KR100578073B1 - Traction dirve continuously various transmission - Google Patents

Abstract

The present invention relates to a friction transmission continuously variable transmission. The apparatus of the present invention includes a drive rotor (100) having an end surface formed in a circular shape on one side; A driven rotor (200) having an end surface formed in a circular shape on one side; And it is formed of a sphere having an outer surface in contact with the inner surface of the drive rotor and the driven rotor, respectively, and comprises a counter rotor 300 that rotates about the rotation axis while friction transmission is performed through the contact surface. By rotating the rotating shaft at a predetermined interval at the center of the rotating shaft, a pivot point for connecting to an external device is installed to adjust the distance between each contact point and each shaft, thereby adjusting the speed ratio.

Stepless speed change, Durable outer surface contact, Friction transmission, Counter rotor, Drive rotor, Driven rotor

Description

Friction-driven continuously variable transmission {Traction dirve continuously various transmission}

1 is an explanatory diagram showing a basic concept of a conventional toroidal CVT.

2 is an explanatory diagram showing an analysis relationship of a force of a contact portion;

3 is an explanatory diagram showing an inner surface-outer surface contact state;

4 is a schematic diagram of a first embodiment of the present invention;

5 is a schematic view of a second embodiment of the present invention.

6 is a schematic diagram of a third embodiment of the present invention.

7 is a schematic diagram of a fourth embodiment of the present invention.

Figure 8 is an exemplary perspective view showing a configuration example applying one embodiment of the present invention.

9 is a schematic diagram of a fifth embodiment of the present invention.

10 is a schematic diagram of a sixth embodiment of the present invention.

11 is a schematic diagram of a seventh embodiment of the present invention.

12 is a schematic diagram of an eighth embodiment of the present invention.

Explanation of symbols on the main parts of the drawings

100, 100a, 100b, 100c ..... Drive rotor

200, 200a, 200b, 200c ..... driven rotor

300, 300a, 300b, 300c ..... Counter Rotor

310, 310a, 310b, 310c ..... axis of rotation

320, 320a, 320b, 320c ..... pivot point

The present invention relates to a friction-driven continuously variable transmission, and more particularly, a friction-driven continuously variable transmission in which a drive rotor, a driven rotor, and a counter rotor make contact with an outer surface-inner surface, so that power transmission can be most efficiently performed. It is about.

In general, the continuously variable transmission using friction is known to have excellent advantages such as speed control and relatively simple structure, such as driving performance and ride comfort. However, due to the constraints in terms of power transmission capacity, there was a problem that it is difficult to put to practical use. Therefore, in recent years, various researches and developments have been made to expand the power transmission capacity of the continuously variable transmission, and some of them have been commercialized.

The continuously variable speed transmission apparatus using such friction includes a belt pulley (various pulley-belt type) and a traction drive type (rotor).

In the currently commercially available variable pulley-belt type continuously variable transmission, the one side of the pulley is configured to be movable to change the rotation radius of the belt by changing the pulley, and thus the speed is continuously changed. Such a variable pulley-belt type has the advantages of simple structure and easy position adjustment of the pulley. Recently, it has been commercialized as a transmission of a small passenger car.

However, such a variable pulley-belt type transmission has a disadvantage in that the speed range is narrow and the belt is specially manufactured, and the range of power transmission is greatly limited.

Toroidal CVT is one of the continuously variable transmissions of friction transmission. The toroidal CVT is a CVT formed by contact between a toroidal furface and an outer spherical surface. The toroidal CVT has a relatively wide shift range and a considerable power transmission compared to the CVT of the variable pulley-belt type. Therefore, it is used in the medium passenger car.

1 shows a basic structure of a conventional toroidal friction transmission continuously variable transmission. The toroidal continuously variable transmission includes a drive rotor 10 and a driven rotor 20, and a plurality of counter rotors 12 and 14 relaying between the drive rotor and the driven rotor.

The rotational force of the drive rotor 12 that rotates by power from a power source causes the counter rotors 12 and 14 to rotate by friction transmission. In addition, the rotational force of the counter rotors 12 and 14 equally rotates the driven rotor 18 by friction transfer. At this time, the speed ratio is determined by the distance between the respective contact points and the shaft.

The relationship between the input and the force of the contact portion of the driven rotor and the counter rotor as shown above is shown in FIG. As shown in the drawing, the counter rotor 12 and the rotor 10 forming a contact portion are in contact with each other via a traction oil 3. At this time, the frictional force is defined by the vertical force acting in the direction perpendicular to the contact portion, and can be thought of as the static frictional force, that is, the tangential force, generated at the tangent of the counter rotor 12 against the driving torque of the rotor 10. have.

When the tangential force is greater than the drive torque, the counter rotor 12 transmits power while performing the movement by rolling contact with respect to the rotor 10, and when the tangential force is smaller than the drive torque, a sliding motion occurs.

According to Hertz's contact theory, the contact stress is proportional to one-third of the normal force and two-thirds the sum of the inverses of the radius of curvature of the contacting parts (K value). Here, the K value is 1 / (first direction radius of curvature of object 1) + 1 / (second direction radius of curvature of object 1) + 1 / (first direction radius of curvature of object 2) + 1 / of object 2 Second direction radius of curvature). Here, the radius of curvature of an object is defined as negative (-) when the curve is concave and positive (+) when the curve is convex.

In the above-described toroidal CVT, the shape curved surface at the contact portion of two objects (for example, the rotor and the counter rotor) can be said to be a contact between an outer spherical surface and a toroidal surface. One of the two curvature radii of the toroidal surface is positive and the other is negative. Both radiuses of curvature of the outer surface in contact with the toroidal plane are positive. Therefore, it can be seen that the outer surface and the toroidal surface are convex-convex contact with each other in one main axis direction, and the outer surface and the toroidal surface are convex-concave contact with each other in the other main axis direction. The latter contact has the effect of reducing the above-described K value. Therefore, the toroidal CVT is an advantageous mechanism in terms of stress relaxation than the outer-surface contact and outer-plane contact methods. . However, in the toroidal CVT, since there is always a convex-convex contact, there is a certain limit in reducing the K value.

If a CVT is devised that can use endurance contact, the K value can be significantly reduced. That is, as shown in FIG. 3, in the case of the mechanism in which the rotor 10 and the counter rotor 12 make an inner surface-outer surface contact, both radiuses of curvature of the inner surface are negative, Both radii of curvature are positive. Therefore, both main axis directions are concave-convex contact, which has the effect of reducing the K value. In this contact relationship, the smaller the difference in the radius of curvature of the two objects, the greater the K value reduction effect. However, because the power loss of the friction part increases due to the spin motion between the two objects, the difference cannot be made infinitely small.

Another feature of the inner-surface-surface contact is that the contact surface is formed in a nearly circular shape due to the elastic deformation of the contact portion. Therefore, as in the toroidal CVT, the spin loss is smaller than the elliptical contact area.

In order to solve the above disadvantages of spherical contact, Milner CVT has been proposed as PCT / GB02 / 04065. However, in this Milner CVT, either one of the two contacts of the driving part and the follower is in contact with the inner surface-outer surface, but the other is composed of the outer surface-toroidal surface contact such as the toroidal CVT, so that only one side Since this inner surface to outer surface contact is used, there is a certain limit as described above.

In summary, prior art as described above, the toroidal CVT is in contact with two outer surface-toroidal surface, and Milner CVT is in contact with the outer surface-toroidal surface and the inner surface-outer surface contact. Therefore, Milner CVT is more effective than toroidal CVT in terms of stress relaxation effect. In addition, in terms of spin energy loss, Milner CVT is more effective than toroidal CVT because it is more advantageous than the toroidal toroidal contact.

However, none of the above-mentioned continuously variable transmissions have achieved complete inner-surface contact, and in view of stress relaxation and spin loss, power transmission by inner-surface contact is most preferable.

As mentioned above, the most preferable thing in the contact system of a concrete rotor can be said to be the inner surface-outer surface contact system shown in FIG. Since the contact method is a form in which both contact intervals gradually widen from the center contact portion to the outside, the actual contact area can be said to be wide, and the flow of lubricant between the contact portions can be relatively stabilized, and the stress Great effect of relaxation

SUMMARY OF THE INVENTION An object of the present invention is to provide a triboelectric continuously variable transmission configured to achieve a reliable transmission while having a simple structure.

Another object of the present invention is to provide a friction-driven continuously variable transmission that can effectively achieve stress relaxation and spin loss reduction and at the same time have a stable and high efficiency in power efficiency over a full speed fluctuation range.

Friction transmission continuously variable apparatus according to the present invention for achieving the above object, the drive rotor having an endurance formed in a circular shape on one side; A driven rotor having an endurance surface formed in a circular shape on one side; And a counter rotor formed of a sphere having an outer surface in contact with the inner surfaces of the driving rotor and the driven rotor, respectively, and rotating about a rotating shaft while friction transmission is performed through the contact surface. At the center of the rotating shaft by rotating the rotating shaft at a predetermined interval, it is characterized in that the pivot point for connection with the external device is installed, so that the distance between each contact point and each axis can be adjusted.

According to the embodiment, the driving rotor and the driven rotor are arranged such that the counter rotor is interposed between the inner surface of the driving rotor and the inner surface of the driven rotor. In this case, the rotation shaft may be disposed between the contact points of the driving rotor and the driven rotor and the counter rotor, or may not be disposed between the contact points.

According to another embodiment, the driving rotor and the driven rotor are arranged in the same direction, the inner surface of the drive rotor has a larger diameter than the inner surface of the driven rotor, each of the inner surface is in contact with the counter rotor in the same quadrant It is configured to.

Each of the rotational shafts of the driving rotor and the driven rotor may be coaxial with each other, or may be positioned at a predetermined interval. In addition, the respective rotation shafts of the driving rotor and the driven rotor may have a constant angle, such as forming a right angle.

According to the present invention as described above, when the driving rotor and the driven rotor in contact with the counter rotor, it makes the inner surface-outer surface contact. Therefore, the effect of stress relaxation during power transmission is great, and the range of power transmission will be expected to be wider.

Next, the present invention will be described in more detail with reference to the embodiments shown in the drawings.

4 to 7 are cross-sectional views according to the first to fourth embodiments showing the basic principle of the present invention, Figure 8 is a substantially applied one using the basic principle of the transmission apparatus according to the present invention An exemplary perspective view showing a configuration example of the.

First, a first embodiment of the present invention shown in FIG. 4 will be described. As shown, the continuously variable transmission according to the present invention includes a drive rotor 100 that rotates with power at a drive source, a driven rotor 200 that provides rotational output at a predetermined speed ratio, and the drive rotor and driven rotor. It is comprised including the counter-rotor 300 of the sphere which friction-drives between.

The drive rotor 100 is a part that rotates by the rotational power of the drive source, and has an inner spherical surface 110 on a circumference at least on one side, and has a disc shape as in the illustrated embodiment. Can be formed. The driven rotor 200 is output with a predetermined speed ratio with respect to the rotational speed of the drive rotor 100, and the endurance surface 210 is formed on a surface of the drive rotor 100 facing the end surface 110. It is shape | molded in the disk shape provided with a column shape.

And the counter rotor 300 is formed in a sphere, the contact portion 330 in contact with the inner surface 110 of the drive rotor 100 and the contact in contact with the inner surface 210 of the driven rotor 200 The portions 340 all become outer spherical surfaces.

Therefore, the contact portion during friction transmission in accordance with the present invention, the inner surface 110 of the drive rotor 100 and the outer surface contact portion 330 of the counter rotor 300, and the inner surface 210 of the driven rotor 200 And the outer circumferential contact portion 340 of the counter rotor 300 are both the inner and outer circumferential contact as shown in FIG. 3. Therefore, according to the friction transmission according to the present invention, the contact area becomes substantially wider, the stress relaxation can be achieved by the wide contact area, and the reduction of the spin loss will be effectively achieved.

In addition, the counter rotor 300 performs frictional transmission between the driving rotor 100 and the driven rotor 200 to provide an appropriate reduction ratio. In this embodiment, the counter rotor 300 is rotated about the rotating shaft 310 is installed in the horizontal direction (that is, in the axial direction of the drive rotor and the driven rotor) in the drawing, the drive rotor 100 And frictional transmission with the driven rotor (200).

The rotary shaft 310 is supported by another structure, the pivot point 320 is connected to the center thereof. The pivot point 320 is configured to rotate the rotary shaft 310 (clockwise or counterclockwise), and is connected to an external mechanism so as to rotate the rotary shaft 310.

When the rotating shaft 310 is rotated about the pivot point 320, the contact points of the driving rotor 100, the counter rotor 300, and the counter rotor 300 and the driven rotor 20 are substantially respectively. And the distance between each axis will change. Therefore, by rotating the rotary shaft 310 about the pivot point 320, it is possible to substantially adjust the speed ratio. Thus, for example, in the state illustrated in FIG. 1, when the rotation shaft 310 is rotated at a predetermined angle clockwise about the pivot point 320, the output becomes substantially higher. On the contrary, if the counterclockwise rotation is performed at an angle, the output will be substantially slow.

In the present invention, as described above, it is a basic technical idea to configure the counter rotor, the driving rotor, and the driven rotor to perform both inner and outer surface contact in friction transfer using the concrete counter rotor. .

In the first embodiment as described above, the drive rotor 100 and the driven rotor 200 are provided in a direction facing each other. And the rotation shaft 310 of the counter rotor 300 is installed so as not to be located between the contact point of the drive rotor 100 and the counter rotor 300 and the driven rotor 200 and the counter rotor 300. Able to know.

Next, a second embodiment of the present invention shown in FIG. 5 will be described. As shown, the friction transmission continuously variable transmission of this embodiment includes a drive rotor 100a that rotates with power from a drive source, a driven rotor 200a that provides rotational output at a predetermined speed ratio, and driven with the drive rotor. It is comprised including the spherical counter rotor 300a which friction-transfers between rotors. Each such component itself is substantially the same as the first embodiment described above.

Also in this embodiment, each contact between the drive rotor 100a and the counter rotor 300a, and the counter rotor 300a and the driven rotor 200a is frictional while making the inner-surface-surface contact as described above. It is comprised so that transmission may take place.

In this embodiment, the rotary shaft 310a of the counter rotor 300a is perpendicular to the drawing, and the rotary shaft 310a has respective contact points (contact points of the drive rotor and the counter rotor and contact points of the counter rotor and the driven rotor). You can see that it is located in between. In the present embodiment, the rotation shaft 310a may be rotated by the pivot point 320a connected to the external device, and the transmission ratio may be determined as described above by the rotation of the pivot point centeraround of the rotation shaft 310a. will be.

In the above-described first and second embodiments, it can be seen that only the positions of the rotating shafts of the counter rotor described above are set differently. As a result of performing the analysis and simulation of the motion components of each component with respect to the first and second embodiments, it can be seen that the first embodiment has a relatively small spin loss and thus enables efficient shifting. Could.

Next, a third embodiment shown in FIG. 6 will be described. The first and second embodiments described above are embodiments in which the driving rotor and the driven rotor are arranged so as to face each other. However, the third embodiment and the fourth embodiment described below are embodiments in which the driving rotor and the driven rotor are arranged on the same side.

First, in the embodiment shown in FIG. 3, an end surface 110b is formed on one side of the driving rotor 100b, and an end surface 210b is formed on one side of the driven rotor 200b. In this embodiment, the driving rotor 100b and the driven rotor 200b are disposed in the same direction. In the illustrated embodiment, the diameter of the drive rotor 100b has a diameter larger than that of the driven rotor 200b, so that the driven rotor is disposed inside the drive rotor on the same side.

And it can be seen that each of the contact points of the counter rotor (300b) in contact with the inner surface (110b) of the drive rotor and the inner surface (210b) of the driven rotor are all located in the same first quadrant in the drawing. That is, since the drive rotor 100b and the driven rotor 200b are provided in the same direction, the contact points with the counter rotors are equally positioned in the first quadrant.

Also in this embodiment, it is natural that the counter rotor 300b causes frictional movement while rotating about the rotation shaft 310b. In addition, a pivot point 320b connected to an external device is connected to the center of the rotation shaft 310b, so that the rotation shaft 310b is rotatable about the pivot point 320b. Also in this embodiment, when the rotating shaft 310b is rotated, each contact point and the distance between the shaft is changed, the transmission ratio will be determined by this relationship.

In this embodiment, the rotary shaft 310b is designed to be located between the contact point of the drive rotor 100b and the counter rotor 300b and the contact point of the counter rotor 300b and the driven rotor 200b.

Next, a fourth embodiment of the present invention shown in FIG. 7 will be described. In this embodiment, the positional relationship between the drive rotor 100c, the driven rotor 200c, and the counter rotor 300c is the same as in the third embodiment. In this embodiment, the position and the contact form of each of the contact points of the drive rotor, the driven rotor, and the counter rotor are the same as in the above-described third embodiment.

In this embodiment, the rotation shaft 310c of the counter rotor 300c is not located between the contact point of the drive rotor 100c and the counter rotor 300c and the contact point of the counter rotor 300c and the driven rotor 200c. It is designed.

And also in this embodiment, by rotating the rotation axis 310c of the counter rotor 300c about the pivot point 320c, the distance between each contact point and the axis is changed to be able to adjust the speed ratio substantially It is natural.

The third embodiment and the fourth embodiment, it can be seen that the embodiment is distinguished by the positional relationship between the respective contact points of the drive rotor, the driven rotor and the counter rotor, and the rotary shaft. When the rotary shaft 310b is positioned between the pair of contact points as in the third embodiment, the driving direction of the drive rotor and the output direction of the driven rotor become different directions, and as shown in the fourth embodiment, the rotary shaft is paired. If not located between the contact points of, the driving direction and the output direction will be the same direction.

8 is a configuration example in which the second embodiment is implemented. For convenience of explanation, the same reference numerals are given to the components of the second embodiment shown in FIG. In the present embodiment, it can be seen that the counter rotor 300a is configured in plural, and the stepless speed change is caused by frictional transmission by the outer surface-inner surface contact between the counter rotor 300a and the driving and driven rotor. It is easy to understand that it is possible.

Next, a fifth embodiment to an eighth embodiment of the present invention will be described. The first to fourth embodiments as described above are embodiments in which the shafts of the driving rotor and the driven rotor are coaxial. The embodiment described below is an embodiment in which the axes of the driving rotor and the driven rotor are not coaxial.

First, a fifth embodiment of the present invention shown in FIG. 9 will be described. The present embodiment is an embodiment to which the present invention is applied in a state where the rotation axis of the driving rotor 100d and the rotation axis of the driven rotor 200d are parallel and spaced apart at regular intervals. As shown in the drawing, an endurance surface 110d is formed in the driving rotor 100d, and an endurance surface 210d is formed in the driven rotor 200d. The counter rotor 300d interposed between the driving rotor 100d and the driven rotor 200d has an outer peripheral surface contacting the respective inner surfaces 110d and 210d.

The driven rotor 300d rotates about the rotation shaft 310d, and a pivot point 320d is installed at an intermediate portion of the rotation shaft 310d so as to rotate the rotation shaft and connected to an external device. Also in this embodiment, the speed ratio will be determined according to each contact point and the axis distance as described above, and the actual speed ratio can be varied by rotating the rotary shaft 310d.

10, a sixth embodiment of the present invention is shown. As shown, this embodiment is also an embodiment in which the respective rotation axes of the drive rotor 100e and the driven rotor 200e are parallel but spaced apart by a predetermined interval, and the present embodiment is more effective than the fifth embodiment. It can be seen that the rotary shaft and the rotary shaft of the driven rotor are more spaced apart. In this embodiment, since the distance between each rotation shaft of the drive rotor and the driven rotor is large, the contact portion of the drive rotor (100e) in contact with the counter rotor (300e) is substantially different from the fifth embodiment.

Also in this embodiment, the inner surface 110e of the drive rotor 100e and the inner surface 210e of the driven rotor 200e are in contact with the outer surface of the counter rotor 300e. The same as in the fifth embodiment. The counter rotor 300e is rotated based on the rotation shaft 310e, and a pivot point 320e for rotating the rotation shaft 310e by an external device is installed at the center of the rotation shaft 310e.

Also in the fifth and sixth embodiments, the rotary shafts 310d and 310e may include the contact points between the drive rotors 100d and 100e and the counter rotors 300d and 300e, the counter rotors 300d and 300e, and the driven rotors. It may be designed to be located between the contact points of (200d, 200e), or not located between the same as the above-described embodiment. In addition, the contact points and the distance between the shafts are changed by the rotation of the rotary shaft, and accordingly, the speed ratio can be adjusted.

Next, the seventh and eighth embodiments of the present invention shown in FIGS. 11 and 12 will be described.

The seventh and eighth embodiments of the present invention are applied to the rotation axis of the drive rotor and the rotation axis of the driven rotor being perpendicular to each other.

In the embodiment shown in Fig. 11, the axis of rotation of the drive rotor 100f is perpendicular to the drawing, and the axis of rotation of the driven rotor 200f is horizontal, so that the input shaft and the output shaft are substantially perpendicular to each other. It can be seen that.

In this embodiment, it can be seen that the ball rotor 300f is interposed between the driving rotor 100f and the driven rotor 200f and is designed to enable friction transmission. The drive rotor 100f and the driven rotor 200f are respectively provided with endurance surfaces 110f and 210f in contact with the counter rotor, respectively. It is obvious that the counter rotor 300f of the sphere has an outer surface which contacts the respective inner surfaces 110f and 210f.

The counter rotor 300f is rotatably supported by the rotation shaft 310f, and has a pivot point 320f connected to the center of the rotation shaft 310f so as to rotate the rotation shaft.

In addition, as in the eighth embodiment shown in FIG. 12, it can be seen that the rotation shafts of the driving rotor 100g and the driven rotor 200g form a right angle with each other. In this embodiment, the driving rotor (100g) and the driven rotor (200g) is in contact with the outer surface of the concrete counter rotor (300g) in the inner surface (110g, 210g), respectively, perform friction transfer. The present embodiment is configured substantially similarly to the seventh embodiment, and only the contact positions of the drive rotor 100g and the counter rotor 300g are different.

In this embodiment, the counter rotor (300g) is rotatably supported by a rotation shaft (310), the center of the rotation shaft (310g) is connected to an external device to adjust the speed ratio by rotating the rotation shaft It has a pivot point (320g).

Also in the seventh and eighth embodiments as described above, the gear ratio is determined by the relationship between the respective contact points and the shaft distance, and the rotary shaft 310f is connected by an external device connected by the pivot points 320f and 320g. When 310g) is rotated, the speed ratio is adjusted while the distance between the contact point and the shaft is changed.

The fifth to eighth embodiments may be applied to a case in which the driving rotor and the driven rotor are not coaxial, that is, when the driving rotor and the driven rotor are spaced at regular intervals or are perpendicular to each other. As described above, the present invention can be applied not only when the rotation shafts of the driving rotor and the driven rotor are coaxial, but also when the rotation shafts are spaced apart at regular intervals while being in parallel with each other, and can be applied even when they have a constant angle to each other. It can be seen.

As described above, according to the present invention, a continuously variable transmission by friction transmission using a concrete counter rotor is implemented, and friction transmission by inner-surface-surface contact between the counter rotor, the driving rotor, and the driven rotor is performed. It can be seen that the configuration is made to be a basic technical idea.

Within the scope of the basic technical spirit of the present invention, many other modifications are possible to those skilled in the art, as well as the present invention should be interpreted based on the appended claims.

According to the present invention as described above, it can be seen that the stepless speed change is made by friction transmission using a spherical counter rotor. In the present invention, it can be seen that each contact portion of the driving rotor and the driven rotor in contact with the counter rotor performs the inner surface-outer surface contact. Therefore, it is expected that the effect of relaxation of stress is large due to the contact area provided between the two, and the range of power transmission can be increased relatively compared with the conventional one.

Claims (11)

A driving rotor having an end surface formed in a circular shape on one side thereof; A driven rotor having an endurance surface formed in a circular shape on one side; And It is formed of a sphere having an outer surface in contact with the inner surface of the drive rotor and the driven rotor, respectively, and comprises a counter rotor that rotates about a rotating shaft while friction transmission is performed through the contact surface;  The driving rotor and the driven rotor are disposed in the same direction, the inner surface of the driving rotor has a larger diameter than the inner surface of the driven rotor, each of the inner surface in contact with the counter rotor in the same quadrant; And a contact point and a distance between the shafts can be adjusted by rotating the rotation shafts at regular intervals in the center of the rotation shafts. delete delete delete delete The continuously variable friction drive according to claim 1, wherein the rotating shaft is disposed between each contact point of the driving rotor and the driven rotor and the counter rotor. The continuously variable friction drive according to claim 1, wherein the rotating shaft is disposed so as not to be positioned between each contact point of the driving rotor and the driven rotor and the counter rotor. 2. The frictionless continuously variable transmission as claimed in claim 1, wherein the rotating shaft of the drive rotor and the driven rotor is coaxial. According to claim 1, wherein the rotational axis of the drive rotor and the driven rotor is parallel, friction-driven continuously variable device, characterized in that spaced apart at regular intervals. According to claim 1, wherein the rotational axis of the drive rotor and the driven rotor is a friction-driven continuously variable transmission, characterized in that at an angle to each other. According to claim 1, wherein the rotational axis of the drive rotor and the driven rotor is a friction-driven continuously variable transmission, characterized in that perpendicular to each other.

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