved in the longitudinal direction (horizontal direction). By moving the pin 2 in the cam slot 28 ″,
2 ′ slides up and down to take a first state (A) and a second state (B) (see FIG. 5).

The operation of the present embodiment is basically the same as that of the first embodiment, and the present embodiment also provides the same functions and effects as those of the first embodiment.

FIG. 6 is a perspective view showing a third embodiment of the continuously variable transmission according to the present invention, and FIGS. 7 and 8 are a schematic sectional view and a schematic side view, respectively. In these drawings, members having the same functions as those in FIGS. 1 to 5 are denoted by the same reference numerals.

In the present embodiment, the first continuously variable transmission unit and the second continuously variable transmission unit are provided by using two continuously variable transmissions as in the first and second embodiments. , And realizes an expansion of the speed ratio range.

In this embodiment, the driven shaft 4 of the first and second embodiments is used as an intermediate rotation shaft (hereinafter, simply referred to as "intermediate shaft"). The intermediate shaft 4 has a first
In addition to the variable distance V pulley 30, a second variable distance V pulley 31 is additionally provided. The V pulley 30 is
The movable half 34 ′ is mounted movably in the axial direction with respect to the fixed half 32 via a spline 33 ′ formed at
Having. The V pulley 31 is a movable half 3 of the V pulley 30.
4 ′, a first movable half 34 ″ formed on a common member,
A second movable half 34 movably mounted in the axial direction with respect to the first movable half 34 '' via a spline 33 'formed on the intermediate shaft 4. The second movable half 34 is connected to the shaft. The compression coil spring 44 for urging in the direction constitutes the urging means for the V pulley 31 and also constitutes the urging means for the V pulley 30 (that is, the urging means for the two V pulleys 30 and 31 is Common).

On the other hand, a final driven rotation shaft 50 is coaxially opposed to the drive shaft 2. 50a is the center of rotation of the final driven rotation shaft 50. The drive shaft 2 and the final driven side rotary shaft 50 are supported by a frame member (not shown) via a bearing, and the arm member 16 is also supported by the frame member (not shown) via a bearing. The final driven-side rotary gear 50 is provided with a final driven-side external gear 15. In addition, the arm member 16 includes
A pin 18 'parallel to the pin 18 is mounted, and a second control external gear 20' is mounted on the pin 18 'so as to be rotatable via a bearing. The control external gear 20 ′ meshes with the final driven external gear 15, and is formed on the conical surfaces of the first and second movable half portions 34 ″, 34 constituting the V groove of the V pulley 31. Abut.

That is, the relationship between the driving-side external gear 14, the control external gear 20 and the V pulley 30 of the first-stage continuously variable transmission unit, and the final driven-side outer gear of the second-stage continuously variable transmission unit. Tooth gear 15,
The relationship between the control external gear 20 'and the V pulley 31 is basically the same except that the direction of transmission of the rotational force is different.

However, as shown in FIG. 8, when viewed in the axial direction, the rotation center of the control external gear 20 and the rotation center of the control external gear 20 'correspond to the driving side external gear 14 And the circumferential position of the final driven external gear 15 with respect to the rotation center differs by the angle θ. This angle θ can be determined as follows. That is, the arm member 16 is connected to the driving side external gear 14.
And the angle θ around the rotation center of the final driven side external gear 15.
, The radial distance from the rotation center of the intermediate shaft at the position where the contact portion of the control external gear 20 contacts the V-groove of the V-pulley 30 increases. The radial distance from the center of rotation of the intermediate shaft at the position where the contact portion of the external gear 20 ′ contacts the V groove of the second V pulley 31 is reduced.
Conversely, when the arm member 16 is rotated around the rotation center of the driving-side external gear 14 and the final driven-side external gear 15 in the second direction opposite to the first direction within the range of the angle θ. The radial distance from the center of rotation of the intermediate shaft at the position where the contact portion of the control external gear 20 contacts the V groove of the V pulley 30 decreases, and the contact portion of the control external gear 20 ′ moves to the second position. The radial distance from the center of rotation of the intermediate shaft at the position where it contacts the V groove of the V pulley 31 increases.

In FIG. 8, the control external gear 20 of the first-stage continuously variable transmission unit takes the first state as shown in FIG. 3A, and the second-stage continuously variable transmission unit. Is in the second state as shown in FIG. 3 (B). Then, in FIG. 8, when the arm member 16 is rotated counterclockwise by the angle θ, the control external gear 20 of the first-stage continuously variable transmission unit is shifted to the second external gear 20 as shown in FIG. In the second state (position is different from that in FIG. 3), the control external gear 20 'of the second continuously variable transmission unit takes the first state as shown in FIG. Become.

Therefore, in this embodiment, if the speed ratio of the _first continuously variable transmission portion is n ₁ and the speed ratio of the second continuously variable transmission portion is n ₂ , n ₁ × A large gear ratio of n ₂ is possible. As a feature of the present embodiment, the shift operation of both the first-stage and second-stage continuously variable transmission portions is performed simultaneously using one arm member 16, so that the rotation of the arm member 16 is performed. An extremely large speed ratio range can be realized despite the small angle, and the speed change operation can be performed very quickly.

Further, as another feature of this embodiment, the urging means (coil spring 44) of the two V pulleys 30 and 31 attached to the intermediate shaft 4 is shared, and one of the V pulleys is used. One of a pair of 30 halves 3
4 ′ is one of the pair of halves of the other V-pulley 31
4 "is formed on a common member, so that by moving this common member in the axial direction, the interval between a pair of halves of the two V pulleys can be changed.
Half 3 of the second V pulley 31 pressed in the axial direction by 4
4 can be extremely reduced in the axial movement distance.
Thus, an automatic pressure adjusting cam (automatic pressure cam) can be used as the urging means. This means that the right end face of the half part 34 of the V-pulley 31 and the left end face of the fixing member 54 arranged on the right side of the V pulley 31 with respect to the direction of the center axis rotation center 4a, as shown in FIG. Opposite arrangement, V of half 34
The ball 52 is arranged between the mold concave portion and the V-shaped concave portion of the fixing member 54 (the ball 52 is arranged between the V-shaped concave portion of the half portion 34 and the V-shaped concave portion of the fixing member 54 in the circumferential direction). Three or more evenly provided). In this case, the fixing member 54 is fixed to the intermediate shaft 4 and the half 34 is
Is mounted so that it can move in the axial direction and rotate around the center of rotation 4a (ie, the splines shown in FIG. 7 are not used for the half portion 34).

This embodiment also has a clutch function. That is, in FIG. 8, the arm member 16 is rotated counterclockwise by the angle θ, and the control external gear 20 of the first-stage continuously variable transmission unit takes the second state and the second-stage continuously variable gear. After the control external gear 20 'of the transmission unit has taken the first state,
Further, when the arm member 16 is rotated counterclockwise to retreat the first control external gear 20 from the V groove of the V pulley 30, the connection between the first control external gear 20 and the V pulley 30 is established. It is released and the transmission of the driving force is cut off.

As described above, according to the present embodiment, a wide speed ratio range can be achieved, a large torque can be transmitted, and a clutch function can be provided even though the size can be reduced with a simple configuration. There are great advantages.

[0053]

As described above, according to the present invention, there is provided a continuously variable transmission having a simple structure, capable of transmitting a large torque, and having sufficient strength and sufficient life. Further, according to the present invention, it is possible to widen the shift range in such a continuously variable transmission. Furthermore, by using the continuously variable transmission of the present invention in combination with a plurality of speeds and simultaneously controlling the plurality of speeds by a common control means, it is possible to reduce the size of the gears with a simple structure and to achieve a wide speed change. An improved continuously variable transmission is provided that has a ratio range, is capable of transmitting large torque, and has a clutch function.

[Brief description of the drawings]

FIG. 1 is a perspective view showing a first embodiment of a continuously variable transmission according to the present invention.

FIG. 2 is a schematic cross-sectional view of the embodiment of FIG.

FIG. 3 is a schematic sectional view of the embodiment of FIG. 1;

FIG. 4 is a schematic sectional view showing a second embodiment of a continuously variable transmission according to the present invention.

5 is a schematic cross-sectional view of the embodiment of FIG.

FIG. 6 is a perspective view illustrating a continuously variable transmission according to a third embodiment of the present invention.

FIG. 7 is a schematic sectional view of the embodiment of FIG. 6;

FIG. 8 is a schematic side view of the embodiment of FIG.

FIG. 9 is a circumferential development partial view showing a modification of the embodiment of FIG. 6;

[Explanation of symbols]

 Reference Signs List 2 drive shaft 2a drive shaft rotation center 4 driven shaft (intermediate shaft) 4a driven shaft rotation center (intermediate shaft rotation center) 12 spline 14 driving-side external gear 15 final driven-side external gear 16 arm member 17 arm member branch 18 , 18 'Pin 20, 20' Control external gear 20a Control external gear rotation center 21 Control external gear outer peripheral slope 22, 22 'Pin 24 Connecting member 26 Pin 28 Control rod 28' Control rod 28 "Cam slot 29 Slide holding member 30, 31 Variable V-pulley 32 V-pulley fixed half 32 'V-pulley movable half 32" Compression coil spring 33, 33' Spline 34, 34 ', 34 "V-pulley movable half 36 Nut 38 Locking member 40 Cover member 42 Nut 44 Compression coil spring 50 Final driven side rotating shaft 50a Final driven side rotating shaft rotation Center 52 ball 54 fixed member

Claims (15)

[Claims] A drive-side external gear provided on the drive-side rotary shaft, and one end of an arm member is supported so as to be rotatable around a rotation center of the drive-side rotary shaft; A control external gear is attached to the other end of the member so as to be rotatable around a rotation center parallel to the rotation center of the drive side rotation shaft, and the control external gear is the drive side external gear. The driven-side rotating shaft is provided with a V-pulley which is formed with a pair of halves having a variable axial spacing so as to form a V-shaped groove. The urging means are urged in directions approaching each other in the axial direction. The control external gear has a contact portion that contacts the V groove of the V pulley. By rotating about the rotation center of the drive side rotation shaft, the control By changing the radial distance from the center of rotation of the driven-side rotary shaft at the position where the contact portion of the external gear contacts the V-groove of the V-pulley, the gear ratio is continuously changed. Features a continuously variable transmission. 2. The V-pulley is formed by attaching at least one of the pair of halves to a spline fixedly arranged with respect to the driven-side rotating shaft so as to be able to reciprocate in the axial direction. The continuously variable transmission according to claim 1, wherein: 3. The continuously variable transmission according to claim 1, wherein said urging means uses an elastic force of a spring. 4. The continuously variable transmission according to claim 1, wherein said urging means uses a fluid pressure. 5. The continuously variable transmission according to claim 1, wherein a contact portion of the external gear for control is a slope adapted to a V groove of the V pulley. 6. The continuously variable transmission according to claim 1, wherein the external gear for control is mounted on the arm member so as to be able to reciprocate in an axial direction. . 7. A fluid pressure drive means for rotating the arm member around a rotation center of the drive-side rotation shaft, according to claim 1, wherein: Continuously variable transmission. A fluid delivery device according to claim 1. 8. The apparatus according to claim 1, wherein an electric drive unit is used to rotate the arm member around a rotation center of the drive-side rotation shaft. Step transmission. 9. A continuously variable transmission, wherein the drive side and the driven side of the continuously variable transmission according to claim 1 are interchanged. 10. A driving-side external gear is attached to the driving-side rotating shaft, and a final driven-side external gear is attached to a final driven-side rotating shaft arranged coaxially with the driving-side rotating shaft. One end of the arm member is supported so as to be rotatable around the rotation center of the drive-side rotation shaft and the final driven-side rotation shaft, and the other end of the arm member is provided with the drive-side rotation shaft and the final driven shaft. A first control external gear and a second control external gear are mounted so as to be rotatable around first and second rotation centers parallel to the rotation center of the side rotation shaft, respectively. The control external gear and the second control external gear mesh with the driving-side external gear and the final driven-side external gear, respectively, and a pair of halves each having a variable axial spacing on the intermediate rotary shaft. First and second V-pulleys are formed so as to form V-grooves. The pair of halves of each of the first and second V pulleys are urged by urging means in a direction approaching each other in the axial direction. Has a contact portion that contacts the V groove of the first V pulley, and the second control external gear has a contact portion that contacts the V groove of the second V pulley. By rotating the arm member about the rotation center of the drive-side rotation shaft and the final driven-side rotation shaft, the first
The radial distance from the center of rotation of the intermediate rotary shaft at the position where the contact portion of the control external gear contacts the V groove of the first V pulley is changed, and the contact of the second control external gear is changed. By changing the radial distance from the center of rotation of the intermediate rotary shaft at the position where the contact portion comes into contact with the V groove of the second V pulley, the gear ratio is continuously changed. Continuously variable transmission. 11. The first and second rotation centers are configured such that, when the arm member is rotated within an appropriate range around the rotation centers of the drive-side rotation shaft and the final driven-side rotation shaft, the first and second rotation centers are moved to the first rotation center. When the radial distance from the rotation center of the intermediate rotation shaft at the position where the contact portion of the control external gear contacts the V groove of the first V pulley increases, the contact of the second control external gear increases. The radial distance from the center of rotation of the intermediate rotation shaft at the position where the contact portion contacts the V groove of the second V pulley decreases, and
When the radial distance from the center of rotation of the intermediate rotary shaft at the position where the contact portion of the control external gear contacts the V groove of the first V pulley decreases, the contact of the second control external gear may decrease. 11. The device according to claim 10, wherein the contact portion is set so that a radial distance from a center of rotation of the intermediate rotary shaft to a position where the contact portion contacts the V groove of the second V pulley increases. Continuously variable transmission. 12. The method according to claim 10, wherein the urging means for the first V-pulley and the urging means for the second V-pulley are shared. Continuously variable transmission. 13. One of a pair of halves of the first V-pulley is formed on a member common to one of a pair of halves of the second V-pulley. The continuously variable transmission according to any one of claims 10 to 12, wherein 14. The first and second V-pulleys are configured to reciprocate at least one of the pair of halves in an axial direction with respect to a spline fixed to the intermediate rotation shaft. The continuously variable transmission according to any one of claims 10 to 13, wherein the continuously variable transmission is mounted on a vehicle. 15. The apparatus according to claim 10, wherein the first and second control external gears are mounted on the arm member so as to be reciprocally movable in the axial direction. The continuously variable transmission according to any one of the preceding claims.