JP6784905B2 - Continuously variable transmission - Google Patents

Description

The present invention relates to a continuously variable transmission used as a power transmission means.

As a power transmission means from the drive shaft to the output shaft, a continuously variable transmission capable of continuously changing the gear ratio has been proposed. There are belt type, chain type and toroidal type continuously variable transmissions of this type. For example, Patent Document 1 discloses a toroidal continuously variable transmission.

JP-A-2010-32033

Toroidal continuously variable transmissions have been adopted in electric vehicles and hybrid vehicles in recent years, but their structures are complicated and maintainability is not sufficient.

An object of the present invention is to provide a continuously variable transmission having a novel and simple structure.

The continuously variable transmission according to the present invention
1st axis and
A second axis that is parallel to the first axis and eccentric to the first axis,
The first disk connected to the first axis and
A second disk that is at least partially opposed to the first disk and is connected to the second axis.
A first spherical rolling element arranged between the first disc and the second disc and in contact with the first disc,
A second spherical rolling element, which is arranged between the first disk and the second disk, is in contact with the second disk and is connected to the first spherical rolling element so as to be able to transmit power.
The first spherical rolling element and the second spherical rolling element are rotatably and power-transmittedly connected, the first spherical rolling element is brought into contact with the first disk, and the second spherical rolling element is brought into contact with the second disk. With a holder that holds it in contact with
A holder moving means for moving the holder in a plane parallel to the first axis and the second axis in a region facing the first disk and the second disk.
To have.

The first spherical rolling element and the second spherical rolling element can be spherical.

The first spherical rolling element may have at least a spherical shape at a portion in contact with the first disc and the second spherical rolling element.

The first spherical rolling element and the second spherical rolling element are in contact with each other.

One or a plurality of spherical rolling elements are arranged between the first spherical rolling element and the second spherical rolling element.

The first disc and the second disc have a disk shape.

At least one of the first disk and the second disk has a diameter equal to or larger than the eccentric distance between the first axis and the second axis.

The first disc and the second disc each have a first engaging portion and a second engaging portion formed of a plurality of concave and / or convex portions on opposite surfaces thereof, and the first spherical rolling element has a plurality of concave and / or convex portions. A first meshing portion that meshes with the first engaging portion is formed on the surface, and a second meshing portion that meshes with the second engaging portion is formed on the surface of the second spherical rolling element.

In the first spherical rolling element and the second spherical rolling element, the first meshing portion and the second meshing portion mesh with each other.

The first disc and the first spherical rolling element, and the second disc and the second spherical rolling element are in frictional contact with each other.

The first spherical rolling element and the second spherical rolling element are in frictional contact with each other.

According to the continuously variable transmission of the present invention, the gear ratio of the power transmitted from the first axis to the second axis can be freely changed only by adjusting the contact position of the spherical rolling element with the disk.

Further, since the continuously variable transmission of the present invention can be configured by a disc, a spherical rolling element, a holder for holding the spherical rolling element, and a holder moving means, the configuration is simpler than that of the conventional continuously variable transmission. .. Further, the continuously variable transmission of the present invention can greatly change the gear ratio from 0 to infinity. Furthermore, it is also excellent in maintainability.

FIG. 1 is a perspective view showing a schematic configuration of a continuously variable transmission according to a first embodiment of the present invention. FIG. 2 is a side view of the continuously variable transmission according to the first embodiment of the present invention. FIG. 3 is a cross-sectional view of the continuously variable transmission viewed from the first axis side, which is a cross section taken along the arrow AA of FIG. FIG. 4 is an explanatory diagram when the gear ratio of the second axis to the first axis is large and the rotation directions of the first axis and the second axis are opposite to each other. FIG. 5 is an explanatory diagram when the gear ratio of the second axis to the first axis is small and the rotation directions of the first axis and the second axis are opposite to each other. FIG. 6 is an explanatory diagram showing a neutral state in which the first axis and the first spherical rolling element are arranged side by side. FIG. 7 is an explanatory diagram showing a neutral state (or locked state) in which the second axis and the second spherical rolling element are arranged side by side. FIG. 8 is an explanatory diagram when the gear ratio of the second axis to the first axis is small and the rotation directions of the first axis and the second axis are the same. FIG. 9 is an explanatory diagram when the gear ratio of the second axis to the first axis is large and the rotation directions of the first axis and the second axis are the same. FIG. 10 is a cross-sectional view of the continuously variable transmission according to the second embodiment of the present invention. FIG. 11 is a cross-sectional view taken along the line BB of FIG. FIG. 12 is an enlarged cross-sectional view showing different embodiments of the first engaging portion and the first engaging portion. FIG. 13 is an enlarged cross-sectional view showing different embodiments of the first engaging portion and the first engaging portion. FIG. 14 is a plan view showing a third embodiment in which the first spherical rolling element and the second spherical rolling element are spherical only on the contact surface. FIG. 15 is a cross-sectional view taken along the line AA of the third embodiment. FIG. 16 is a plan view showing a state in which the holder is pulled back from the state of FIG. FIG. 17 is a plan view showing a state in which the holder is further pulled back from the state of FIG. FIG. 18 is a plan view showing a state in which the holder is extruded from the state of FIG.

The continuously variable transmission 10 of the present invention can be used as a transmission for vehicles such as automobiles, trucks and buses, industrial machines and industrial machines. Hereinafter, the continuously variable transmission 10 of the present invention will be described with reference to the drawings.

<First Embodiment>
FIG. 1 is a perspective view showing a schematic configuration of a continuously variable transmission 10 according to a first embodiment of the present invention, FIG. 2 is a side view, and FIG. 3 is a front view seen from the first axis 20 side. As shown in the figure, in the continuously variable transmission 10, the first shaft 20 connected to the drive source 12 and the second shaft 30 on the output side are arranged in parallel and eccentrically. A motor or an engine can be exemplified as the drive source 12. Further, the second shaft 30 is an output shaft, and the output can be used directly for rotating tires, driving various mechanisms, tools, etc., or via an accelerator / reducer or the like.

The first shaft 20 is rotatably supported by a bearing or the like, and the first disc 21 is connected to the tip thereof. In the illustrated embodiment, the first disk 21 is a disk body in which the first facing surface 22 facing the second axis 30 is perpendicular to the first axis 20. As shown in FIG. 8 to be described later, when the rotation directions of the first axis 20 and the second axis 30 can be switched, the diameter of the first disk 21 is the eccentric distance between the first axis 20 and the second axis 30. That is all.

The second shaft 30 is rotatably supported by a bearing or the like, and the second disc 31 is connected to the tip thereof. In the illustrated embodiment, the second disc 31 is also a disk body, the second facing surface 32 facing the first axis 20 is perpendicular to the second axis 30, and further, the second facing surface 32. Is at least partially opposed to the first facing surface 22. Desirably, the second facing surface 32 faces parallel to the first facing surface 22. As shown in FIG. 9 described later, when the rotation directions of the first axis 20 and the second axis 30 can be switched in this facing region, the diameter of the second disk 31 is the first axis 20 and the second axis 20. The eccentric distance of the shaft 30 or more.

A plurality of spherical rolling elements 40, 50 that connect the first disk 21 and the second disk 31 so as to be able to transmit power are arranged between the first disk 21 and the second disk 31. In the illustrated embodiment, there are two spherical rolling elements 40 and 50, the spherical rolling element 40 on the first disk 21 side is the first spherical rolling element, and the spherical rolling element 50 on the second disk 31 side is the second spherical rolling element. Called a moving body.

The first spherical rolling element 40 and the second spherical rolling element 50 are spherical bodies in the present embodiment. The first spherical rolling element 40 is in contact with the first facing surface 22, and the second spherical rolling element 50 is in contact with the second facing surface 32. Further, the first spherical rolling element 40 and the second spherical rolling element 50 are also in contact with each other. Then, in the present embodiment, the first spherical rolling element 40 and the second spherical rolling element 50 have diameters (referred to as diameter lines L) arranged in a straight line, and the diameter lines L are the first axis 20 and the second axis. It is held in the holder 60 so as to be parallel to 30 (holder 60 is not shown in FIG. 1). The diameter line L is preferably parallel to the first axis 20 and the second axis 30, but may be non-parallel to these, and the first spherical rolling element 40 and the second spherical rolling element 40. The moving body 50 may be offset in diameter instead of being aligned in a straight line.

The holder 60 rotatably holds the first spherical rolling element 40 and the second spherical rolling element 50. More specifically, the illustrated holder 60 has bearings 61 such as thrust bearings arranged on the inner surfaces of the opposing plate-shaped pedestals. The pedestals are held so that the distance between them is constant. Then, the first spherical rolling element 40 protrudes from one end of the holder 60 toward the first facing surface 22, and the second spherical rolling element 50 protrudes from the other end toward the second facing surface 32.

The holder 60, together with the first spherical rolling element 40 and the second spherical rolling element 50, is located between the first disk 21 and the second disk 31 in a plane parallel to the first axis 20 and the second axis 30. Is connected to the holder moving means 64 so as to be movable in the opposite region of the second disc 31. The moving direction of the holder 60 is indicated by an arrow 6A in FIGS. 2 and 3. The holder moving means 64 can exemplify an actuator-65 such as a cylinder, and in this case, the piston rod 66 can be connected to the holder 60.

The first facing surface 22 and the first spherical rolling element 40 of the first disc 21, the first spherical rolling element 40 and the second spherical rolling element 50, and the second spherical rolling element 50 and the second facing surface of the second disc 31. 32 are in frictional contact with each other. For example, the facing surfaces 22, 32 and the spherical rolling elements 40, 50 are preferably made of a metal such as steel, hard rubber, hard resin, or the like. In order to improve the efficiency of the continuously variable transmission 10, it is desired to reduce the slippage between the facing surfaces 22 and 32 and the spherical rolling elements 40 and 50.

The operating principle of the continuously variable transmission 10 described above will be described with reference to FIGS. 1 to 3. When the drive source 12 is operated and the first shaft 20 rotates in the direction of arrow 2A in the drawing, the first disc 21 also rotates together with the first shaft 20. Since the first spherical rolling element 40 is in frictional contact with the first facing surface 22 and is held by the holder 60, the first spherical rolling element 40 rolls in the direction of arrow 4A in the drawing by the rotation of the first disc 21. The second spherical rolling element 50, which is in frictional contact with the first spherical rolling element 40, rolls in the direction of arrow 5A in the figure due to the rolling of the first spherical rolling element 40.

Since the second facing surface 32 is in frictional contact with the second spherical rolling element 50, the second disc 31 is rotated in the arrow 3A direction in the drawing by the rolling of the second spherical rolling element 50 in the arrow 5A direction. Then, the second axis 30 rotates in the opposite direction to the first axis 20.

Here, when the holder moving means 64 is operated, the gear ratio of the first shaft 20 and the second shaft 30 can be changed. When the diameters of the first spherical rolling element 40 and the second spherical rolling element 50 are the same, the gear ratio is the distance S1 from the first axis 20 to the diameter line L shown in FIG. 2 and the diameter line from the second axis 30. It can be expressed by the value (S1 / S2) divided by the distance S2 to L. The larger the gear ratio, the higher the rotation speed of the second shaft 30 with respect to the first shaft 20, but the torque of the second shaft 30 becomes smaller, and the smaller the gear ratio, the larger the rotation speed of the second shaft 30 with respect to the first axis. The number is small, but the torque of the second shaft 30 is large.

Regarding the gear ratio, in FIG. 2, the distance S1 from the first axis 20 to the diameter line L and the distance S2 from the second axis 30 to the diameter line L are set to 1: 1. Therefore, the gear ratio (S1 / S2) of the first shaft 20 and the second shaft 30 is 1.

On the other hand, when the holder moving means 64 is shortened and the distance S1 from the first axis 20 to the diameter line L is made larger than the distance S2 from the second axis 30 to the diameter line L, as shown in FIG. (S1 / S2) is larger than 1.

On the contrary, when the holder moving means 64 is extended and the distance S1 from the first axis 20 to the diameter line L is smaller than the distance S2 from the second axis 30 to the diameter line L, as shown in FIG. The ratio (S1 / S2) is less than 1.

As described above, according to the continuously variable transmission 10 of the present invention, the position of the first spherical rolling element 40 and the second spherical rolling element 50 is set between the first axis 20 and the second axis 30 by the holder moving means 64. By moving with, the rotation of the first shaft 20 can be transmitted to the second shaft 30 at a desired gear ratio.

As shown in FIG. 6, the first spherical rolling element 40 and the second spherical rolling element 50 are formed by expanding and contracting the holder moving means 64 so that the rotation center of the first axis 20 and the diameter line L coincide with each other. As shown by arrows 4B and 5B in the figure, they rotate in a plane orthogonal to the first axis 20 and the second axis 30. As a result, the rotation of the first shaft 20 is in a neutral state that is not transmitted to the second shaft 30.

Further, as shown in FIG. 7, by expanding and contracting the holder moving means 64 so that the rotation center of the second axis 30 and the diameter line L coincide with each other, the first spherical rolling element 40 and the second spherical rolling element 50 can be moved. Although it rotates along the arrows 4A and 5A in the figure, since the diameter line L coincides with the second axis 30, the rotation is not transmitted from the second spherical rolling element 50 to the second axis 30, and the rotation of the first axis 20 is , It becomes a neutral state that is not transmitted to the second shaft 30. At this time, if slip does not occur between the first disk 21, the first spherical rolling element 40, the second spherical rolling element 50, and the second disk 31, the second spherical rolling element 50 rotates in the direction of arrow 5A. The first spherical rolling element 40 also stands still without rotating in the direction of arrow 4A. Since the first disk 21 and the first axis 20 are also prevented from rotating in the direction of the arrow 2A, the drive source 12 can be locked.

As shown in FIGS. 6 and 7, in the neutral state, the power transmission from the first shaft 20 to the second shaft 30 is cut off, but the first spherical rolling element 40 or the second spherical rolling element 50 , The first disk 21 or the second disk 31 is driven to rotate. As a result, the first spherical rolling element 40 and the second spherical rolling element 50 may be worn due to frictional contact.

Therefore, in order to bring the ball into the neutral state in the above case, as shown in FIGS. 6 and 7, the spherical rolling elements 40 and 50 can be freely rolled around the rotation centers of the first disc 21 and the second disc 31. A configuration in which idling means 29 and 39 such as bearings are provided can be exemplified. In this case, when the first spherical rolling element 40 moves on the idling means 29 of the first disc 21, the rotation of the first disk 21 is not transmitted to the first spherical rolling element 40, and the second spherical rolling element is not transmitted. When the 50 moves onto the idling means 39 of the second disc 31, the neutral state (or stopped state) in which the rotation of the second spherical rolling element 50 is not transmitted to the second disc 31 can be realized.

The idling means 39 can be idled in the state of FIG. 7 by configuring the idling means 39 to rotate around the second axis 30 only in the plane of the second disc 31. .. At this time, if slip does not occur between the first disk 21, the first spherical rolling element 40, the second spherical rolling element 50, and the idling means 39, the second spherical rolling element 50 moves in the direction of arrow 5A. It stands still without rotating, and similarly, the first spherical rolling element 40 also stands still without rotating in the direction of arrow 4A. Since the first disk 21 and the first axis 20 are also prevented from rotating in the direction of the arrow 2A, the drive source 12 can be locked.

8 and 9 are examples of rotating the first axis 20 and the second axis 30 in the same direction. As shown in FIGS. 8 and 9, when the diameter line L is not between the first axis 20 and the second axis 30, the second axis 30 is the first axis 30 as shown by the arrow 3B in the figure. It rotates in the same direction as the rotation direction of the shaft 20.

By combining the above, according to the continuously variable transmission 10 of the present invention, it is possible to change the gear ratio from the first shaft 20 to the second shaft 30, and of course, the rotation of the second shaft 30 with respect to the first shaft 20. The direction can also be controlled.

In the first embodiment, there are two spherical rolling elements, the first spherical rolling element 40 and the second spherical rolling element 50, but the number may be three or more. In this case, if the number of spherical rolling elements is an even number, the rotation directions of the first axis 20 and the second axis 30 are the same as described above. On the other hand, if the number of spherical rolling elements is odd, the rotation directions of the first axis 20 and the second axis 30 are opposite to those described above.

Further, in the first embodiment, the diameters of the first spherical rolling element 40 and the second spherical rolling element 50 are the same, but the diameters of the first spherical rolling element 40 and the second spherical rolling element 50 may be changed. Absent.

Further, in the first embodiment, the first facing surface 22 of the first disc 21 and the second facing surface 32 of the second disc 31 are each flat, but one of them is concave such as a concave cone shape or a bowl shape. The shape may be a convex shape corresponding to the concave shape. In this case, it is necessary to adjust the distance between the first facing surface 22 and the second facing surface 32 so that the frictional contact between the facing surfaces 22 and 32 and the spherical rolling elements 40 and 50 or the spherical rolling bodies 40 and 50 does not decrease. There is.

According to the continuously variable transmission 10 described above, the gear ratio of the power transmitted from the first shaft 20 to the second shaft 30 can be determined simply by adjusting the contact positions of the spherical rolling elements 40 and 50 with the discs 21 and 31. The direction of rotation can be changed freely, and it can be set to neutral without transmitting power.

Further, since the continuously variable transmission 10 can be composed of the discs 21 and 31, the spherical rolling elements 40 and 50, the holder 60 for holding the spherical rolling elements, and the holder moving means 64, the continuously variable transmission 10 is compared with the conventional continuously variable transmission. The configuration is simple, and it is easy to maintain.

Further, when it is desired to generate a braking effect on the output side, the continuously variable transmission 10 can be used as a brake by moving the holder 60 to adjust the gear ratio. Then, by returning the energy acting on the first axis 20 to the drive source 12 at this time, it can also be used as regenerative energy.

<Second Embodiment>
In the first embodiment, the first spherical rolling element 40 and the second spherical rolling element 50 arranged between the first disk 21 and the second disk 31 so as to make frictional contact with the first disk 21 and the second disk 31 are brought into contact with each other. By connecting the two discs 31 so as to be able to transmit power, the rotation of the first shaft 20 is transmitted to the second shaft 30. On the other hand, in the second embodiment, the rotation of the first shaft 20 is rotated to the second shaft 30 by the meshing of the unevenness. In the second embodiment, unless otherwise specified, the same members as those in the first embodiment are designated by the same members, and the description thereof will be omitted.

FIG. 10 is a cross-sectional view of the continuously variable transmission 10 according to the second embodiment of the present invention. As shown in the figure, the first facing surface 22 and the first spherical rolling element 40 of the first disk 21, the first spherical rolling element 40 and the second spherical rolling element 50, the second spherical rolling element 50 and the second disk 31 A plurality of irregularities are formed on the second facing surface 32, respectively, and these irregularities mesh with each other. In the following description, it goes without saying that the unevenness can be concave as convex and convex as concave.

More specifically, as shown in FIGS. 10 and 11, a first engaging portion 24 having a plurality of protrusions is formed on the first facing surface 22 of the first disc 21. As shown in FIG. 10, the first engaging portion 24 is formed so that all the protrusions are evenly spaced around the center of rotation of the first axis 20. In the illustrated embodiment, with respect to the convex formed at the position corresponding to the rotation center of the first axis 20, other convexes are formed so as to be 60 ° staggered.

Further, as shown in FIG. 11, the second facing surface 32 of the second disc 31 is formed with a second engaging portion 34 having a plurality of concave portions. The second engaging portion 34 is formed so that all the recesses are evenly spaced around the center of rotation of the second shaft 30. In the illustrated embodiment, other recesses are formed so as to be 60 ° staggered with respect to the recess formed at a position corresponding to the rotation center of the second axis 30.

The first spherical rolling element 40 is formed with a first meshing portion 44 that meshes with the first engaging portion 24. The first engaging portion 44 is a concave portion that can mesh with the convex portion of the first engaging portion 24, and is formed on the surface of the first spherical rolling element 40 at substantially equal intervals at the same intervals as the convex portion of the first engaging portion 24. Has been done. It should be noted that the reason why the first meshing portions 44 are formed at substantially equal intervals is that the first meshing portions 44 are ideally formed at equal intervals on the surface of the first spherical rolling element 40, but geometrically evenly spaced portions may be formed. It is impossible. Therefore, for the first engaging portion 24 and the first engaging portion 44 that meshes with the first engaging portion 24, for example, the tip of the convex and / or the inner surface of the concave is chamfered, or the diameter of the concave is formed larger than the diameter of the convex. , It is desirable to have a structure with play.

The second spherical rolling element 50 is formed with a second meshing portion 54 that meshes with the second engaging portion 34 of the second disc 31 and meshes with the first meshing portion 44. The second meshing portion 54 is a convex that can mesh with the concave portion that is the second engaging portion 34 and the concave portion that is the first engaging portion 44, and is at the same interval as the second engaging portion 34 and the first meshing portion 44. It is formed on the surface of the second spherical rolling element 50 at substantially equal intervals. It should be noted that the second meshing portion 54 cannot be geometrically formed at equal intervals like the first meshing portion 44. Therefore, similarly to the above, it is desirable to chamfer the tip of the convex and / or the inner surface of the concave, or to form the diameter of the convex smaller than the diameter of the concave to provide play.

The first spherical rolling element 40 and the second spherical rolling element 50 described above are housed in the holder 60. Inside the holder 60, a bearing 61 such as a thrust bearing and dish-shaped receiving portions 62 and 62 for freely rolling the spherical rolling elements 40 and 50 are provided, and the first spherical rolling element 40 and the second spherical rolling element 50 are provided. Is rotatably accommodated in a state where the first meshing portion 44 and the second meshing portion 54 are in mesh with each other. As in the first embodiment, the holder 60 allows the first spherical rolling element 40 and the second spherical rolling element 50 to be moved in the plane including the first axis 20 and the second axis 30 by the holder moving means 64.

The operating principle of the continuously variable transmission 10 having the above configuration is the same as that of the continuously variable transmission of the first embodiment described above, and while the first embodiment transmits power by frictional contact, the second embodiment The form differs in that power is transmitted depending on the engagement between the engaging portions 24 and 34 and the engaging portions 44 and 54.

That is, when the drive source 12 is operated to rotate the first shaft 20 and the first disc 21, the first spherical rolling element 40 has the first meshing portion 44 with the first engaging portion 24 of the first disc 21. It rotates while meshing sequentially. Since the rotation direction is the same as that of the first embodiment, the description thereof will be omitted.

The second spherical rolling element 50 rotates by moving the second meshing portion 54 while meshing with the first meshing portion 44 as the first spherical rolling element 40 rotates. Then, the rotation causes the second disc 31 and the second shaft 30 connected to the second disc 31 to rotate by moving the second engaging portion 34 that meshes with the second meshing portion 54.

By moving the position of the holder 60 by the holder moving means 64, the rotation direction can be changed and the gear ratio can be adjusted steplessly, and the rotation center of the first axis 20 and the second axis 30 and the first By aligning the rotation centers of the spherical rolling element 40 or the second spherical rolling element 50, it is possible to obtain a neutral state in which the rotation of the first axis 20 is not transmitted to the second axis 30.

In the second embodiment, since power is transmitted by the meshing of concave and convex, slip does not occur between the discs 21, 31 and the spherical rolling elements 40, 50, so that the rotation of the first shaft 20 is accurately performed without loss. It can be transmitted to the two axes 30.

12 and 13 show a configuration in which the engaging portions 24, 34 and / or the engaging portions 24, 34 can be swung in order to guarantee the engagement between the engaging portions 24, 34 and / or the engaging portions 44, 54. More specifically, FIG. 12 is an enlarged view showing an embodiment of the convex side first engaging portion 24 provided on the first disc 21, and FIG. 13 is an enlarged view showing an embodiment of the convex side first engaging portion 24, and FIG. 13 is a concave side first provided on the second disc 31. 2 It is an enlarged view which shows the embodiment of the engaging part.

FIG. 12 is an enlarged view of the first disc 21, in which a plurality of first insertion holes 210 are formed through the first disc 21, and each first insertion hole 210 is provided with a first engagement pin. 250 are arranged. The opening of the first insertion hole 210 on the side of the first facing surface 22 is enlarged in order to allow the first engaging pin 250 to swing.

The first engaging pin 250 has a first bulging portion 251 at its tip, and has a first pin member 252 extending from the first bulging portion 251 toward the first facing surface 22. The first pin member 252 includes a first insertion portion 253 fitted into the first mounting hole 261 of the first holding member 260 described below, and a first groove 254 into which the first retaining means 255 such as a C ring is fitted. Is formed.

A plate-shaped first holding member 260 having elasticity such as rubber is arranged on the back surface side of the first facing surface 22 of the first disc 21. The first holding member 260 is formed with a plurality of first mounting holes 261 that communicate with the first insertion hole 210 of the first disc 21 and into which the first insertion portion 253 of the first pin member 252 is fitted.

The first engaging pin 250 is attached to the first disk 21 by inserting the first insertion portion 253 into the first mounting hole 261 and mounting the first retaining means 255 such as a C ring in the first groove 254. .. Here, as described above, since the first holding member 260 is made of an elastic member such as rubber, the first engaging pin 250 (convex of the first engaging portion 24) is relative to the first disk 21. It can swing.

As shown in FIG. 12, the first spherical rolling element 40 having the first disc 21 having the above configuration and the first engaging portion 44 which is concave is when the first engaging portion 44 faces the first engaging pin 250. Even if the first meshing portion 44 is displaced with respect to the first engaging pin 250, the elastic force of the first holding member 260 causes the first engaging pin 250 to swing, resulting in the first engaging portion. The engagement between the 44 and the first engaging pin 250 (first engaging portion 24) is guaranteed, and power can be transmitted.

FIG. 13 is an enlarged view of the second disc 31, in which a plurality of second insertion holes 310 are formed through the second disc 31, and a second engagement pin is formed in each of the second insertion holes 310. 350 are arranged. The opening of the second insertion hole 310 on the side of the second facing surface 32 has an enlarged diameter so as to allow the second engaging pin 350 to swing.

The second engaging pin 350 has a second recess 351 formed at the tip thereof into which the second engaging portion 34 of the second spherical rolling element 50 is fitted, and extends from the second recess 351 toward the second facing surface 32. It has a second pin member 352. The second pin member 352 includes a second insertion portion 353 that fits into the second mounting hole 361 of the second holding member 360 described below, and a second groove 354 into which the second retaining means 355 such as a C ring fits. Is formed.

A plate-shaped second holding member 360 having elasticity such as rubber is arranged on the back surface side of the second facing surface 32 of the second disc 31. The second holding member 360 is formed with a plurality of second mounting holes 361 that communicate with the second insertion hole 310 of the second disc 31 and into which the second insertion portion 353 of the second pin member 352 is fitted.

The second engaging pin 350 is attached to the second disc 31 by inserting the second insertion portion 353 into the second mounting hole 361 and mounting the second retaining means 355 such as a C ring in the second groove 354. .. Here, as described above, since the second holding member 360 is made of an elastic member such as rubber, the second engaging pin 350 (concave portion of the second engaging portion 34) is relative to the second disk 31. It can swing.

As shown in FIG. 13, the second spherical rolling element 50 having the second disc 31 and the second meshing portion 54 having the above configuration is when the second meshing portion 54 faces the second engaging pin 350. Even if the second meshing portion 54 is displaced with respect to the second recess 351 as a result of the second engaging pin 350 swinging due to the elastic force of the second holding member 360, the second engaging pin 350 The engagement between the second recess 351 and the second recess 351 (second engaging portion 34) is guaranteed, and power can be transmitted.

As described above, by making the first engaging portion 24 and / or the second engaging portion 34 swingable, even if the first spherical rolling element 40 and the second spherical rolling element 50 are geometrically formed. Even when the meshing portions 44 and 54 cannot be formed at equal intervals, the engaging portions 24 and 34 and the meshing portions 44 and 54 can be meshed well.

<Third Embodiment>
In the first embodiment and the second embodiment, the first spherical rolling element 40 and the second spherical rolling element 50 are both spherical, but the first spherical rolling element 40 and the second spherical rolling element 50 are the first. Only the contact surface with the disc 21, the other spherical rolling element 40 or 50, and the second disc 31 has a spherical shape. In the third embodiment, unless otherwise specified, the same members as those in the first embodiment and the second embodiment are designated by the same members, and the description thereof will be omitted.

As shown in FIGS. 14 and 15 (FIG. 15 is a cross-sectional view of the first spherical body 40), the first spherical rolling element 40 and the second spherical rolling element 50 have a spherical shape at the center instead of a spherical shape. It is widened and has a barrel shape with a flat end face.

The first spherical rolling element 40 and the second spherical rolling element 50 have an inner surface whose diameter is reduced to a substantially fan shape in cross section from the outer peripheral side, and bearings 70 and 70a are arranged at the center thereof. Examples of the bearings 70 and 70a include self-aligning ball bearings. Support shafts 71, 71a are rotatably arranged on the inner rings of the bearings 70, 70a, and both ends of the support shafts 71, 71a are connected to the vertical shafts 72, 72 and 72a, 72a, respectively, in a substantially H shape. It has become. The ends of the vertical axes 72, 72 and 72a, 72a are connected by support plates 74, 74a so as to vertically sandwich the first spherical rolling element 40 and the second spherical rolling element 50. Further, the vertical axes 72 and 72a are equipped with rollers 73 and 73a that can roll freely at positions facing the end faces of the spherical rolling elements 40 and 50. The rollers 73, 73a come into contact with the end faces of the spherical rolling elements 40, 50 and roll as the spherical rolling elements 40, 50 rotate, thereby suppressing the rotational shake of the spherical rolling elements 40, 50.

The support plates 74, 74a are swingably supported (75, 75a) by the U-shaped holder 60. The holder 60 has a holder plate 68, 68 having a substantially isosceles triangular shape and a vertical plate 69 connecting the holder plates 68, 68, and the vertical plate 69 is connected to the piston rod 66 of the holder moving means 64.

More specifically, the holder plates 68 and 68 maintain the support plates 74 and 74a in contact with the equiangular two-sided portions so that the first spherical rolling element 40 and the second spherical rolling element 50 are in contact with each other. I support it. Further, the remaining one corner portion of the holder plates 68 and 68 is connected by a vertical plate 69.

The first spherical rolling element 40 and the second spherical rolling element 50 supported as described above can roll with respect to the support shafts 71 and 71a while maintaining the state of being in contact with each other, and the holder plate 68, The support shafts 71, 71a can swing in the plane including the support shafts 71, 71a by 68. Therefore, as in the first embodiment, when the first disc 21 rotates, the rotation is transmitted to the first spherical rolling element 40 and the second spherical rolling element 50, and further transmitted to the second disc 31. .. Further, by the piston rod 66 that moves by expanding and contracting the holder moving means 64, the first spherical rolling element 40 and the second spherical rolling element 50 are connected to the first disk 21 and the second disk 31 as in the first embodiment. By changing the contact position, the ratio of the rotation speeds of the first disc 21 and the second disc 31 can be changed steplessly, and the rotation direction thereof can be changed.

FIG. 14 shows a state in which the support shafts 71 and 71a are parallel to each other. For example, assuming that this state corresponds to FIG. 2 of the first embodiment, when the holder moving means 64 is reduced from this state and the holder 60 is pulled back as shown by the arrow in FIG. 16, the support shafts 71 and 71a It swings so that the tip side approaches, and the contact positions with the first disk 21 and the second disk 31 are changed to the states of FIGS. 16 and 17, which correspond to the states of FIGS. 4, 6 and 8 described above. To reach. As a result, the ratio of the rotation speeds transmitted from the first disc 21 to the second disc 31 is continuously changed to transmit power.

On the other hand, when the holder moving means 64 is extended from the state of FIG. 14 and the holder 60 is pushed out as shown by an arrow in the figure, the first spherical rolling element 40 and the second spherical rolling element 50 are the first disk 21, the second. While rotating while changing the contact position with the disk 31, the state of FIG. 18 corresponding to the above-mentioned states of FIGS. 5, 7 and 9 is reached. As a result, the ratio of the rotation speeds transmitted from the first disc 21 to the second disc 31 is continuously changed to transmit power.

As described above, the first spherical rolling element 40 and the second spherical rolling element 50 are not spherical, but are supported by the holder 60 via bearings 70, 70a and support shafts 71, 71a. Power transmission similar to that of the embodiment can be performed.

The above description is for the purpose of explaining the present invention, and should not be construed as limiting or limiting the scope of the claimed invention. In addition, the configuration of each part of the present invention is not limited to the above embodiment, and it goes without saying that various modifications can be made within the technical scope described in the claims.

10 Continuously variable transmission 20 1st shaft 21 1st disc 22 1st facing surface 24 1st engaging portion 30 2nd shaft 31 2nd disc 32 2nd facing surface 34 2nd engaging portion 40 1st spherical rolling element 44 First meshing portion 50 Second spherical rolling element 54 Second engaging portion 60 Holder 61 Bearing 64 Holder moving means

Claims (11)

1st axis and
A second axis that is parallel to the first axis and eccentric to the first axis,
The first disk connected to the first axis and
A second disk that is at least partially opposed to the first disk and is connected to the second axis.
A first spherical rolling element arranged between the first disc and the second disc and in contact with the first disc,
A second spherical rolling element, which is arranged between the first disk and the second disk, is in contact with the second disk and is connected to the first spherical rolling element so as to be able to transmit power.
The first spherical rolling element and the second spherical rolling element are rotatably and power-transmittedly connected, the first spherical rolling element is brought into contact with the first disk, and the second spherical rolling element is brought into contact with the second disk. With a holder that holds it in contact with
A holder moving means for moving the holder in a plane parallel to the first axis and the second axis in a region facing the first disk and the second disk.
The equipped,
The first spherical rolling element and the second spherical rolling element are spherical.
Continuously variable transmission. 1st axis and
A second axis that is parallel to the first axis and eccentric to the first axis,
The first disk connected to the first axis and
A second disk that is at least partially opposed to the first disk and is connected to the second axis.
A first spherical rolling element arranged between the first disc and the second disc and in contact with the first disc,
A second spherical rolling element, which is arranged between the first disk and the second disk, is in contact with the second disk and is connected to the first spherical rolling element so as to be able to transmit power.
The first spherical rolling element and the second spherical rolling element are rotatably and power-transmittedly connected, the first spherical rolling element is brought into contact with the first disk, and the second spherical rolling element is brought into contact with the second disk. With a holder that holds it in contact with
A holder moving means for moving the holder in a plane parallel to the first axis and the second axis in a region facing the first disk and the second disk.
The equipped,
One or more spherical rolling elements are arranged between the first spherical rolling elements and the second spherical rolling elements.
Continuously variable transmission. The first spherical rolling element and the second spherical rolling element are spherical.
The continuously variable transmission according to claim 2 . The first spherical rolling element has at least a spherical shape at a portion in contact with the first disc and the second spherical rolling element.
The continuously variable transmission according to claim 2 . The first spherical rolling element and the second spherical rolling element are in contact with each other.
The continuously variable transmission according to claim 1 . The first disc and the second disc have a disk shape.
The continuously variable transmission according to any one of claims 1 to 5. At least one of the first disk or the second disk has a diameter equal to or greater than the eccentric distance between the first axis and the second axis.
The continuously variable transmission according to any one of claims 1 to 6. The first disc and the second disc each have a first engaging portion and a second engaging portion formed of a plurality of concave and / or convex portions on opposite surfaces thereof, and the first spherical rolling element has a plurality of concave and / or convex portions. A first meshing portion that meshes with the first engaging portion is formed on the surface, and a second meshing portion that meshes with the second engaging portion is formed on the surface of the second spherical rolling element.
The continuously variable transmission according to any one of claims 1 to 7. In the first spherical rolling element and the second spherical rolling element, the first meshing portion and the second meshing portion mesh with each other.
The continuously variable transmission according to claim 8. The first disc and the first spherical rolling element, and the second disc and the second spherical rolling element are in frictional contact with each other.
The continuously variable transmission according to any one of claims 1 to 7. The first spherical rolling element and the second spherical rolling element are in frictional contact with each other.
The continuously variable transmission according to claim 10.

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