JPH10274304A - Frictional continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a traction drive style continuously variable transmission provided with a suitable structure for the purpose of transmitting continuously an output axis driving a high speed rotating body such as an impeller of a centrifugal blower or the like. SOLUTION: This frictional continuously variable transmission is provided with an input axis 11 being touched internally by plural cones 27 kept autorotatable and revoluvable, an output axis 15 touched externally by the plural of cones 27, a pressing spring 19 applying elastic pressing contact force between input/output axes 11, 15 and plural of cones 27, a speed change ring 26 slidably brought into press contact with each cones 27 and transmits the rotating power between the input/output axes 11, 15 via a rotation of the cones 27 and transmits the number of revolutions of the rotating power transmitted by the slide moving of a speed change ring 26, in this case it is provided with a cone support axis 30 bering the each cones 27.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a friction type continuously variable transmission, and more particularly to a friction type continuously variable transmission used as a speed increasing device in a centrifugal blower, a centrifugal compressor, a radial turbine, and the like.

[0002]

2. Description of the Related Art A device capable of obtaining a large gear ratio is 3K.
FIG. 13 shows a 3K-type traction drive type continuously variable transmission in which a planetary gear train is generally known, and is applied to a traction drive. FIG. 13 shows a case where the continuously variable transmission is used as a speed reducer. However, when the continuously variable transmission is used as a speed increase gear, the input / output shafts 6 and 7 are exchanged.

In this type of continuously variable transmission, a planetary cone 1
Are the input disk 2, the cam disk 3 and the transmission ring 4
One traction member is in contact with each of the three traction members. The planetary cone 1 has a structure dynamically balanced by the normal forces received at the three contact portions described above. In this case, gear shifting is performed by moving the transmission ring 4 in the input / output axial direction. Regardless of the axial movement of the transmission ring 4, the normal force at the three contact portions is balanced as described above. What can be held is that the contact portion between the input disk 2 and the planetary cone 1 is formed by a surface having a secondary curvature, so that the input disk 2 and the planetary cone 1 This is because the direction of the normal force acting on the contact portion between them changes. Therefore, the cone holder 5 has a function of merely holding the planetary cones 1 at equal intervals in the circumferential direction, and is not supported by other members.

[0004]

However, if the contact portion between the planetary cone 1 and the input disk 2 is constituted by a contact surface having a secondary curvature, the influence of spin increases. When the continuously variable transmission shown in FIG. 13 is used as a gearbox, when the output shaft is rotated at a high speed, the input disk 2 rotates at a high speed, and the moment of inertia of the output shaft system is large. Since the peripheral speed and spin at the contact portion are large, a large power loss occurs, and this type of continuously variable transmission is not suitable for use of a high-speed rotating centrifugal blower.

Accordingly, the present invention has been proposed in view of the above problems, and has as its object to continuously change the speed of an output shaft for driving a high-speed rotating body such as an impeller such as a centrifugal blower. SUMMARY OF THE INVENTION It is an object of the present invention to provide a traction drive type continuously variable transmission having a structure suitable for the present invention.

[0006]

The present invention has the following features as technical means for achieving the above object. An input shaft in which a plurality of cones rotatably held are inscribed, an output shaft in which the plurality of cones are circumscribed, and pressurizing means for applying elastic pressure between the input / output shaft and the plurality of cones. A friction-type continuously variable transmission that continuously changes the rotation speed while transmitting rotational power between the input and output shafts through rotation of the cone, and a cone supporting shaft that supports and supports each cone. And a holder body comprising the cone support shaft and a holder body integrally disposed at equal circumferential intervals. An input shaft in which a plurality of cones rotatably held are inscribed, an output shaft in which the plurality of cones are circumscribed, and pressurizing means for applying elastic pressure between the input / output shaft and the plurality of cones. A friction-type continuously variable transmission that continuously changes the rotation speed while transmitting rotational power between the input and output shafts through rotation of the cone, and a cone supporting shaft that supports and supports each cone. And a holder body having the cone support shafts inserted and fixed at equal circumferential intervals.

It is desirable that the holder main body be supported by a bearing on an input shaft. An input shaft in which a plurality of cones rotatably held are inscribed, an output shaft in which the plurality of cones are circumscribed, and pressurizing means for applying elastic pressure between the input / output shaft and the plurality of cones. A frictionless continuously variable transmission that continuously changes the rotation speed while transmitting rotational power between the input and output shafts through rotation of the cone, and restricts axial movement of each cone. A position restricting portion is provided between the output shaft and each cone or between each cone and the cone holder.

[0008]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS FIG. 1 to FIG.
2 and described in detail below. The following embodiment is applied to a 3K traction drive type continuously variable transmission in which an output shaft for driving a high-speed rotating body such as an impeller of a centrifugal blower is continuously variable.

This traction drive type continuously variable transmission has an overall structure as shown in FIG. First, the input shaft 11 is rotatably supported on the housing body 12 by bearings 13 and 14, and the output shaft 15 is rotatably supported on the front housing 16 by bearings 17 and 18. The input shaft 11 and the output shaft 15 are arranged so that their axes are on the same straight line by combining and integrating the input shaft 11 and the output shaft 16. The bearings 13 and 14 that support the input shaft 11 are provided with the housing body 1.
A pressurizing spring 19, which is a pressurizing means, is interposed between the input shaft 11 and the input shaft 11 and presses the input shaft 11 via the bearings 13 and 14 so that the elastic force is applied to the output shaft. Like that.

The inner shaft end of the input shaft 11 has a hollow shape whose diameter is increased integrally, and a cone 27 (described later) is formed on the inner diameter surface of the tip.
Of the input shaft traction part 2 in which the input side contact part 33 of
Has zero. Further, the inner shaft end of the output shaft 15 has a conical shape whose diameter is integrally reduced, and has an output shaft traction portion 21 with which the output side contact portions 34 and 35 of the cone 27 circumscribe the outer surface of the tip. An impeller 22 is fixedly supported at the outer shaft end of the output shaft 15. Note that an annular member 23 for regulating the axial position of the cone 27 is externally inserted into the output shaft 15.

On the other hand, the input / output shaft 1
For example, a ball screw 24 is installed in parallel with the gears 1 and 15, and a speed change ring 26 is attached via a ball bush 25 screwed to the ball screw 24.
Is pressed against the shift-side contact portion 36 of the cone 27,
The rotation of the ball screw 24 enables movement in the input / output axis direction.

A plurality of cones 27 are interposed between the input shaft traction unit 20, the output shaft traction unit 21, and the transmission ring 26. Here, the output shaft 1 that rotates at high speed
In order to reduce the moment of inertia and the peripheral speed of 5, the rotation radius of the output shaft traction portion 21 is reduced, and the generating line on the conical surface of the output shaft traction portion 21, the axis of the output shaft 15, and the rotation axis of the cone 27 are rotated. With a structure that intersects at one point,
Spin is prevented from occurring at the contact portion between the cone 27 and the output shaft 15. Due to such a structure, the angle between the rotation axis of the cone 27 and the input / output axes 11 and 15 is considerably small. As a result, the cone 27 has a shape that is long in the axial direction, the distance between the contact portions where the normal force and the tangential force (traction) act is also long, and the moment for causing the cone 27 to skew increases. If the supporting structure is not used, troubles such as rotation failure will occur.

The plurality of cones 27 are held at equal circumferential intervals by the cone holder 28 so that they can rotate and revolve. As shown in FIG. 3, the cone holder 28 is made of an integral body of a holder main body 29 and a cone support shaft 30, and the holder main body 29 is rotatably inserted coaxially with the input shaft 11 via a bearing 31. A plurality of cone support shafts 30 which are integrally erected on the main body 29 at equal circumferential intervals.
The cone 27 is rotatably supported via a bearing 32. With such a support structure for the cone 27, the skew of the cone 27 with respect to the input / output shafts 11 and 15 is prevented, and rotation due to skew and reduction in transmission efficiency are avoided.

The holder body 29 and the cone 2 described above are used.
For example, needle rollers with retainers can be used for the bearings 31 and 32 of the seventh embodiment, respectively, and the holder body 29 and the cone 27 are used as the rolling surfaces of the bearings 31 and 32. FIG.
In the embodiment of the present invention, two needle rollers with retainers having different sizes are used for the bearings 31 of the holder body 29. However, as another structure, as in the embodiment shown in FIG. It is also possible to use two needle rollers with the same size as the bearing 31 with a cage. Further, as the bearings of the holder body 29 and the cone 27, it is also possible to use a rolling bearing or a sliding bearing other than the above-described needle roller with cage.

Each of the cones 27 makes frictional contact with the input shaft traction portion 20 at one input side contact portion 33, and makes frictional contact with the output shaft traction portion 21 at two output side contact portions 34 and 35. Further, the transmission side frictional contact is made with the transmission ring 26 at the transmission side contact portion 36 whose diameter is reduced toward the front end. The output side contact portions 34 and 35 of the cone 27 contacting the output shaft traction portion 21 are conical surfaces having the same generatrix, and the generatrix of the output side contact portions 34 and 35 is the input side of the cone 27 contacting the input shaft traction portion 20. Both are set at a slight angle with respect to the output shaft 15 and the input shaft 11 together with the generatrix at the contact portion 33. Due to the shape of the contact portion between the input / output shaft traction portions 20 and 21 and the cone 27 and the axial force generated by the pressure spring 19, the contact portion between the input and output shaft traction portions 20 and 21 and the transmission ring 26 and the cone 27 is provided. Normal forces required for power transmission are generated at 33 to 36.

In this traction drive type continuously variable transmission, power is transmitted from the input shaft 11 to the input side contact portion 33 of the cone 27 via the input shaft traction portion 20, and the power is transmitted by the rotation motion and the revolving motion of the cone 27. And transmitted from the output side contact portions 34 and 35 of the cone 27 to the output shaft 15 via the output shaft traction portion 21. At this time, the transmission ring 26 is connected to the transmission side contact portion 36 of the cone 27.
The ratio between the rotation of the cone 27 and the revolution thereof is determined by the position where the cone 27 contacts, and the overall speed ratio is determined by the ratio. Further, the speed ratio is reduced by moving the speed change ring 26 in the input / output axis direction by the ball screw 24. Can be changed in steps. As a result, the output shaft 15 that drives the impeller 22 at high speed is continuously variable, so that the output shaft 15 can rotate at a constant speed even when the rotation speed of the input shaft 11 fluctuates.

Here, an oil bath lubrication system is the simplest lubrication system as a system for supplying lubricating oil to each contact portion or the like where power is transmitted. However, in the case of the traction drive type continuously variable transmission as in the present invention, in the oil bath lubrication system, the resistance of oil agitation due to the revolving motion of the cone 27 is large, and the power loss due to the agitation resistance increases as the rotation speed increases. become. Further, most of the lubricating oil is bounced radially outward due to centrifugal force due to the rotation and revolution of the cone 27, and sufficient lubricating oil is not supplied to the output shaft traction portion 21 having the highest peripheral speed. The bath lubrication system is not suitable. In addition, instead of the oil bath lubrication system, there is a system in which lubricating oil is sprayed from the outside in the radial direction. However, this system is also unsuitable because it causes the output shaft traction unit 21 to run out of lubricating oil.

Therefore, oil passages 37 to 40 are provided inside the cone holder 28 as shown in FIGS. First, lubricating oil is pumped through an oil passage 37 provided in the axial direction of the holder body 29 toward a contact portion between the output shaft traction portion 21 and the cone 27. The lubricating oil supplied in this manner is scattered uniformly radially outward by the rotation of the output shaft 15 and the centrifugal force caused by the rotation and revolution of the cone 27, so that the other contact portions (the input shaft traction portion 20 and the cone 27,
Sufficient lubricating oil is also supplied to the transmission ring 26 and the cone 27).

Further, by forcibly supplying the lubricating oil to the bearing 32 through the oil passage 40 provided inside the cone support shaft 30 via the oil passages 37 and 39, damage to the bearing 32 due to insufficient lubricating oil is prevented. I do. Furthermore, by supplying lubricating oil to the bearing 31 through oil passages 38 and 39 provided in the radial direction of the holder main body 29 via the oil passage 37, seizure or the like due to insufficient lubricating oil is prevented.

The lubricating oil is supplied to the cone holder 28 by providing an oil passage 41 in the housing body 12 as shown in FIG. The second spacer 43 is interposed between the inner races. As the input shaft 11 rotates, the first spacer 4
2 is stationary, and the second spacer 43 rotates together with the input shaft 11, but the inner diameter of the first spacer 42 is slightly larger than the outer diameter of the second spacer 43 so as not to greatly deteriorate the sealing property between the spacers. Reduce the sliding resistance between spacers. The first and second spacers 42 and 43 are provided with holes 44 and 45 penetrating in the radial direction, and the lubricating oil that has passed through the oil passage 41 of the housing body 12 is used for the first and second spacers 42 and 43. Input shaft 1 through holes 44 and 45 of
1 and supplied to the cone holder 28.

By the way, the cone 27 described above is
Centrifugal force and gyro moment acting at high speed rotation,
The shape is such that normal forces received from the four contact portions are balanced mechanically. However, if the manufacturing accuracy of the positional relationship of the cone support shaft 30 with respect to the holder body 29 is poor, the cone 2
7 is not established, and an excessive load acts on the cone support shaft 30 and the bearing 32. In addition, the balance of the forces received by the input shaft traction unit 20 or the output shaft traction unit 21 from the plurality of cones 27 is lost, and the bearings 13 and 14 of the input shaft 11 or the bearings 17 and 18 of the output shaft 15 are excessively radially biased. Load acts. As a result, the life of the bearings 13 and 14 of the input shaft 11 or the bearings 17 and 18 of the output shaft 15 is shortened or early damage is caused. Further, the manufacturing accuracy of the cone holder 28 is low, and the cone 27 is
In the case of skew with respect to 15, the power transmission efficiency is greatly reduced, so that it becomes impossible to rotate.

Therefore, as in the above-described embodiment, the cone holder 28 is formed of an integral body of the holder body 29 and the cone support shaft 30 (see FIG. 3), and the positional relationship of the cone support shaft 30 with respect to the holder body 29. Had good manufacturing accuracy.

However, when the holder body 29 and the cone support shaft 30 are integrally formed, each of the cone support shafts 3
A large space between 0 must be cut out by turning or milling. For this reason, there are many wasteful materials that need to be discarded, and it takes a long time for processing, which may increase the manufacturing cost.

Therefore, for example, FIG. 6 and FIG.
As shown in (b), the holder body 29 'and the cone support shaft 3
The manufacturing cost can be reduced by manufacturing the cone holder 28 'in a state where the cone holder 28' is separate from 0 '. That is, the holder body 2
9 ′ indicates that each cone support shaft 3
It is manufactured by processing such that a plane perpendicular to 0 'forms a triangular pyramid surface, and has a fitting hole 29a' into which the cone support shaft 30 'is inserted. Further, the cone support shaft 30 ′ has a fitting portion 30 a ′ into the holder main body 30 ′ and a cone support portion 30 ′.
b ′, the holder body 29 ′ of the cone support shaft 30 ′
A flange 30c 'is formed to regulate the length of insertion into the flange 30c'.

The cone holder 28 'in which the holder body 29' and the cone support shaft 30 'are separated from each other is manufactured by assembling the cone support shaft 30' into the holder body 29 'by press-fitting, shrink-fitting or the like. You. At this time, the side surface of the flange portion 30c 'provided on the cone support shaft 30' and the holder body 29 '
When the triangular pyramid surfaces of the cone support shaft 30 'are assembled, the strength of the cone support shaft 30' after assembly is improved. Also, the cone support shaft 30 'is not finished until the last step, leaving a margin for the cone support portion 30b'. Then, necessary accuracy can be obtained by finishing (grinding) the cone support portion 30b 'after assembly.

As shown in FIG. 8, a cone holder 28 in which a holder body 29 and a cone support shaft 30 are integrally formed.
Similarly to the case (see FIG. 5), if the oil passages 37 'to 40' are formed in the holder main body 29 'and the cone support shaft 30', it becomes possible to supply a sufficient lubricating oil to the contact portion easily and easily. Further, the supply of the lubricating oil to the cone holder 28 'is performed in the same manner as in the above-described embodiment in which the oil passage 41 is formed in the housing 12 and the first and second spacers 42 and 43 are provided as shown in FIG. What is necessary is just to make it the same.

If the input shaft traction portion 20 and the output shaft traction portion 21 have perfect coaxiality, the plurality of cones 27 arranged at equal circumferential intervals are all restricted to the same position in the axial direction. become. But in practice,
Due to the manufacturing accuracy of each part, the assembling accuracy, the rattling in the radial direction of each bearing, and the like, there is a possibility that an axial variation may occur between the cones 27 during operation.

If this variation is large, the input / output shafts 11,
With the rotation of No. 15, an eccentric load is generated in the input / output shaft traction units 20 and 21 and each bearing, and there is a high possibility that uneven rotation, a reduction in efficiency, a reduction in bearing life, and the like are caused. Therefore, the axial position of the cone 27 must be regulated.
When the position restricting portion is provided, the cone 27 and the axial position restricting portion come into sliding contact with each other, and it is necessary to minimize the power loss due to this contact.

Therefore, as shown in FIG.
5, a flange 2 for regulating the axial position of the cone 27;
3 'is integrally formed as one of the axial position regulating portions. Further, as another axial position regulating portion, one annular member 23 can be extrapolated to the output shaft 15 and disposed between the output shaft 15 and the cone 27 as shown in FIG. (See FIGS. 1, 2 and 4). Further, as shown in FIG. 3C, a plurality of (two in the figure) annular members 23
a and 23b can be extrapolated to the output shaft 15 and, as shown in FIG.
An elastic member 46 such as a disc spring, a spring washer, or a corrugated washer may be interposed therebetween.

As a result, even if any of the plurality of cones 27 attempts to move to the output shaft side, all the cones 27 are restricted by the flange 23 ′ or the annular member 23.
Are held in the same axial position. In addition, a plurality of cones 2
7 moves to the input shaft side, the remaining cone 27 moves to the output shaft side due to the restriction by the inner diameter of the transmission ring 26, and is provided between the output shaft 15 and the cone 27. The cone 27 is held at the same axial position by interference with the flange portion 23 'or the annular member 23.

Further, by forming the annular member 23 with a material having excellent slidability (copper alloy, oil-impregnated bearing material, resin material, etc.), power loss due to sliding contact between the cone 27 and the annular member 23 is obtained. Can be lowered. Further, in the case where the ring members 23a and 23b are formed, the slip speed difference between the cone 27 and the output shaft 15 or the slip speed difference between the cone 27 and the cone holder 28 is dispersed by the slip between the ring members 23a and 23b. Power loss can be reduced. Further, when the elastic member 46 is interposed between the ring member 23 and the output shaft 15, the force acting between the cone 27 and the ring member 23 can always be made substantially constant. The efficiency does not decrease due to excessive interference with the ring member 23.

As shown in FIGS. 10 (a) to 10 (d) and FIG. 11, the cone 2 is formed on the flange 23 'or the annular member 23.
7 or the contact surface m contacting the output shaft 15 or, in the case of a plurality of annular members 23a and 23b, the contact surface m between the annular members.
Can be formed into a predetermined shape that generates a dynamic pressure that supports the axial force. In this case, power loss due to sliding contact can be reduced.

In the above, the cone 27 is attached to the output shaft 15.
Although the case where the axial position regulating portion of was provided was described,
It is also possible to provide the cone support shaft 30 of the cone holder 28 with an axial position restricting portion of the cone 27, for example, as shown in FIG.
2 (a), a flange 47 'is integrally formed at the base end of the cone support shaft 30, or the annular member 47 is connected to the base end of the cone support shaft 30 as shown in FIG. 2 (b). The elastic member 48 such as a disc spring, a spring washer, or a corrugated washer can be interposed between the annular member 47 and the cone support shaft 30 as shown in FIG. It is.

[0034]

According to the present invention, a continuously variable transmission having a large practical value and having a structure suitable for use in continuously variable transmission of an output shaft for driving a high-speed rotating body such as an impeller of a centrifugal blower or the like. And the following effects can be obtained. The skew of the cone with respect to the input / output shaft is prevented by providing a cone holder composed of a cone support shaft that supports each cone as a bearing and a holder body in which the cone support shafts are integrally disposed at equal circumferential intervals. In addition, it is possible to prevent rotation failure and reduction in transmission efficiency due to skew, thereby realizing a highly reliable and high-performance continuously variable transmission. By providing a cone holder consisting of a cone support shaft that supports each cone as a bearing and a holder body in which the cone support shafts are inserted and fixed at equal circumferential intervals, the holder body and the cone support shaft are manufactured as a single unit. Compared to the case, no wasteful material to be discarded is generated, and the time required for processing is reduced, so that the manufacturing cost can be reduced. By disposing the position restricting portion for restricting the axial movement of each cone between the output shaft and each cone or between each cone and the cone holder, all the cones are surely at the same axial position. Thus, it is possible to prevent a decrease in efficiency and a decrease in the life of the bearing due to an eccentric load acting on the input / output traction portion and each bearing, thereby realizing a highly reliable and high-performance continuously variable transmission.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing the overall structure of a traction drive type continuously variable transmission according to an embodiment of the present invention.

FIG. 2 is a cross-sectional view showing another embodiment of the present invention.

FIG. 3A is a side view showing a cone holder that supports a plurality of cones. FIG. 3B is a front view of FIG.

FIG. 4 is a cross-sectional view when an oil passage is formed in a cone holder.

5A is a side view when an oil passage is formed in a cone holder. FIG. 5B is a cross-sectional view taken along line AA in FIG.

FIG. 6 is a front view including a partial cross section showing a cone holder in which a holder main body and a cone support shaft are separate bodies.

7A is a front view including a partial cross section showing the holder main body of FIG. 6; FIG. 7B is a side view of FIG. 6A; FIG. 7C is a front view showing the cone support shaft of FIG.

FIG. 8 is a sectional view when an oil passage is formed in the cone holder of FIG. 6;

9 (a) is a partial front view showing an output shaft having a flange formed thereon, (b) is a partial front view showing an output shaft provided with one annular member, and (c) is provided with two annular members (D) is a partial front view showing an output shaft in which an elastic member is added to a ring member.

10A is a perspective view showing a flange or an annular member in which a contact surface is shaped to generate a dynamic pressure for supporting an axial force, and FIG. 10B is a cross-sectional shape of the contact surface in FIG. Sectional view (c) is a perspective view showing a flange or an annular member having a contact surface having another shape that generates a dynamic pressure for supporting an axial force. (D) shows a sectional shape of the contact surface in (c). Sectional view

FIG. 11 is a side view showing a flange or an annular member having a contact surface having another shape which generates a dynamic pressure for supporting an axial force;

12A is a partial front view showing a cone support shaft having a flange formed thereon, FIG. 12B is a partial front view showing a cone support shaft provided with one annular member, and FIG. Partial front view showing cone support shaft with added members

FIG. 13 is a front view showing a conventional friction type continuously variable transmission.

[Explanation of symbols]

 Reference Signs List 11 input shaft 15 output shaft 19 pressurizing means (pressurizing spring) 23 position regulating part (annular member) 26 transmission ring 27 cone 28, 28 'cone holder 29, 29' holder main body 30, 30 'cone support shaft

Claims (4)

[Claims] 1. An input shaft in which a plurality of cones rotatably held are inscribed, an output shaft in which the plurality of cones are circumscribed, and an elastic pressure contact force is applied between the input / output shaft and the plurality of cones. A friction-type continuously variable transmission that includes a pressurizing means and continuously changes the rotation speed while transmitting rotational power between the input and output shafts via rotation of the cone, wherein each of the cones is a bearing. A friction-type continuously variable transmission, comprising: a cone holder comprising a supported cone support shaft and a holder main body in which the cone support shafts are integrally disposed at equal circumferential intervals. 2. An input shaft in which a plurality of cones rotatably held are inscribed, an output shaft in which the plurality of cones are circumscribed, and an elastic pressure contact force is applied between the input / output shaft and the plurality of cones. A friction-type continuously variable transmission that includes a pressurizing means and continuously changes the rotation speed while transmitting rotational power between the input and output shafts via rotation of the cone, wherein each of the cones is a bearing. A friction type continuously variable transmission, comprising: a cone holder including a cone support shaft that is supported, and a holder body in which the cone support shaft is inserted and fixed at equal circumferential intervals. 3. The friction type continuously variable transmission according to claim 1, wherein the holder main body is supported by a bearing on an input shaft. 4. An input shaft in which a plurality of cones rotatably held are inscribed, an output shaft in which the plurality of cones are circumscribed, and an elastic pressure contact force is applied between the input / output shaft and the plurality of cones. A friction-type continuously variable transmission that includes a pressurizing means and continuously changes the rotation speed while transmitting rotational power between the input and output shafts via rotation of the cones. A friction-type continuously variable transmission, wherein a position restricting portion for restricting directional movement is disposed between the output shaft and each cone or between each cone and the cone holder.