JP2011122625A - Load-sensitive continuously variable transmission - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a load-sensitive continuously variable transmission, capable of automatically and continuously varying speed according to a load by a small-sized, lightweight and inexpensive structure. <P>SOLUTION: The load-sensitive continuously variable transmission includes an input shaft 10; an input disk 11 fixed to the input shaft 10; an output disk 21 disposed oppositely to the input disk 11; an output shaft 20 fixed to the output disk 21; a first power transmission disk 30 and a second power transmission disk 31 which are disposed to sandwich the input disk 11 and the output disk 21 therebetween, and transmits rotation from the input disk 11 to the output disk 21 through friction force; a holding member 40 which rotatably holds the first power transmission disk 30 and the second power transmission disk 31; and a bias mean 50 which biases the holding member 40. <P>COPYRIGHT: (C)2011,JPO&amp;INPIT

Description

  The present invention relates to a load-sensitive continuously variable automatic transmission.

  A load-sensitive type in which the high-speed side clutch output disk is connected to the high-speed side input disk when the load is small and the low-speed side clutch output disk is connected to the low-speed side input disk when the load is large due to the action of the spring and magnet. An automatic transmission is disclosed (for example, refer to Patent Document 1).

  Further, a rotary continuously variable transmission is disclosed in which a cylindrical body is pressed against a tapered surface of a transmission, and a radius formed by a pressure contact between an edge of the cylindrical body and the tapered surface changes according to a load (for example, (See Patent Document 2).

Japanese Patent No. 3584396 JP 2002-276759 A

  However, the adjustment range of the reduction ratio by the load-sensitive automatic transmission of Patent Document 1 is two stages of high speed and low torque and low speed and high torque, and the reduction ratio is adjusted steplessly according to the continuously changing load. I can't. In addition, it has a complex number of parts including a high-speed input disk, a low-speed input disk, a reducer, a high-speed clutch output disk, a low-speed clutch output disk, a clutch plate connecting rod, an output disk, a magnet, a spring, etc. Therefore, it is difficult to reduce the size, weight, and cost.

  Further, in the rotary continuously variable transmission of Patent Document 2, it is difficult to apply a large load because the portion where the edge of the cylindrical body is pressed against the tapered surface of the transmission is unstable. In addition, it has a complicated configuration with a large number of parts including a planetary gear, a transmission with a tapered surface, a cylindrical body with a hole in the bottom, a disk with a hole, a sphere, etc. It is difficult to reduce weight and cost.

  The present invention has been made in view of the above problems, and provides a load-sensitive continuously variable automatic transmission that can automatically and continuously change gears according to a load with a small, lightweight, and low-cost configuration. This is the issue.

  According to a first aspect of the present invention, there is provided a load-sensitive continuously variable automatic transmission in which an input shaft, an input disk fixed to the input shaft, and an output spaced apart from the input disk are arranged. A disc, an output shaft fixed to the output disc and arranged coaxially with the input shaft, and opposed to sandwich the input disc and the output disc, and the output from the input disc A first power transmission disk and a second power transmission disk that transmit rotation to the disk via frictional force, and a holding member that rotatably holds the first power transmission disk and the second power transmission disk And urging means for urging the holding member.

  According to a second problem-solving means of the present invention, the holding member holds the first power transmission disk movably in a direction perpendicular to the input shaft and parallel to the first power transmission disk. The second power transmission disc is held movably in a direction perpendicular to the input shaft and parallel to the second power transmission disc.

  A third problem solving means of the present invention is that the urging means is a curved portion provided on at least one of the first power transmission disk and the second power transmission disk.

  According to the present invention, a load-sensitive continuously variable automatic transmission that has a simple configuration including an input disk, a first power transmission disk, a second power transmission disk, an output disk, and the like, is small, light, and low in cost. It becomes. In this load-sensitive continuously variable automatic transmission, when the load on the output side increases, the frictional force generated between the output disk on which the output shaft is fixed, the first power transmission disk, and the second power transmission disk Due to this, the distance from the center of the first power transmission disk (or the second power transmission disk) to the contact point between the output disk and the first power transmission disk (or the second power transmission disk) is short, In the direction that the distance from the center of the power transmission disk (or the second power transmission disk) to the contact point between the input disk and the first power transmission disk (or the second power transmission disk) becomes longer, the first power The transmission disk and the second power transmission disk automatically move to increase the reduction ratio. Further, when the load decreases, the output disk and the first power transmission disk (or the second power transmission disk) from the center of the first power transmission disk (or the second power transmission disk) by the biasing force of the biasing means. The distance to the contact point with the power transmission disk is long, and the input disk and the first power transmission disk (or the second power transmission disk) from the center of the first power transmission disk (or the second power transmission disk). The first power transmission disk and the second power transmission disk are automatically moved in the direction in which the distance to the contact point becomes shorter, thereby reducing the reduction ratio.

  The first power transmission disc is movable in a direction perpendicular to the input shaft and parallel to the first power transmission disc, and the second power transmission disc is perpendicular to the input shaft and the second power transmission disc. Can be shifted more smoothly.

  The biasing means may use a spring member, but by providing a curved portion in at least one of the first power transmission disk and the second power transmission disk, a spring member as the biasing means or The urging force can be applied to the first power transmission disk and the second power transmission disk without specially providing a fixing member for fixing the urging means, leading to reduction in the number of parts and miniaturization.

1 is a conceptual diagram illustrating a load-sensitive continuously variable automatic transmission according to an embodiment of the present invention. 1 is a perspective view showing a part of a load-sensitive continuously variable automatic transmission according to an embodiment of the present invention. It is explanatory drawing which shows transmission of rotation from the input disk to an output disk via a 1st power transmission disk. It is explanatory drawing which shows transmission of rotation from the input disk to an output disk via a 2nd power transmission disk. It is explanatory drawing which exaggerates and shows the state which the 1st power transmission disc moved to the position where the extension line of the 1st rotating shaft of the 1st power transmission disc does not cross | intersect the extension line of an input shaft and an output shaft. It is explanatory drawing which exaggerates and shows the state which the 2nd power transmission disc moved to the position where the extension line of the 2nd rotating shaft of the 2nd power transmission disc does not cross | intersect the extension line of an input shaft and an output shaft. FIG. 5 is a perspective view showing a load-sensitive continuously variable automatic transmission in which a first insertion hole of a holding member is elongated in a direction perpendicular to an input shaft and parallel to a first power transmission disc. It is a perspective view which shows the state which rotated 180 degree | times about the axis | shaft substantially perpendicular | vertical to the paper surface of the load sensitive continuously variable transmission of FIG. It is a conceptual diagram which shows the load-sensitive continuously variable automatic transmission with which the 1st power transmission disc was equipped with the 1st curved part, and the 2nd power transmission disk was equipped with the 2nd curved part.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

  FIG. 1 is a conceptual diagram showing a load-sensitive continuously variable automatic transmission according to an embodiment of the present invention. FIG. 2 is a perspective view showing a part of the load-sensitive continuously variable automatic transmission according to the embodiment of the present invention. The description will be given mainly with reference to FIG.

  The load-sensitive continuously variable automatic transmission includes an input shaft 10, an input disk 11 fixed to the input shaft 10, an output disk 21 that is spaced apart from the input disk 11, and an output disk 21. The output shaft 20 fixed to the input shaft and arranged coaxially with the input shaft is disposed so as to sandwich the input disk 11 and the output disk 21, and rotates from the input disk 11 to the output disk 21 by frictional force. A first power transmission disk 30 and a second power transmission disk 31 for transmission, a holding member 40 for rotatably holding the first power transmission disk 30 and the second power transmission disk 31, and a holding member 40 are provided. Biasing means 50 for biasing.

  One end of the input shaft 10 is connected to a drive source such as a motor (not shown), and the input disk 11 is fixed to the other end of the input shaft 10. The input disk 11 is composed of, for example, a metal disk. The output shaft 20 is disposed coaxially with the input shaft 10, and an output disk 21 is fixed to one end of the output shaft 20. A driven device (not shown) is connected to the other end of the output shaft 20. The output disc 21 is configured by, for example, a metal disc, like the input disc 11. The diameter of the input disk 11 and the diameter of the output disk 21 are equal.

  The first power transmission disk 30 and the second power transmission disk 31 are arranged to face each other so as to sandwich the input disk 11 and the output disk 21. The 1st power transmission disc 30 and the 2nd power transmission disc 31 are constituted by a metal disc, for example. A first rotary shaft 32 is fixed to the first power transmission disc 30, and a second rotary shaft 33 is fixed to the second power transmission disc 31.

  The holding member 40 is made of, for example, a metal plate, and is in contact with the surface of the first power transmission disc 30 opposite to the surface in contact with the input disc 11 and the input disc 11 of the second power transmission disc 31. It is bent along the surface opposite to the surface (that is, the surface of the first power transmission disk 30 and the second power transmission disk 31 that are not opposed to each other) (see FIG. 2). . The first holding surface 41 bent toward the first power transmission disc 30 is provided with a first insertion hole 43, through which the first rotation shaft 32 of the first power transmission disc 30 is inserted and held rotatably. Is done. A second insertion hole 44 is provided in the second holding surface 42 bent to the second power transmission disc 31 side, and the second rotating shaft 33 of the second power transmission disc 31 is inserted and held rotatably. Is done. At this time, in the first power transmission disk 30 and the second power transmission disk 31, the first rotation shaft 32 and the second rotation shaft 33 are arranged coaxially, and the center lines of those axes are the input shaft 10 and the output shaft. It arrange | positions so that 20 centerlines may be crossed.

  The biasing means 50 is, for example, a spring or the like, and one end is attached to the holding member 40. The other end of the urging means 50 is attached to a fixing member 60 such as a housing. The biasing means 50 determines an initial position of the holding member 40 at a balance position by the biasing force, and restricts the movement of the holding member 40 in a direction parallel to the input shaft 10 and the output shaft 20. When the initial position of the holding member 40 is determined, the positions of the first power transmission disk 30 and the second power transmission disk 31 held rotatably with respect to the holding member 40 with respect to the input disk 11 and the output disk 21. Is also determined.

  The operation of the load-sensitive continuously variable automatic transmission having the above configuration will be described below.

  FIG. 3 is an explanatory view showing the transmission of rotation from the input disk 11 to the output disk 21 via the first power transmission disk 30. FIG. 3 is a view from above of FIG. 1, and the input disk 11 and the output disk 21 in the lower direction of FIG. 1 of the first power transmission disk 30 (the direction from the front to the back of FIG. 3). Shows a state where is arranged. FIG. 4 is an explanatory view showing the transmission of rotation from the input disk 11 to the output disk 21 via the second power transmission disk 31. FIG. 4 is a view from above of FIG. 1, and the illustration of the first power transmission disk 30 is omitted for the sake of explanation.

  A process of transmitting rotation from the input shaft 10 to the output shaft 20 will be described. As shown in FIG. 2, when the input shaft 10 is rotated clockwise (in the direction of arrow B in FIGS. 3 and 4) when viewed from the left in FIG. The input disc 11 thus rotated integrally rotates in the same direction (the direction of arrow B in FIGS. 3 and 4). When the input disk 11 rotates, the rotation is transmitted from the input disk 11 to the first power transmission disk 30 by frictional transmission, and the first power transmission disk 30 has the first rotation shaft 32 as the center of rotation. Rotate counterclockwise (in the direction of arrow C in FIG. 3) when viewed from above 2. At the same time, rotation is transmitted from the input disk 11 to the second power transmission disk 31 by frictional force, and the second power transmission disk 31 is viewed from above in FIG. And rotate clockwise (arrow D direction in FIG. 4). The rotation of the first power transmission disk 30 and the second power transmission disk 31 is transmitted to the output disk 21 by frictional force, and the output disk 21 is clockwise when viewed from the right in FIG. 2 (FIGS. 3 and 4). In the direction of arrow E).

  As shown in FIGS. 3 and 4, the torque applied to the input disk 11 from the drive source is transmitted to the output disk 21 via the first power transmission disk 30 and the second power transmission disk 31. At this time, the rotational speed is the distance a from the center of the first power transmission disk 30 to the contact X between the first power transmission disk 30 and the input disk 11 (= the second power transmission disk 31 to the second center). Distance c) between the power transmission disk 31 and the input disk 11 to the contact point M), distance b from the center of the first power transmission disk 30 to the contact point Y between the first power transmission disk 30 and the output disk 21 (= Distance d from the center of the second power transmission disk 31 to the contact point N between the second power transmission disk 31 and the output disk 21).

  The gear ratio accompanying transmission of rotation from the input disk 11 to the output disk 21 is obtained as follows. When the first power transmission disk 30 and the second power transmission disk 31 are rotated once by the input disk 11, the input disk 11 is (2 × π × a / (length of the entire circumference of the input disk 11). )) And the output disc 21 rotates ((2 × π × b / (length of the entire circumference of the output disc 21)). The diameters of the input disc 11 and the output disc 21 are the same, and the input disc 21 is rotated. Since the length of the entire circumference of the disk 11 and the length of the entire circumference of the output disk 21 are equal, when the input disk 11 makes one revolution, ((2 × π × b / (the total circumference of the output disk 21 Length)) / (2 × π × a / (length of the entire circumference of the input disk 11)) = (b / a), and the output disk 21 rotates (b / a). The rotational speed of the output disk 21 is (b / a) times the rotational speed of the input disk 11.

  When the force exerted on the first power transmission disk 30 and the second power transmission disk 31 by the rotation of the input disk 11 is F1, the torque generated in the first power transmission disk 30 and the second power transmission disk 31 is F1 × a. When the force exerted on the output disk by the rotation of the first power transmission disk 30 and the second power transmission disk 31 is F2, the contact X on the first power transmission disk 30 and the second power transmission disk 31 and Since the torque at the contact Y (contact M and contact N) is equal, F1 × a = F2 × b, and F2 = (a / b) × F1. That is, the output disk 21 is subjected to a force a / b times the force generated by the rotation of the input disk 11. If the radius of the input disc 11 is r1, the torque T1 of the input disc 11 is F1 × r1, and if the radius of the output disc 21 is r2, the torque T2 of the output disc 21 is F2 × r2, and the input circle Since the radius r1 of the plate 11 is equal to the radius r2 of the output disc 21, T2 / T1 = (F2 × r2) / (F1 × r1) = (a / b), and the torque of the output disc 21 is the input disc. This is (a / b) times the torque of the plate 11.

  Here, when a load is applied to the output shaft 20, the output disk 21 exerts a frictional force on the first power transmission disk 30 and the second power transmission disk 31. The direction of the frictional force is opposite to the rotational direction of each of the first power transmission disc 30 and the second power transmission disc 31. For the first power transmission disc 30, the direction of the arrow G in FIG. About the power transmission disc 31, it is an arrow H direction of FIG. Due to this frictional force, the first power transmission disc 30 is moved downward (arrow G direction) in FIG. 3, the second power transmission disc 31 is moved upward (arrow H direction) in FIG. The extension lines of the first rotating shaft 32 of the first power transmission disk 30 and the second rotating shaft 33 of the second power transmission disk 31 extend the input shaft 10 and the output shaft 20 as much as the mounting backlash allows. Move to a position that does not intersect the line. Since the first power transmission disk 30 moves downward in FIG. 3, the contact point X with the input disk 11 and the contact point Y with the output disk 21 are above the center of the first rotating shaft 32 in FIG. 3. It becomes. Since the second power transmission disk 31 moves upward in FIG. 4, the contact point M with the input disk 11 and the contact point N with the output disk 21 are below the center of the second rotating shaft 33 in FIG. 4. Become the side.

  FIG. 5 is an explanatory view exaggeratingly showing a state in which the first power transmission disc 30 has moved to a position where the center line of the first rotating shaft 32 does not intersect the center lines of the input shaft 10 and the output shaft 20. FIG. 6 is an explanatory view exaggeratingly showing a state in which the second power transmission disc 31 has moved to a position where the extension line of the second rotating shaft 33 does not intersect the extension lines of the input shaft 10 and the output shaft 20. When a load is applied to the output shaft 20, the first power transmission disk 30 exerts a frictional force in the direction of arrow J in FIG. The component in the direction parallel to the input shaft 10 and the output shaft 20 of the frictional force exerted on the output disc 21 by the first power transmission disc 30 acts to move the output disc 21 leftward in FIG. However, since the output disc 21 and the output shaft 20 cannot move in a direction parallel to the input shaft 10 and the output shaft 20, the reaction force of the force acting on the left side of the output disc 21 in FIG. The transmission disk 30 is operated to move in the right direction in FIG. 5, and the first power transmission disk 30 is moved in the right direction in FIG. 5 with respect to the input disk 11 and the output disk 21. As a result, the distance a from the center of the first power transmission disk 30 to the contact X between the first power transmission disk 30 and the input disk 11 is increased, and the first power transmission from the center of the first power transmission disk 30 is increased. The distance b to the contact point Y between the disc 30 and the output disc 21 is reduced.

  Similarly, when a load is applied to the output shaft 20, the second power transmission disk 31 exerts a frictional force in the direction of arrow K in FIG. 6 on the output disk 21. The component in the direction parallel to the input shaft 10 and the output shaft 20 of the frictional force exerted on the output disc 21 by the second power transmission disc 31 acts to move the output disc 21 leftward in FIG. However, since the output disc 21 and the output shaft 20 cannot move in the direction parallel to the input shaft 10 and the output shaft 20, the reaction force of the force acting on the left side of the output disc 21 in FIG. The power transmission disk 31 is moved to the right in FIG. 6, and the second power transmission disk 31 is moved to the right in FIG. 6 with respect to the input disk 11 and the output disk 21. As a result, the distance c from the center of the second power transmission disk 31 to the contact point M between the second power transmission disk 31 and the input disk 11 is increased, and the second power transmission from the center of the second power transmission disk 31 is increased. The distance d to the contact point N between the disk 31 and the output disk 21 is reduced.

  Since the first power transmission disk 30 and the second power transmission disk 31 are connected by the holding member 40, the distance a after the movement of the first power transmission disk 30 and the second power transmission disk 31 is determined. And distance c, and distance b and distance d are equal. Further, the biasing means 50 attached to the holding member 40 generates a biasing force as the holding member 40 moves together with the first power transmission disk 30 and the second power transmission disk 31.

  Distance a from the center of the first power transmission disk 30 to the contact X between the first power transmission disk 30 and the input disk 11 (= the center of the second power transmission disk 31 to the second power transmission disk 31 The distance c) from the center of the first power transmission disk 30 to the contact point Y between the first power transmission disk 30 and the output disk 21 is increased (the distance c from the center of the first power transmission disk 30). The distance d) from the center of the second power transmission disk 31 to the contact point N between the second power transmission disk 31 and the output disk 21 is reduced, and the rotational speed of the input disk 11 is (b / a) times. Therefore, the rotation of the input disk 11 is transmitted to the output disk 21 after being decelerated more than before the load is applied to the output shaft 20. Therefore, as the first power transmission disk 30 and the second power transmission disk 31 move, the peripheral speed of the output disk 21 and the first contact Y between the first power transmission disk 30 and the output disk 21 are increased. The difference between the peripheral speed on the power transmission disk 30 and the peripheral speed on the second power transmission disk 31 at the contact point N between the second power transmission disk 31 and the output disk 21 is reduced. The peripheral speed of the output disk 21, the peripheral speed of the contact Y between the first power transmission disk 30 and the output disk 21 on the first power transmission disk 30, and the second power transmission disk 31 and the output The input disk 11 and the output disk of the first power transmission disk 30 and the second power transmission disk 31 where the peripheral speed on the second power transmission disk 31 of the contact point N with the disk 21 is balanced. The movement with respect to 21 stops. At this time, as described above, the torque of the output disk 21 is (a / b) times the torque of the input disk 11, and a is large and b is small due to the load applied to the output shaft 20, The torque of the input disk 11 is amplified and transmitted to the output disk 21 more greatly than before.

  When the load applied to the output shaft 20 is reduced, the first power transmission disk 30 and the second power transmission disk 31 are moved by the urging force of the urging means 50 attached to the holding member 40 and the input disk 11 and The output disk 21 moves to the left in FIGS. Therefore, the distance a from the center of the first power transmission disk 30 to the contact X between the first power transmission disk 30 and the input disk 11 (= the center of the second power transmission disk 31 to the second power transmission disk 31) The distance c) from the center of the first power transmission disk 30 to the contact Y between the first power transmission disk 30 and the output disk 21 is shortened. = The distance d) from the center of the second power transmission disk 31 to the contact point N between the second power transmission disk 31 and the output disk 21 is increased, and the rotational speed of the input disk 11 is (b / a ) Is doubled and transmitted to the output disk 21, so that the rotation of the input disk 11 is transmitted to the output disk 21 with a smaller deceleration than before.

  Thus, a load-sensitive continuously variable automatic transmission that can automatically and continuously change gears according to the load applied to the output shaft 20 with a small, light and low-cost configuration is obtained.

  The load-sensitive continuously variable automatic transmission of the present embodiment automatically increases at a low speed when the load is large and rotates reliably at a low speed, and automatically rotates at a high speed at a low speed when the load is small. Therefore, a safe and easy-to-use electric device can be configured.

  The load-sensitive continuously variable automatic transmission according to the present embodiment can be applied to, for example, an electric seat driving device of an automobile. When there is no seated person on the seat, the load is reduced and the reduction ratio is reduced, so that the seat can be moved at a high speed. When there is a seated person on the seat, the load increases and the reduction ratio increases, so that the seat can be moved more safely at a low speed. Moreover, since the reduction ratio increases as the load increases, the torque of the motor used on the input side can be kept small, and the motor can be downsized. Therefore, the weight reduction, size reduction, and power saving of the drive device for the electric seat can be achieved. Further, automatic transmission with a reduction ratio corresponding to the load can be performed without using any other power source or load detector, and the number of parts of the driving device for the electric seat can be reduced, and the size and cost can be reduced.

  FIG. 7 is a perspective view showing a load-sensitive continuously variable automatic transmission in which the first insertion hole 43 of the holding member 40 is longer in the direction perpendicular to the input shaft 10 and parallel to the first power transmission disc 30. . FIG. 8 is a perspective view showing a state in which the load-sensitive continuously variable automatic transmission of FIG. 7 is rotated 180 degrees about an axis substantially perpendicular to the paper surface. In the above embodiment, the first rotating shaft 32 fixed to the first power transmission disc 30 is inserted into the first insertion hole 43 provided in the holding member 40 and is rotatably held, and the second power transmission circle is provided. The plate 31 is inserted into the second insertion hole 44 provided in the holding member 40 and is rotatably held, and receives the frictional force generated by the load applied to the output shaft 20 to receive the first power transmission disc 30 and the second plate 31. The power transmission disc 31 moves as much as the backlash attached to the holding member 40 allows. Here, in a state where the first rotating shaft 32 is inserted into the first insertion hole 43 of the holding member 40, the first play is performed so that a large backlash is generated in a direction perpendicular to the input shaft 10 and parallel to the first power transmission disc 30. When the direction of the insertion hole 43 that is perpendicular to the input shaft 10 and parallel to the first power transmission disk 30 is made longer, the first power transmission disk 30 receives the frictional force generated by the load applied to the output shaft 20. It moves smoothly in a direction perpendicular to the input shaft 10 and parallel to the first power transmission disc 30. Further, the second rotation shaft 33 is inserted into the second insertion hole 44 of the holding member 40, so that a large backlash is generated in a direction perpendicular to the input shaft 10 and parallel to the second power transmission disc 31. When the direction of the insertion hole 44 perpendicular to the input shaft 10 and parallel to the second power transmission disk 31 is made longer, the second power transmission disk 31 receives the frictional force generated by the load applied to the output shaft 20 and the second power transmission disk 31 receives the input. It moves smoothly in a direction perpendicular to the shaft 10 and parallel to the second power transmission disk 31. Therefore, a smoother speed change is possible.

  FIG. 9 is a conceptual diagram showing a load-sensitive continuously variable automatic transmission in which the first power transmission disc 30 includes a first curved portion 34 and the second power transmission disc 31 includes a second curved portion 35. In the above-described embodiment, the first power transmission disc 30 and the second power transmission disc 31 are provided with the biasing means 50 (FIG. 1) such as a spring that biases the holding member 40 that rotatably holds the first power transmission disc 30. The first curved portion 34 is in contact with the input disc 11 and the output disc 21 of the first power transmission disc 30, and the second surface is in contact with the input disc 11 and the output disc 21 of the second power transmission disc 31. The bending portion 35 may be provided as an urging means. Accordingly, the first power transmission disk 30 and the second power transmission disk 31 receive the frictional force generated by the load applied to the output shaft 20, and the left direction in FIG. 9 with respect to the input disk 11 and the output disk 21. 9, the first power transmission disc 30 and the second power transmission disc 31 move the first curved portion 34 and the second curved portion 35 to the input disc 11 in a direction perpendicular to the input shaft 10 (in FIG. Direction) and move while elastically deforming. Therefore, when the load applied to the output shaft 20 is reduced, the first power transmission disc 30 and the second power transmission disc 31 are reduced in elastic force of the first power transmission disc 30 and the second power transmission disc 31. Move in the direction. Therefore, the spring as the urging means and the fixing member 60 for fixing the urging means 50 in FIG. 1 are not required, leading to reduction in the number of parts and miniaturization. The same effect can be obtained by providing one of the first curved portion 34 of the first power transmission disc 30 and the second curved portion 35 of the second power transmission disc 31 and the other being a flat plate.

  In the above embodiment, the rotation direction of the input shaft 20 has been described as the arrow B direction in FIG. 3, but the same effect can be obtained even if the rotation of the input shaft 20 is in the reverse direction.

  In this embodiment, the first insertion hole 43 and the second insertion hole 44 provided in the holding member 40 are used to hold the rotation shafts of the first power transmission disk 30 and the second power transmission disk 31. However, it is not limited to this. The first power transmission disc 30 and the second power transmission disc 31 may be configured to be rotatably held by the holding member 40 via a bearing mechanism such as a bearing. In this case, the bearing mechanism may be fixed to the holding member 40, and slightly slides on the first holding surface 41 and the second holding surface 42 of the holding member 40 in a direction orthogonal to the input shaft 10 and the output shaft 20. It may be installed movably.

DESCRIPTION OF SYMBOLS 10 Input shaft 11 Input disk 20 Output shaft 21 Output disk 30 1st power transmission disk 31 2nd power transmission disk 34 Bending part (1st bending part)
35 bending portion (second bending portion)
40 holding member 50 biasing means

Claims (3)

An input shaft;
An input disk fixed to the input shaft;
An output disc spaced apart from the input disc; and
An output shaft fixed to the output disc and disposed coaxially with the input shaft;
A first power transmission disk and a second power transmission disk, which are arranged so as to sandwich the input disk and the output disk, and transmit rotation from the input disk to the output disk via a frictional force. When,
A holding member for rotatably holding the first power transmission disc and the second power transmission disc;
A load-sensitive continuously variable automatic transmission comprising an urging means for urging the holding member. The holding member holds the first power transmission disc movably in a direction perpendicular to the input shaft and parallel to the first power transmission disc, and the second power transmission disc is perpendicular to the input shaft. The load-sensitive automatic transmission according to claim 1, wherein the load-sensitive automatic transmission is held movably in a direction parallel to the second power transmission disc. 3. The load-sensitive type according to claim 1, wherein the biasing means is a curved portion provided in at least one of the first power transmission disk and the second power transmission disk. Automatic transmission.

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