JP2005233432A - Mechanical continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a mechanical continuously variable transmission allowing "contact close to line contact" in place of conventional "point contact". <P>SOLUTION: A roll surface 31 forming a circular arc when cut in a plane passing the center axis of each counter roll 30 is formed on the surface of each counter roll 30. The plurality of counter rolls 30 are rotatably assembled with each other in the state of being adjacent to each other on the same circumference of a disk 40 connected to an output shaft 12 so that the circular arc of each roll surface 30 forms a roughly continued circle. A plurality of power rolls 20 of the same shape are prepared, and installed to be rotated simultaneously in the same direction by a rotating force from the input shaft 11 side, and spherical roll surfaces 21 are formed on the surfaces of the power rolls 20 to 20 so that the power rolls 20 can be brought into contact with the counter rolls 30 on the roll surfaces 21. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a continuously variable transmission that continuously transmits rotation and force (rotational torque) from an input shaft side to an output shaft side, and in particular, from an idling state (neutral) to a forward or reverse rotation direction. The present invention also relates to a continuously variable transmission that can shift continuously.

  For example, as a device that further shifts the rotational torque produced by the engine of an automobile and transmits it to the output shaft to the wheel side, a fluid transmission with a fluid intervening and a planetary gear are used. There is a mechanical transmission. This mechanical transmission can be divided into those that transmit gears in stages using gears and the like and those that are continuously variable.

  As for this mechanical continuously variable transmission, IPC F16H (transmission device) 15/00 is also classified as “transmission device for rotation transmission or reverse rotation having a variable gear ratio by friction between rotating members”. There are also mechanical continuously variable transmissions that utilize "friction". Of course, since the F16H 15/00 of this IPC is further classified, it can be seen that various proposals have been made for mechanical continuously variable transmissions using this type of friction.

  As a mechanical continuously variable transmission in recent years, in particular, a traction drive type, a toroidal CVT (Continuously Variable Transmission) has been in the spotlight. This toroidal CVT is a Charlies W. Hunt first proposed in Patent Document 1 and had the following basic features.

  As shown in FIG. 32, the contents of the Hunt patent described in this Patent Document 1 slide on disks B and D facing each other (the inner surfaces of these disks are toroidal, that is, donut-shaped). The wheel E (hereinafter also referred to as a power roll) is arranged and the angle of the wheel E is changed so that the sliding contact radius of the wheel E with respect to the disc B side and the sliding contact radius of the wheel E with respect to the disc D are relative to each other. It was to change to. Thereby, when the rotational torque of the disk B is transmitted to the disk D, the rotational speed between the disks B and D can be changed.

  As described above, the toroidal CVT according to this Hunt patent has a circular shape like a donut, that is, the toroidal shape of the inner surfaces of both disks B and D. The mechanical continuously variable transmission has come to be called toroidal CVT.

  Since the toroidal CVT according to the Hunt patent has a basic structure as shown in FIG. 32, the toroidal CVT is very simple and has high expectations for industrial use. In particular, in response to the advent of automobiles, application to this was made in the 1920s, and various prototypes and sales were made, but for some reason they were not put into practical use in large quantities.

  Various improvements have been made since then, but the type of recent toroidal CVT has been largely divided into “full toroid” shown in FIG. 33 and “half toroid” shown in FIG.

  The characteristics of the full toroidal CVT are basically the same as those of the Hunt patent. As shown in FIG. 33, as shown in FIG. 33, the center of the power roll (corresponding to the wheel E in FIG. 32) , O ′) passes through the center of the toroidal cavity formed by the inner surfaces of both disks. Thereby, in order to transmit power between the input and output disks, the pressing force between the applied disks does not act on the support shaft for relatively rotating the power roll. The roll angle can be changed smoothly. On the other hand, since the two tangent lines drawn to the contact points O and O 'are parallel to each other, the spin at each contact point O and O' increases.

  On the other hand, in the half toroidal CVT shown in FIG. 34, the two tangents from the contact points O and O ′ are not parallel but have an intersection E. When the intersection point E is on the rotation axis I, the spins at the contact points O and O ′ are eliminated and the CVT becomes efficient.

  In any case, in the toroidal CVT, metals pressed against each other by a strong pressing force come into contact with each other at a contact portion close to a point such as a blackened portion in FIG. (Hiraku Tanaka; Toroidal CVT, issued by Corona in July 2000) If the metals come into contact with each other at a small contact portion close to such a point, naturally frictional heat is generated.

  If this frictional heat is left undisturbed, the metals will be burned together, so oil must be interposed at the contact portion. In addition, in the toroidal CVT, since the two metals (disk or roll) must be pressed with a very strong pressing force, the pressure of the oil to be interposed must also be considerably high. In this case, when this type of toroidal CVT is applied to an automobile, the oil pressure must be increased by using the power of the engine, so that the so-called “fuel consumption” is deteriorated.

In addition, in the conventional CVT, the gear shift in the case of “reverse rotation” cannot be performed at all, and the continuously variable transmission that can steplessly shift from the idling state (neutral) to either the forward or reverse rotation direction. Is waiting for development.
US Patent No. 197472, Hunt Patent

  Therefore, the present inventor has conducted various studies on recent toroidal CVT, that is, how to improve the above-described actual condition in a continuously variable transmission, and as a result, the conventional toroidal CVT is applied to an automobile. The increase in fuel consumption was found to have the greatest cause in the structure in which metals contact each other at a limited portion, and the present invention was completed.

  That is, an object of the present invention is to enable a “contact close to a line contact” from a conventional “limited point contact” for a metal component in this type of mechanical continuously variable transmission. As a result, other energy for maintaining the action can be reduced, and for example, when applied to an automobile, the fuel consumption is reduced.

In order to achieve the above object, first, the means taken by the invention according to claim 1 will be described with reference numerals used in the description of the best mode described below.
“A power roll 20 rotated by a rotary shaft 22 connected to the input shaft 11 side, and a plurality of counter rolls 30 connected to the output shaft 12 by being rotated by contact with the power roll 20 and rotating. A mechanical continuously variable transmission 100,
The surface of each counter roll 30 is formed with a roll surface 31 that forms an arc when cut along a plane passing through the rotation center axis, and the plurality of counter rolls 30 are connected to the same circumference of the disk 40 connected to the output shaft 12. By assembling rotatably in a state of being adjacent to each other on top of each other, each arc of each roll surface 31 forms a substantially continuous circle,
A plurality of power rolls 20 having the same shape are prepared, and these power rolls 20 to 20 are simultaneously rotated in the same direction by the rotational force from the input shaft 11 side. A spherical roll surface 21 is formed on each surface so that the power roll 20 contacts each counter roll 30 on the roll surface 21.
In addition, the mechanical continuously variable transmission 100 capable of rotating forward and reverse is characterized in that the rotating shaft 22 of the power roll 20 can be tilted steplessly with respect to the disk 40 ".
It is.

  That is, in the mechanical continuously variable transmission 100 according to the first aspect, as shown in FIGS. 1 and 2, the power roll 20 rotated by the rotary shaft 22 connected to the input shaft 11 side and the power roll 20 are in contact with each other. As shown in FIG. 12 to FIG. 15, the power roll 20 has the same shape as the power roll 20. A plurality of items are prepared.

  Here, since the description will be complicated if a plurality of power rolls 20 having the same shape are suddenly prepared, the case where a single power roll 20 is prepared will be described.

  As shown in FIGS. 1 and 2, for example, the mechanical continuously variable transmission 100 having a single power roll 20 has a roll surface 21 of the power roll 20 rotated by the rotational force from the input shaft 11. Are arranged so as to be brought into contact with the respective roll surfaces 31 of the plurality of counter rolls 30 arranged in an annular shape. Therefore, in the mechanical continuously variable transmission 100 of the present invention, first, regarding the surface shape of the roll surface 21 of the power roll 20 rotated by the input shaft 11, a “sphere” is cut by, for example, two parallel surfaces. On the other hand, the surface shape of the roll surface 31 of each counter roll 30 is, as shown in FIG. 3, the shape of the roll surface 21 on the power roll 20 side. It is a concave shape corresponding to. That is, the roll surface 31 of each counter roll 30 appears as a complete “arc” when cut along its central axis.

  Accordingly, the lines appearing when the roll surfaces 31 of the counter rolls 30 are cut at the center of the rotation shaft 32 are formed into an annular shape when the counter rolls 30 are arranged in an annular shape. It forms a “circle”. In this circle, the roll surface 21 of one or more power rolls 20 in the neutral state comes into contact with the circle, and when the power roll 20 is tilted, it also comes into contact with the arc portion of the circle. Of course, each counter roll 30 is rotatably assembled to the disk 40 by its rotating shaft 32, and is "rolling contact" with the power roll 20 on the driving side.

  Here, when the relationship between the diameters of the circle formed by the roll surface 21 on the power roll 20 side and the circle formed by each roll surface 31 constituting the ring by connecting a plurality of counter rolls 30 is considered, It is as follows.

  First, regarding the roll surface 21 on the power roll 20 side, in the case of the example shown in FIGS. 1 and 2, as shown in FIG. 3, it has a circle C0 passing through the center O of the sphere as the maximum portion. A circle having a diameter smaller than C0 is taken as the minimum portion. The maximum portion of the circle formed by the roll surface 21 on the power roll 20 side is not necessarily the circle C0 shown in FIG. 3, and the radius is 0 (zero) in the minimum circle. Also good.

  Further, as shown in FIG. 10A, for example, the power roll 20 is fitted in an annular formed by each counter roll 30 and must be prevented from coming off. The inner diameter of the ring formed by each counter roll 30 must be smaller than the outer diameter of the power roll 20. This is true even when only one power roll 20 is used or when a plurality of power rolls 20 described below are used as the present invention.

  Now, the power roll 20 that constitutes the mechanical continuously variable transmission 100 maintains the state in which the roll surface 21 is kept in contact with each counter roll 30, while changing the axial center direction of the rotary shaft 22. It must be tilted with respect to the plane on which the disk 40 is formed. For this purpose, a transmission lever or handle 13 is coupled to the rotary shaft 22 and the rotary shaft 22 and the input shaft 11 are connected using a bevel gear train or the like employed in the best mode described later. To do. Of course, the roll surface 21 of the power roll 20 and the roll surface 31 of each counter roll 30 must be kept in pressure contact with each other. Therefore, the positions of the power rolls 20 and the disks 40 are maintained by the casing 10. In addition, for example, a leaf spring 50 as shown in FIG. 4B is used.

  On the other hand, for each counter roll 30, it is not necessary to change the direction of the rotating shaft 32 at all. An annular contact surface on which 21 abuts smoothly must be formed. Since each counter roll 30 can form only a partial circle of the complete circle of the roll surface 31, a plurality of the counter rolls 30 must be assembled so as to be rotatable on the disk 40 as shown in FIGS. . As shown in FIG. 1, when each counter roll 30 is completely assembled to the disk 40, a substantially continuous annular surface can be formed at the inner center by the roll surface 31 of each counter roll 30. .

  By combining the power roll 20 and the plurality of counter rolls 30 as described above, rotation from the input shaft 11 can be transmitted to the output shaft 12 provided on the disk 40 while changing the speed as follows. .

  First, FIG. 5 shows a so-called “neutral state”. That is, in this case, as shown in FIG. 5B, the roll surface 21 of the power roll 20 is in the same position as the annular surface formed by each counter roll 30, and therefore FIG. As shown, the roll surface 21 of the power roll 20 is in contact with the three counter rolls 30 on each of the upper and lower surfaces in the figure. In the case of this neutral, the center of the three counter rolls 30 has the same center as the center line orthogonal to the rotation axis 22 of the power roll 20. Each counter roll 30 is in a line symmetrical position with respect to the center line of the power roll 20.

  Here, when the power roll 20 is rotated in the direction indicated by the arrow in FIG. 5, the counter rolls 30 in contact with the power roll 20 are rotatably supported by the disk 40, and the power The roll 20 is rotated by being in rolling contact with the roll 20. What is important at this time is that the power roll 20 and each counter roll 30 are always in “contact”, but this is because the roll surface 21 of the power roll 20 has the same shape as a part of the sphere surface. This is because the concave roll surface 31 corresponding to this is formed on the counter roll 30.

  As shown in FIG. 5A, the rotating one power roll 20 is in contact with each of the three counter rolls 30 in the upper and lower parts of the drawing, and is simply rotated. Only. Therefore, in this case (specifically, when the rotating shaft 22 on the power roll 20 side is orthogonal to the plane formed by the disk 40), no force for rotating the disk 40 is applied. Therefore, the disk 40 and hence the output shaft 12 do not rotate.

  Next, in order to consider the case where the rotational force from the input shaft 11 is shifted and transmitted to the output shaft 12 side, the rotational shaft 22 of the power roll 20 is in the state shown in FIG. Assume a state in which the plane is inclined to 30 ° to the left with respect to the plane formed by 40. When the rotary shaft 22, that is, the power roll 20, is tilted, the roll surface 21 continues to make line contact while moving one after another to another counter roll 30 adjacent to the counter roll 30 that has been in contact. To go. This is because the roll surface 21 of the power roll 20 is a part of a spherical surface, the roll surface 31 of each counter roll 30 is also a concave surface corresponding to the spherical surface of the roll surface 21, and each counter roll 30 is annular. This is because each roll surface 31 is substantially continuous. While the power roll 20 is rotated up to 30 ° with respect to the disk 40, the mechanical continuously variable transmission 100 is shifting, but the state is the state when it is rotated up to the next 30 °. The explanation will be based on this.

  When the power roll 20 rotated by the input shaft 11 is tilted with respect to the disk 40 to a position of 30 ° as shown in FIG. 6B, the roll surface 21 of the power roll 20 is set to each counter. Since the roll 30 is still in contact with the roll surface 31, each counter roll 30 is moved in the direction of the small arrow shown in FIG. That is, when looking at one counter roll 30 that is in contact with the power roll 20, the roll surface 31 of the counter roll 30 has a rolling frictional force with a roll surface 21 on the side of the power roll 20 inclined by 30 °. Part of it is used for the rotational force about the rotation shaft 32 of the counter roll 30 and the rest is rotated in the direction indicated by the small arrow shown in FIG. It will be used for power.

  When a force in the direction indicated by the dotted line arrow is applied to each counter roll 30 with which the power roll 20 abuts, the disc 40 is rotated as a result. The disk 40 is half of the rotational speed, and as a result, the output shaft 12 connected to the disk 40 is rotated at a variable speed. Of course, the shifting up to the 30 ° inclination is successively performed.

  When the inclination of the power roll 20 is further increased and the power roll 20 is inclined to 90 ° as shown in FIG. 7B, all of the rotational force of the power roll 20 causes the counter rolls 30 to be The counter roll 30 does not rotate with respect to the disk 40 because it is used for the rotational force in the direction indicated by the outer arrow in FIG. That is, the rotational speed of the power roll 20 and the rotational speed of the disk 40 are the same, and in the case of this 90 ° inclination, no speed change is made.

  Of course, the rotation amount around the rotation shaft 32 of each counter roll 30 gradually decreases from the 30 ° inclination described above to the 90 ° inclination, and the rotation amount of the disk 40 is successively increased. It gets bigger. As a result, the speed change by the mechanical continuously variable transmission 100 is successively performed in accordance with the amount of inclination of the power roll 20, resulting in a “continuously variable speed”.

  And what is important in the mechanical continuously variable transmission 100 is that when the power roll 20 is inclined to the opposite side to the inclination shown in FIG. 6B as shown in FIG. This means that a shift with “reverse rotation” is added. That is, in the mechanical continuously variable transmission 100 according to the present invention, it is possible to perform a stepless shift from the idling state (neutral) to either the forward or reverse rotation direction.

  In the above description, it is assumed that each power roll 20 and counter roll 30 are formed of metal as a material. However, these power roll 20 and counter roll 30 are composed of at least the roll surfaces 21 and 31 thereof. Of course, it may be carried out by forming a resin or ceramic as a material.

  Therefore, the mechanical continuously variable transmission 100 employing one power roll 20 can perform continuously variable transmission while always contacting each power roll 20 and the counter roll 30, and this contact is close to "line contact". Therefore, deformation of the roll surfaces 21 and 31 based on the Herz contact can be suppressed as much as possible, and even if each power roll 20 and the counter roll 30 are formed of a metal material, the amount of generated heat can be suppressed. Thus, the speed can be changed steplessly in either the forward or reverse rotation direction.

  In the mechanical continuously variable transmission 100 described above, there is one power roll 20 for transmitting the rotational force from the input shaft 11 in order to explain the previous stage of the present invention. The number 20 can be made plural, and this becomes the mechanical continuously variable transmission 100 according to the present invention of claim 1.

That is, in the mechanical continuously variable transmission 100 according to the first aspect, as described above with respect to the mechanical continuously variable transmission 100 having one power roll 20 as described above,
“A plurality of power rolls 20 having the same shape are prepared, and these power rolls 20 to 20 are simultaneously rotated in the same direction by the rotational force from the input shaft 11 side.”
It is characterized by.

  Taking the case of two as a plurality, examples as shown in FIGS. 12 to 15 can be considered. The one shown in FIG. 12 divides one power roll 20 shown in FIG. 1 into two parts and integrates them with another casing or the like so that they can be simultaneously rotated in the same direction. It is a thing. In the mechanical continuously variable transmission 100 shown in FIG. 13, the two power rolls 20 are brought into contact with each other obliquely from the inside. In FIG. In 100, two power rolls 20 are brought into contact with the outer surface.

  In the mechanical continuously variable transmission 100 according to the first aspect, since the power roll 20 is divided into a plurality of parts, an assembly space for various parts can be secured in the disk 40 or in the vicinity thereof, and each power roll 20 can be secured. There is an advantage that the abutting direction with respect to the counter roll 30 can be variously changed, and the entire mechanical continuously variable transmission 100 can be easily assembled for manufacturing.

  If the power roll 20 is divided into a plurality of parts as described above, the power roll 20 can be brought into contact with the small casing 10 from all directions of the disk 40.

As described above, when a plurality of power rolls 20 are used, the exposure direction of each counter roll 30 from the disk 40 must be changed. This is the mechanical continuously variable transmission 100 according to claim 2, and the means employed for the mechanical continuously variable transmission 100 according to claim 1 is as follows.
“By changing the exposure direction of each counter roll 30 from the disk 40, the contact position of each power roll 20 with respect to each counter roll 30 can be made arbitrarily”
It is.

  The mechanical continuously variable transmission 100 according to claim 2 can arbitrarily determine the contact position of the power roll 20 divided into a plurality of parts.

  In the mechanical continuously variable transmission 100 according to claims 1 and 2 described above, since the power roll 20 is divided into a plurality of parts, an assembly space for various parts can be secured in or near the disk 40, and In addition, there is a merit that the contact direction of each power roll 20 with respect to the counter roll 30 can be variously changed, and the entire mechanical continuously variable transmission 100 can be easily assembled for manufacturing.

  In the mechanical continuously variable transmission 100 according to the present invention, the spherical diameter of the roll surface 21 of each power roll 20 is made larger than the diameter of the annular surface formed inside by each counter roll 30. It is also possible to press the power roll 20 toward the disk 40 side.

  That is, in this mechanical continuously variable transmission 100, as illustrated in FIG. 9 (B), FIG. 10, and FIG. , The diameter of the sphere forming the roll surface 21) is larger than the diameter of the inner annular surface formed by each counter roll 30, and for example, as shown in FIG. When the power roll 20 is pressed against the side of the disk 40 to which 30 is assembled, it does not come off to the opposite side of the disk 40. For this reason, the power roll 20 can be pressed to the disk 40 side, and the power roll 20 and each counter roll 30 can be surely in line contact with each other. To get. 9 (A) is the same as that shown in FIG. 7 (B), and is shown for comparison with that shown in FIG. 9 (B). is there.

  The mechanical continuously variable transmission 100 shown in FIG. 10A and FIG. 11A corresponds to the “half-toroidal” type shown in FIG. In contrast to this, the mechanical continuously variable transmission 100 shown in FIGS. 10B and 11B has two apparently spheres that define the shape of 21. Although there is a power roll 20 but substantially one, the power roll 20 has a center of a sphere.

  As described above, the roll surface 21 of the power roll 20 always contacts the roll surface 31 of each counter roll 30 so that the power roll 20 and the disk 40 assembled with the plurality of counter rolls 30 are pressed against each other. You have to do that. As a means for that purpose, the pressing force may be generated by fluid pressure, or may be generated by a mechanical configuration using a cam. In the best mode to be described later, the mechanical type according to claim 3 or claim 4 is used. A continuously variable transmission 100 may be used.

That is, the mechanical continuously variable transmission 100 according to a third aspect is the mechanical continuously variable transmission 100 according to any one of the first to second aspects.
“Pressing between each counter roll 30 and power roll 20 is performed by a leaf spring 50 interposed between the support shaft 31 of each counter roll 30 and the disk 40 supporting the counter roll 30”
It is.

  For example, in the case of the mechanical continuously variable transmission 100 shown in FIG. 1, one power roll 20 is arranged at the center in an annular ring formed by a plurality of counter rolls 30. If each counter roll 30 located around 20 is always urged toward the power roll 20, the power roll 20 can be pressed against the disk 40. Since each counter roll 30 is supported on the disk 40 by its rotating shaft 32, in order to bias it to the power roll 20 side, as shown in FIG. The leaf spring 50 is sufficient.

  The leaf spring 50 may be a bellville spring as shown in FIG. 4B or may be a disc spring having a wave shape. In any case, the leaf spring 50 generates an urging force in the thickness direction of the plate, and can be incorporated in a very narrow space.

  That is, since there is not so much free space between each counter roll 30 and the disk 40, the “plate spring” is the most effective as a spring for applying an urging force. Originally, the power roll 20 and each counter roll 30 are designed to be in close contact with each other, so that the space for pressing may be small. In such a condition, the leaf spring 50 is most effective for pressing each disk 40 against the power roll 20.

  As another pressing method, there is one as in the first embodiment shown in FIGS. 16 to 25, and this is the invention according to claim 4.

That is, the means taken by the mechanical continuously variable transmission 100 according to claim 4 is the mechanical continuously variable transmission 100 according to any one of claims 1 to 3.
“Pressing between each counter roll 30 and power roll 20 is performed by a leaf spring 50 interposed between the disk 40 and the casing 11 supporting the disk 40”.
It is.

  In the mechanical continuously variable transmission 100 according to claim 4, as shown in FIG. 16, the power roll 20 to be connected to the input shaft 11 is completely assembled to the casing 10. It is assembled so that the center of the sphere defining the roll surface 21 of the power roll 20 does not move at all. If each counter roll 30 is pressed against such a power roll 20, the power roll 20 and the counter roll 30 can be sufficiently in close contact with each other. The 40 side may be urged toward the power roll 20.

  In the example shown in FIG. 16, the output shaft 12 is rotatable with respect to the casing 10, but is prevented from coming off by using a bearing so as not to move in the horizontal direction in the figure. A spline is formed on the inner end portion of the output shaft 12, and an arm on the disk 40 side is fitted to the spline. That is, the disk 40 can be moved in the axial direction with respect to the inner end portion of the output shaft 12, but is assembled so as not to rotate with respect to the output shaft 12.

  In the mechanical continuously variable transmission 100 shown in FIG. 16, a plurality of leaf springs 50 are assembled between the inner end surface of the inner race of the bearing built into the casing 10 and the outer end surface of the arm of the disk 40. is there. These leaf springs 50 are bent in the left-right direction in the figure, and thereby urge the disc 40 toward the power roll 20 to a slight extent.

  Therefore, in the mechanical continuously variable transmission 100 according to the fourth aspect, the disk 40 incorporating a plurality of counter rolls 30 is attached to the power roll 20 whose position is fixed by a very small part called a leaf spring 50. Thus, the line contact between the power roll 20 and each counter roll 30 is maintained in a stable state.

  In the mechanical continuously variable transmission 100 shown in FIG. 16, a spline is formed at the inner end of the output shaft 12, and the arm on the disk 40 side is fitted to this. That is, if there is a means for moving this arm in the direction opposite to the urging direction of the leaf spring 50, the contact between the power roll 20 and each counter roll 30 can be released, and torque transmission is not performed. That is, “clutch operation” can be performed. It is the mechanical continuously variable transmission 100 according to claim 5 that enables such clutch operation.

That is, the means taken by the invention according to claim 6 is the mechanical continuously variable transmission 100 according to any one of claims 1 to 4.
“The power roll 20 or each counter roll 30 can be moved in the direction opposite to the pressing direction, and the power roll 20 or each counter roll 30 is moved in the direction opposite to the pressing direction. It has a clutch function that eliminates frictional contact between each counter roll 30 and eliminates the transmission of force between them ”
It is.

The present invention has been made for the purpose of enabling "contact close to line contact" from conventional "point contact" in a mechanical continuously variable transmission, and enables contact close to line contact. In order to obtain a mechanical continuously variable transmission 100 that can reduce the mutual pressing force of the metal components and reduce other energy for maintaining the action,
“A power roll 20 rotated by a rotary shaft 22 connected to the input shaft 11 side, and a plurality of counter rolls 30 connected to the output shaft 12 by being rotated by contact with the power roll 20 and rotating. A mechanical continuously variable transmission 100,
The surface of each counter roll 30 is formed with a roll surface 31 that forms an arc when cut along a plane passing through the rotation center axis, and the plurality of counter rolls 30 are connected to the same circumference of the disk 40 connected to the output shaft 12. By assembling rotatably in a state of being adjacent to each other on top of each other, each arc of each roll surface 31 forms a substantially continuous circle,
A plurality of power rolls 20 having the same shape are prepared, and these power rolls 20 to 20 are simultaneously rotated in the same direction by the rotational force from the input shaft 11 side. A spherical roll surface 21 is formed on each surface so that the power roll 20 contacts each counter roll 30 on the roll surface 21.
In addition, the rotating shaft 22 of the power roll 20 can be inclined steplessly with respect to the disk 40. "
Is.

  Next, the invention of each claim configured as described above will be described with respect to the mechanical continuously variable transmission 100 which is the best mode shown in the drawings. The mechanical continuously variable transmission 100 according to the present invention is illustrated in FIG. 12 to 15. 12 and 15 show the mechanical continuously variable transmission 100 having one power roll 20 necessary for explaining the mechanical continuously variable transmission 100 according to the present invention. It is.

16 to 25 show a first embodiment of the mechanical continuously variable transmission 100 related to the present invention, and FIGS. 26 to 31 show a second embodiment of the mechanical continuously variable transmission 100. An example is shown. Further, since each invention is entirely included in the mechanical continuously variable transmission 100 which is the best mode, in the following, the mechanical continuously variable transmission 100 of the best mode will be described as the first embodiment and the first embodiment. Two examples will be described separately.
(First embodiment)
FIG. 16 shows a cross-sectional plan view of a mechanical continuously variable transmission 100 according to the present invention. This mechanical continuously variable transmission 100 is received by an input shaft 11 protruding to the right side of the casing 10 in the figure. The rotational force is transmitted to the output shaft 12 projecting to the left side of the casing 10 while continuously changing the speed, and most of the components are incorporated in one casing 10. The mechanical continuously variable transmission 100 according to the first embodiment is of a type in which one power roll 20 is fitted into an annular ring formed by counter rolls 30 assembled to a disk 40, This corresponds to that shown in FIGS.

  Now, as shown in FIG. 16, the single hemispherical power roll 20 is rotated around the rotating shaft 22 and tilted around a rotating shaft 73 described later with respect to the casing 10. It is assembled so that. Then, the rotation of the power roll 20 by the rotational force from the input shaft 11 is performed by the rotational force transmission mechanism 60 shown in FIG. 16, and the tilt of the rotational shaft 22 is caused by the shift lever or the handle 13. It is made by the inclination mechanism 70 which transmits operation.

  Of course, the roll surface 21 of the power roll 20 has the same shape as the partial surface of the sphere, but the large diameter side of the power roll 20 has a rotational force transmission mechanism 60 or A large opening is provided to allow the tilting mechanism 70 to be incorporated. Further, the inside of the power roll 20 is a cavity, and a base 71 constituting the tilt mechanism 70 is incorporated therein.

  As shown in FIGS. 19 and 20, the rotational force transmission mechanism 60 that rotates the power roll 20 includes an intermediate shaft 61 that transmits the rotational force from the input shaft 11 through the illustrated bevel gear, and the intermediate shaft 61. A free bevel gear 62 that transmits the rotational force from the shaft 61 to the fixed bevel gear 63 on the power roll 20 side, avoiding the rotation shaft 73 on the tilt mechanism 70 side, and the center for fixedly connecting the fixed bevel gear 63 to the power roll 20 It consists of a shaft 64. Of course, the intermediate shaft 61 has a bevel gear meshing with a bevel gear fixed to the input shaft 11 at both ends thereof and a bevel gear meshing with the free bevel gear 62, respectively. In order to prevent interference with the input shaft 11, as shown in FIG.

  According to such a rotational force transmission mechanism 60, as shown in FIGS. 16 to 21, the rotational force from the input shaft 11 is first transmitted to the intermediate shaft 61 via the bevel gear, and the rotation of the intermediate shaft 61 is performed. It is transmitted to the free bevel gear 62 via the bevel gear. What is important here is that the free bevel gear 62 is positioned so that the rotation shaft 73 that tilts the power roll 20 is located at the center thereof, and can freely rotate with respect to the rotation shaft 73. That is. As a result, the rotational force on the input shaft 11 side can be transmitted to the fixed bevel gear 63 on the power roll 20 side, irrespective of the tilting of the power roll 20 caused by the operation of a shift lever or handle 13 described later.

  A free bevel gear 62 that can freely rotate on the rotation shaft 73 is connected to a central shaft 64 via a fixed bevel gear 63, and the central shaft 64 and the free bevel gear 62 are connected to the tilt mechanism 70 side via a bearing 72. The base 71 is rotatable.

  As a result, as shown in FIG. 19, the power roll 20 is completely independent of the tilting motion by the tilt mechanism 70 described later, and is rotated by the rotational force from the input shaft 11. However, even if it is tilted to the position shown in FIGS. 22 to 25, it is stably rotated by the input shaft 11.

  Next, the tilting mechanism 70 for tilting the power roll 20 is provided. The tilting mechanism 70 is a base housed in the power roll 20 via a bearing 72 as shown in FIGS. 71, a rotating shaft 73 that is bridged to the base 71 as shown in FIGS. 19 and 21 and passes through the center of the free bevel gear 62 that constitutes the rotational force transmission mechanism 60 described above, and this rotation A worm 74 fixedly attached to one end of the moving shaft 73, and a worm provided on the inner end of the speed change lever or handle 13 protruding from the casing 10 as shown in FIG. A wheel 75 is provided.

  According to such a tilting mechanism 70, first, as shown in FIG. 20, the worm 74 is rotated by adjusting the rotation of the shift lever or the handle 13, and the worm wheel 75 meshing with the worm wheel 75 is rotated by the rotation amount of the worm 74. And it will rotate according to the direction. What is important here is that a worm 74 is provided on the shift lever or handle 13 side and a worm wheel 75 is provided on the rotating shaft 73 side. This is because a reaction force is received on the rotating shaft 73 side when the mechanical continuously variable transmission 100 is operated. However, depending on the reaction force, a shift lever or a handle is provided. This is because no force is applied to the side 13 and the rotation of the speed change lever or handle 13 can be adjusted stably.

  Now, as shown in FIG. 19, the worm wheel 75 rotated in accordance with the rotation adjustment of the speed change lever or the handle 13 is integrated with the rotating shaft 73 bridged by the base 71. The base 71 is tilted about the axis 73, that is, about the rotation shaft 73 shown in FIG. Of course, the power roll 20 tilted by the tilt mechanism 70 is also driven to rotate by a rotational force transmission mechanism 60 of a completely different system from the tilt mechanism 70.

  The tilting state of the power roll 20 is shown by way of example in FIGS. 22 to 25. However, since the mechanical continuously variable transmission 100 performs a continuously variable transmission, these FIGS. Needless to say, is a continuous change. 22 to 25, (A) shows a schematic plan view of the worm wheel 75, and the relationship between the power roll 20 and each counter roll 30 in that state is shown by a vertical side view of (B). ing.

  The counter roll 30 is in contact with the power roll 20 that rotates and tilts as described above. In the mechanical continuously variable transmission 100 according to the present embodiment, many of the counter rolls 30 are arranged as shown in FIGS. As shown in FIG. 4, the disc 40 is assembled so as to form an annular shape. Of course, as shown in FIGS. 17 and 18, the roll surface 31 of each counter roll 30 has a concave shape so as to be in contact with the outer surface of the sphere. The disc 40 is supported. The counter roll 30 is supported on the disk 40 as described above with reference to FIG. 1 by supporting the rotating shaft 32 with the bearing 33 so that the counter roll 30 can freely rotate with respect to the disk 40.

  Since the disk 40 is for collecting the reaction force received by each counter roll 30 by the rotation of the power roll 20 to the output shaft 12 side together, as shown in FIG. The output shaft 12 is splined. The disk 40 is spline-coupled to the output shaft 12 because the disk 40 reliably transmits the rotational force to the output shaft 12 side, but the urging force from the leaf spring 50 is shown in FIG. This is to make a right contact with the power roll 20 in a right direction.

Therefore, in the mechanical continuously variable transmission 100 according to the first embodiment, between each leg 41 of the disk 40 and the inner race of the bearing 14 that rotatably supports the output shaft 12 with respect to the casing 10. This is because a plurality of leaf springs 50 are incorporated in the. That is, these leaf springs 50 act so as to resiliently press the disk 40 assembled with a large number of counter rolls 30 against the power roll 20 supported by the casing 10.
(Second embodiment)
26 to 31 show a second embodiment of the mechanical continuously variable transmission 100 according to the present invention. The schematic configuration of the mechanical continuously variable transmission 100 is shown in FIG. It is similar to what is shown. In the mechanical continuously variable transmission 100 according to the second embodiment, the rotational force transmitted from the input shaft 11 and the tilting of the power roll 20 by the shift lever or the handle 13 are incorporated in the power roll 20. The whole is made compact by performing it with a member.

  That is, in the mechanical continuously variable transmission 100 according to the second embodiment, as shown in FIGS. 26 and 27, the power roll 20 has two identical roll rolls 21 each having a roll surface 21 having a spherical shape. The two power rolls 20 are integrally connected by a rotating shaft 22 as a center while being formed of a shape. As a result, the power roll 20 has a shape in which the upper and lower sides of the sphere are cut off by about ¼, and an opening 23 as shown in FIG. It will be a thing. As shown in FIG. 26, the input shaft 11 is inserted into the opening 23 from the right side of the drawing, and the inclined shaft 15 rotated by the speed change lever or the handle 13 is inserted from the left side of the drawing. It becomes.

  Since the inner end of the input shaft 11 inserted into the power roll 20 is meshed with the inner surface side via a bevel gear, the entire power roll 20 causes the rotation shaft 22 to be rotated by the rotational force of the input shaft 11. It will be rotated to the center. That is, the power roll 20 is rotated by the input shaft 11 in the left-right direction in the drawing with the rotation shaft 22 shown in FIG. Of course, as shown in FIG. 27, the power roll 20 is formed with an opening 23 through which the input shaft 11 can pass, so that the power roll 20 has the input shaft 11 and an inclined shaft described below. It rotates without interfering with 15.

  On the other hand, the inner end of the inclined shaft 15 inserted into the power roll 20 from the side opposite to the input shaft 11 is connected to the sleeve 16 fitted to the outer periphery of the rotary shaft 22 on the power roll 20 side. It is. The sleeve 16 is incorporated into the power roll 20 through various bearings and can freely rotate with respect to the rotating shaft 22 on the power roll 20 side. In other words, even if the power roll 20 is rotated by the input shaft 11, the sleeve 16 does not rotate. As a result, the inner end of the inclined shaft 15 can be fixed.

  Now, since the inner end of the inclined shaft 15 is fixedly connected to the sleeve 16, the power roll 20 is shown in FIGS. 29 and 30 by rotating the speed change lever or the handle 13 in a predetermined direction. Thus, the rotation of the power roll 20 by the input shaft 11 is not obstructed even after the change.

  As described above, the power roll 20 is rotated by the input shaft 11 and tilted by the speed change lever or the handle 13. The power roll 20 contacts a number of counter rolls 30 disposed in the casing 10. For this reason, the rotational force of the power roll 20 is transmitted to the disc 40 supporting each counter roll 30 because the speed is changed according to the inclined state. Since the output shaft 12 is connected to the disk 40 as shown in FIG. 26 and the like, as a result, the rotation of the input shaft 11 is shifted and output from the output shaft 12.

  In the second embodiment, as shown in FIG. 26, a plurality of leaf springs 50 are interposed between the casing 10 and the disc 40, so that the disc 40 is moved by the urging force of these leaf springs 50. It is always pressed toward the power roll 20 side.

  In addition, as shown in FIG. 28, the many counter rolls 30 assembled to the disk 40 are formed in an annular shape by the inner ends of the respective roll surfaces 31. As described above, the roll surface 21 of the power roll 20 and the roll surface 31 of each counter roll 30 come into contact with each other even if the state is inclined. Furthermore, since the power roll 20 must always be in contact with the annular roll surface formed by each counter roll 30, the size of the power roll 20 relative to the ring by each counter roll 30 is shown in FIG. As described above, the relationship shown in FIG.

  The state of shifting by the mechanical continuously variable transmission 100 according to the second embodiment is as shown in the graph of FIG. In this graph, the horizontal axis represents the inclination angle of the power roll 20, and the horizontal axis represents the gear ratio. The minus sign means that the input shaft 11 rotates in the direction opposite to the rotation direction.

  As described above in detail, according to the mechanical continuously variable transmission 100 of the present invention, the roll surface 21 of the power roll 20 and the roll surfaces 31 of the plurality of counter rolls 30 can be brought into contact with each other to perform speed change. As a result, the rotational force from the input shaft 11 side can be efficiently transmitted to the output shaft 12 side, and energy loss can be suppressed.

  In addition, since the power roll 20 and each counter roll 30 are in contact with each other, power transmission can be performed without greatly pressing the both. As a result, it is not necessary to supply oil for suppressing heat generation, and even if it is supplied, it is not necessary to increase the oil pressure.

  Furthermore, according to the mechanical continuously variable transmission 100 of the present invention, it is possible to perform a stepless shift from the idling state (neutral) to the forward or reverse rotational direction only by changing the inclination angle of the power roll 20. Is.

  Therefore, when the mechanical continuously variable transmission 100 according to the present invention is used as a component of a machine tool or an automobile, not only continuously variable transmission including reverse rotation but also energy loss for the operation is minimized. It can be suppressed and is very useful in the industry.

It is a partially broken front view which shows an example of the relationship between the power roll 20 and the some counter roll 30 in the mechanical continuously variable transmission 100 relevant to this invention which has one power roll. It is the longitudinal cross-sectional view. It is sectional drawing which shows the end surface shape of the roll surface 21 by the side of the power roll 20 and the roll surface 31 by the side of the counter roll 30 which looked at the bulb | ball 0 as the center. It is the enlarged view (A) of the 1-1 line | wire part of FIG. 1, and the expanded sectional view (B) of the leaf | plate spring 50 currently used there. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown in a cross-sectional plan view of (A) and a longitudinal front view of (B), and shows a case where the power roll 20 and the disk 40 are orthogonal to each other. It is a thing. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown in a cross-sectional plan view of (A) and a longitudinal front view of (B), and shows a case where the power roll 20 is inclined at 30 °. Is. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown in a cross-sectional plan view of (A) and a longitudinal front view of (B), and shows a case where the power roll 20 is inclined at 90 °. Is. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown in a cross-sectional plan view of (A) and a longitudinal front view of (B), showing a case where the power roll 20 is inclined at −30 °. It is a thing. An example in which one power roll 20 is used, (A) shows a case where the maximum part of the power roll 20 is in contact with each counter roll 30, and (B) shows a part smaller than the maximum part of the power roll 20. It is a schematic diagram which shows the case where it contacts each counter roll 30, respectively. An example in which a portion smaller than the maximum portion of the power roll 20 is in contact with each counter roll 30 is shown. (A) shows the case where one power roll 20 is used, and (B) shows two power rolls 20. It is a schematic diagram which respectively shows the case where it uses and it is set as one thing substantially. The case where two disks 40 parallel to each other are arranged on both sides of the power roll 20 is shown. (A) shows the case where one power roll 20 is used, and (B) shows the case where two power rolls 20 are used. It is a schematic diagram which shows each case. The mechanical continuously variable transmission which concerns on this invention is shown, each shows a mode that the example at the time of employ | adopting the several power roll 20 was inclined in order of (A)-(C), and each power roll An example is shown in which 20 is brought into contact with a ring formed by a counter roll 30. 1 shows a mechanical continuously variable transmission according to the present invention, and shows an example of a case where a plurality of power rolls 20 are used, each of which is inclined in the order of (A) to (C). Shows an example in which it is in contact with the inside diagonally. 1 shows a mechanical continuously variable transmission according to the present invention, and shows an example of a case where a plurality of power rolls 20 are used, each of which is tilted in the order of (A) to (C). The example which made each power roll 20 contact | abut to the orthogonal position is shown. 1 shows a mechanical continuously variable transmission according to the present invention, and shows an example in which a plurality of power rolls 20 are employed, and each of the power rolls is shown in an inclined manner in the order of (A) to (C). The example which made 20 contact | abut from the up-and-down both sides of the counter roll 30 is shown. 1 is a cross-sectional plan view showing a mechanical continuously variable transmission 100 according to a first embodiment of the present invention. 2 is a front view of a disk 40 to which a counter roll 30 of the mechanical continuously variable transmission 100 is assembled. FIG. 2 is a longitudinal side view of a disk 40 of the mechanical continuously variable transmission 100. FIG. 2 is a partial cross-sectional view showing a connection relationship between an input shaft 11 and one power roll 20 of the mechanical continuously variable transmission 100. FIG. FIG. 20 shows a connection relationship between the input shaft 11 and the power roll 20 of the mechanical continuously variable transmission 100, and is a partial longitudinal sectional view taken along line 2-2 in FIG. FIG. 20 shows a tilting mechanism for the input shaft 11 of the power roll 20 of the mechanical continuously variable transmission 100, and is a transverse sectional view taken along line 2-3 in FIG. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown in a cross-sectional plan view of (A) and a longitudinal front view of (B). When the power roll 20 is orthogonal to the disk 40 Is shown. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown by a cross-sectional plan view of (A) and a longitudinal front view of (B), and shows a case where the power roll 20 is inclined by 30 °. It is. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown in a cross-sectional plan view of (A) and a longitudinal front view of (B), and shows a case where the power roll 20 is parallel to the disk 40. Is. The relationship between one power roll 20 and the disk 40 corresponding thereto is shown by a cross-sectional plan view of (A) and a longitudinal front view of (B), and shows a case where the power roll 20 is inclined by -15 °. Is. 1 is a longitudinal front view of a mechanical continuously variable transmission 100 according to a second embodiment of the present invention. FIG. 27 is a longitudinal front view showing a mechanical continuously variable transmission 100 according to a second embodiment of the present invention, as seen in a plane orthogonal to the case of FIG. 26. FIG. 27 shows a mechanical continuously variable transmission 100 according to a second embodiment of the present invention, and is a plan view taken along line 4-4 in FIG. The relationship between the power roll 20 and the disk 40 with respect to the mechanical continuously variable transmission 100 according to the second embodiment is shown. (A) shows a case where the power roll 20 and the disk 40 are orthogonal to each other. B) shows the case where the power roll 20 is inclined at −30 °, and (C) shows the case where the power roll 20 is inclined at 30 °. The relationship between the power roll 20 and the disk 40 with respect to the mechanical continuously variable transmission 100 according to the second embodiment is shown. (A) shows the case where the power roll 20 is inclined at 60 °. B) shows the case where the power roll 20 is inclined at 90 °. It is a graph which shows the gear ratio obtained when the power roll 20 is made to incline with the angle of a vertical axis | shaft direction. It is drawing used by the Hunt patent. It is sectional drawing which shows full toroidal CVT. It is sectional drawing which shows half toroidal CVT. It is a perspective view which shows that it is a point contact in the conventional toroidal CVT.

Explanation of symbols

100 ... Mechanical continuously variable transmission,
10 ... casing,
11 ... Input shaft,
12 ... Output shaft,
13 ... shift lever or handle,
14 ... bearings,
15 ... Inclined axis,
16 ... Sleeve,
20 ... Power roll,
21 ... roll surface,
22 Rotating shaft,
23 ... Opening,
30 ... Counter roll,
31 ... roll surface,
32 ... rotating shaft,
33 ... Bearing,
34 ... Base,
40 ... disc,
50 ... leaf spring,
60 ... rotational force transmission mechanism,
61 ... Intermediate shaft,
62 ... Free bevel gear,
63 ... fixed bevel gear,
64 ... central axis,
70 ... tilting mechanism,
71 ... Base,
72 ... bearings,
73 ... rotating shaft,
74 ... Worm,
75 ... Worm wheel

Claims (5)

The power roll (20) rotated by the rotating shaft (22) connected to the input shaft (11) side and the power roll (20) are rotated by contact and rotated to be output to the output shaft (12). A mechanical continuously variable transmission (100) comprising a plurality of connected counter rolls (30),
On the surface of each counter roll (30), a concave roll surface (31) that forms an arc when cut by a plane passing through the rotation center axis is formed, and the plurality of counter rolls (30) are connected to the output shaft (12). ) In a state where the disks (40) are connected to each other on the same circumference so as to be freely rotatable so that each arc of each concave roll surface (31) forms a substantially continuous salt,
A plurality of power rolls (20) having the same shape are prepared, and these power rolls (20) to (20) are simultaneously rotated in the same direction by the rotational force from the input shaft (11) side, A spherical roll surface (21) is formed on each surface of the power rolls (20) to (20), and the power roll (20) is attached to each counter roll (30) on the roll surface (21). Make contact,
A mechanical continuously variable transmission (100) capable of forward and reverse rotation characterized in that the rotating shaft (22) of the power roll (20) can be tilted steplessly with respect to the disk (40). .   The contact position of each power roll (20) with respect to each counter roll (30) can be made arbitrary by changing the exposure direction of each counter roll (30) from the disk (40). The mechanical continuously variable transmission (100) according to Item 1.   The pressure between each counter roll (30) and the power roll (20) is a plate interposed between the support shaft (31) of each counter roll (30) and the disk (40) supporting the same. The mechanical continuously variable transmission (100) according to any one of claims 1 to 2, wherein the mechanical continuously variable transmission (100) is performed by a spring.   The pressing between each counter roll (30) and the power roll (20) is performed by a leaf spring (50) interposed between the disk (40) and the casing (11) supporting the disk (40). The mechanical continuously variable transmission (100) according to any one of claims 1 to 3, wherein the mechanical continuously variable transmission (100) is provided. The power roll (20) or each counter roll (30) can be moved to the side opposite to the pressing direction, and the power roll (20) or each counter roll (30) is moved to the side opposite to the pressing direction. Thus, a frictional contact caused by pressing between the power roll (20) and each counter roll (30) is released, and a clutch function for eliminating transmission of force between the two is provided. The mechanical continuously variable transmission (100) according to any one of claims 1 to 4.

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