JP5695504B2 - Damper pulley - Google Patents

Description

  The present invention relates to a damper pulley that absorbs rotational fluctuation between two rotating bodies and enables transmission of rotational torque between the rotating bodies.

  In the rotation transmission part that transmits rotational torque from the crankshaft of an automobile engine to an auxiliary machine such as an alternator via a belt, the rotating body on the input side provided with a pulley and the rotating body on the output side to the auxiliary machine are coaxial. A damper pulley that is arranged so as to be relatively rotatable above and absorbs rotational fluctuations between these two rotating bodies and enables transmission of rotational torque between the rotating bodies is employed.

  In this type of damper pulley, two rotating bodies on the input side and the output side are connected by an elastic body such as rubber or a coil spring, and the relative rotation between the rotating bodies is allowed by using the torsional deformation of the elastic body. In many cases, it is possible to transmit rotational torque between rotating bodies by absorbing rotational fluctuations between bodies (for example, see Patent Documents 1 and 2).

  Also, instead of using the torsional deformation of the elastic body, two annular races facing each other in the axial direction are arranged between the two rotating bodies coaxially arranged inside and outside, and these opposing surfaces are engaged. A first annular race that is integrally rotatable with the outer rotating body and axially displaceable, a spring is disposed on the back side, and the second annular race is rotatable and axially displaceable with respect to the inner rotating body. A friction clutch pressed and connected by the spring between the second annular race and the inner rotating body is disposed, and the engaging portion of the first annular race descends in the spring arranging direction, and the arcuate slope of the first slope The engaging part of the two annular races is an arcuate slope having a rising gradient in the spring arrangement direction, and the relative torque between the rotating bodies is allowed between the engaging parts, and the rotational torque is applied by the friction clutch pressed by the spring. To communicate Pulleys have also been proposed (e.g., see Patent Document 3).

Japanese Utility Model Publication No. 63-68540 Japanese Patent Laid-Open No. 5-180287 JP 2006-38183 A

  The damper pulley that allows the relative rotation between the rotating bodies using the torsional deformation of the elastic body described in Patent Documents 1 and 2 has a durable life due to fatigue of the elastic body such as rubber or coil spring that undergoes repeated torsional deformation. There is a problem that becomes shorter.

  On the other hand, the damper pulley described in Patent Document 3 does not have a decrease in the endurance life due to such fatigue of the elastic body, but in addition to a mechanism that allows relative rotation between the rotating bodies, a friction clutch that transmits rotational torque is provided. Since this is necessary, there is a problem that the configuration becomes complicated.

  Accordingly, an object of the present invention is to provide a damper pulley having a simple configuration and an excellent durability life.

  In order to solve the above-mentioned problem, the present invention is arranged such that two rotating bodies on the input side and the output side are arranged so as to be relatively rotatable on the same axis, a pulley is provided on the rotating body on the input side, and the two rotations An annular ball guide surface formed with a plurality of crests periodically protruding in the axial direction in the rotation direction is provided on either side of the body, and an annular ball guide surface facing the ball guide surface in the axial direction is provided on the other side. A sphere holding surface is provided, and a plurality of spheres are arranged and held in the circumferential direction between the sphere guide surface and the sphere holding surface, and the rotating body on the side provided with the sphere holding surface is arranged in the circumferential direction. Provided is a sphere accommodating portion that accommodates the arranged spheres while restricting movement in the rotation direction, and either one of the sphere guide surface and the sphere holding surface is arranged in the axial direction of the rotator on the side where this surface is provided. Formed in a separate member that can be moved to the side, and the pressure that axially presses this separate member toward the arranged spheres Employing the configuration provided a spring.

  That is, a spherical guide surface is provided on one side of two rotating bodies that are coaxially rotatable relative to each other and formed with a plurality of crests that periodically protrude in the axial direction in the rotational direction, and a spherical guide surface on the other side. A rotating body on the side provided with a ball holding surface provided with a ball holding surface opposed in the axial direction and arranged and held in a circumferential direction between the annular ball guide surface and the ball holding surface A ball housing portion that accommodates the arranged spheres while restricting movement in the rotation direction, and either one of the ball guide surface and the ball holding surface is arranged in the axial direction of the rotating body on the side on which the surface is provided. By providing a compression spring that presses the separate member in the axial direction toward the ball side, a damper pulley having a simple structure and having an excellent durability life can be provided. That is, while transmitting the rotational torque to the ball guide surface provided on one rotating body side and the ball housing portion provided on the other rotating body side through a ball restricted in the rotation direction, the rotating torque is transmitted between the rotating bodies. When rotation fluctuation occurred, the sphere was rolled between the peaks on both sides of the sphere guide surface so that relative rotation between the rotating bodies was allowed.

  The two rotating bodies are arranged inside and outside so that one of them is inserted into the other, and in the annular space formed between the rotating bodies arranged inside and outside these, the spherical guide surface, the sphere, the spherical holding surface, and By arranging the compression spring, the damper pulley can be designed compactly.

  In the axial movement of the moving member in the direction in which the distance between the sphere guide surface and the sphere holding surface increases, the distance between the peak portion of the sphere guide surface and the sphere holding surface is less than the diameter of the sphere. By restricting in such a way, when a large rotation fluctuation that causes the rotation of the input side rotating body to speed up due to overload occurs, the trip over which the ball goes over the mountain is eliminated, and the generation of noise and torque fluctuation due to this trip operation is eliminated. Can be prevented.

Further, according to the present invention, the spherical guide surface is provided on the rotating body on the input side, and the slope on the opposite side to the rotational direction of the peak is a gentle slope than the slope on the rotational direction side . As a result , when a large rotational fluctuation that causes the rotation of the rotating body on the input side to become faster due to overload occurs, even if the ball gets over the mountain, the ball over the mountain goes gently down the gentle slope, Rapid torque fluctuation can be suppressed.

  The region between the adjacent peaks of the spherical guide surface is formed with a curved slope whose inclination angle increases from the deepest valley bottom toward the peaks on both sides, thereby causing rotational fluctuations between the rotating bodies. Sometimes the moving speed of the ball rolling to the mountain side is decelerated as it approaches the mountain, and the ball whose trip over the mountain is restricted can be quietly stopped.

  The curved surface of the slope whose inclination angle increases from the valley bottom between the peaks toward the peaks on both sides can be an elliptical curved surface whose inclination is zero at the valley bottom.

  The elliptical curved surfaces on both sides of the valley bottom are two ellipses having the same minor axis and different major axes, and the spherical guide surface is provided on the rotating body side on the input side. By making the slope an elliptical elliptical curved surface with a large major axis, when a large rotational fluctuation occurs that causes the rotation of the rotating body on the input side to become faster due to overload, the trip until the sphere gets over the mountain is regulated. It is possible to increase the movement distance and tolerate larger rotation fluctuations.

  By providing means for restricting the movement of the spheres arranged in the radial direction between the sphere guide surface and the sphere holding surface, the movement of the arranged spheres in the radial direction can be reliably restricted.

  When the spherical guide surface is formed on the separate member, the separate member may be provided with means for fixing the rotation direction to the rotating body on the side where the spherical guide surface is provided.

  The damper pulley according to the present invention is provided with a spherical guide surface formed with a plurality of crests periodically protruding in the axial direction in the rotational direction on one side of two rotating bodies that are coaxially and relatively rotatable, and on the other side. The ball holding surface that is opposed to the ball guide surface in the axial direction is provided, and a plurality of balls are arranged and held in the circumferential direction between the annular ball guide surface and the ball holding surface to provide a ball holding surface. The rotator on the other side is provided with a sphere accommodating portion that accommodates the arranged spheres while restricting movement in the rotation direction, and either one of the sphere guide surface and the sphere holding surface is disposed on the side on which this surface is provided. Since the rotation direction is fixed to the rotating body and formed as a separate member that can move in the axial direction, a compression spring that presses the separate member in the axial direction to the ball side is provided. An excellent damper pulley can be provided.

Synthetic longitudinal sectional view showing the damper pulley of the first embodiment Sectional view along the line II-II in FIG. External perspective view of the ball guide plate of FIG. FIG. 3 is a developed cross-sectional view of the spherical guide surface of FIG. FIG. 4 is a developed sectional view showing a modification of the spherical guide surface of FIG. Partially omitted vertical sectional view showing the damper pulley of the second embodiment Sectional drawing along the VII-VII line of FIG. 6 is a developed sectional view of the spherical guide surface of FIG. Partially omitted longitudinal sectional view showing a damper pulley of a third embodiment 9 is a developed sectional view of the spherical guide surface of FIG. The graph which shows the relationship between the torsion angle between rotary bodies in the damper pulley of FIG. 9, and the contact angle with the ball | bowl guide surface of a ball | bowl. Partially omitted longitudinal sectional view showing a damper pulley of a fourth embodiment FIG. 12 is a developed sectional view of the spherical guide surface of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. 1 to 5 show a first embodiment. As shown in FIG. 1, this damper pulley is on the input side where the pulley 1 is provided, on the inner diameter side of the cylindrical first rotating body 2 having a pulley groove on the outer peripheral portion into which the rib portion of the V-ribbed belt is fitted. The second rotating body 3 on the output side is fitted on the same axis, and is supported by the rolling bearing 4 so as to be rotatable relative to the first rotating body 2. The inner surface of the first rotating body 2 is provided with an inward flange portion 2 a that partitions one end side of the annular space 5 between the first rotating body 2 and the second rotating body 3. An annular casing 6 having a U-shaped cross-section for partitioning the other end side of the annular space 5 is attached to the radial surface. In the vertical cross-sectional view of FIG. 1, for convenience, the steady rotation state is displayed on the upper half, and an overload state in which rotational fluctuation that will be described later increases is displayed on the lower half.

  The casing 6 is supported by a sliding bearing 7 a mounted on the inner diameter surface of the first rotating body 2, and is axially positioned by tightening a nut 8 screwed onto the outer diameter surface of the second rotating body 3. The The rolling bearing 4 is positioned in the axial direction by the flange portion 2 a of the first rotating body 2 and the large-diameter step portion 3 a of the second rotating body 3.

  In the annular space 5 partitioned by the flange portion 2a of the first rotating body 2 and the casing 6, an annular ball guide plate 9, a plurality of balls 10, and an annular ball, which will be described later, from the flange portion 2a side to the casing 6 side. The holding plate 11 and the compression coil spring 12 are arranged in order. The ball guide plate 9 is fixed to the flange portion 2a with bolts 13. The spherical guide plate 9 can be divided in the circumferential direction, and can be formed integrally with the flange portion 2a.

  The ball holding plate 11 is movable in the axial direction of the second rotating body 3 via the slide bearing 7b, and is pressed toward the ball 10 by the compression coil spring 12 via the thrust bearing 14. The pressing force of the compression coil spring 12 is adjusted by the tightening position of the nut 8. The compression coil spring 12 may be another compression spring such as a plate spring or a disc spring. Further, the thrust bearing 14 can be omitted.

  Each of the slide bearings 7a and 7b is formed of a metal material such as brass or bronze or a synthetic resin material such as nylon, polytetrafluoroethylene, or high molecular weight polyethylene. A solid lubricant such as molybdenum disulfide, tungsten disulfide, graphite, or boron nitride can be applied to the surface of these materials. Further, the solid lubricant can be dispersed in the synthetic resin material. In the case of forming with a metal material, the surface can be plated with good lubricity.

  As shown in FIG. 2, the large-diameter step portion 3 a of the second rotating body 3 is provided with a plurality of concave ball housing portions 15 at equal intervals in the rotation direction. 10 is accommodated so that movement in the rotational direction is restricted. In this embodiment, the ball accommodating portions 15 are provided at five locations in the rotation direction, and the five balls 10 are arranged in the rotation direction. The number of the ball housing portions 15 and the balls 10 may be two or more, and preferably three or more.

  As shown in FIGS. 1 and 2, the spheres 10 accommodated in the respective sphere accommodating portions 15 are moved outward in the radial direction by the annular portions 11 a protruding in the axial direction on the outer periphery of the sphere holding plate 11. It is held between the ball guide plates 9 so as to be regulated. Since the ball 10 is restrained from moving in the radial direction by the pressing force of the compression coil spring 12, the annular portion 11a can be omitted. Therefore, in this embodiment, the rotational torque input from the pulley 1 to the first rotator 2 includes the sphere guide plate 9 whose rotational direction is fixed to the first rotator 2 and the sphere housing portion of the second rotator 3. 15 is transmitted to the second rotating body 3 on the output side via the ball 10 whose movement in the rotational direction is restricted by 15.

  As shown in FIG. 3, the ball guide plate 9 is formed with a plurality of peaks 16 a that periodically protrude in the axial direction in the rotational direction on the surface of the ball holding plate 11 that faces the ball holding surface 17 in the axial direction. A spherical guide surface 16 is provided. In this embodiment, the mountain parts 16a are formed at five places in the rotation direction. Since each ball 10 accommodated and arranged in the ball housing portion 15 is pressed against the ball guide surface 16 by the compression coil spring 12 via the ball holding plate 11, in the steady rotation state, the middle of each mountain portion 16a. It is located at the deepest valley bottom 16b.

  As shown in FIG. 4, the height H of the crest 16a of the spherical guide surface 16 is 2 to 5 mm, and with respect to the rotation direction of the first rotating body 2 and the second rotating body 3 indicated by arrows in the drawing. The slope 16c on the rotation direction side of the mountain portion 16a and the slope 16d on the opposite side are inclined surfaces symmetrical to the mountain portion 16a. The ball 10 located at the valley bottom 16b in the steady rotation state causes the slopes 16c and 16d on either side of the sphere 10 against the pressing force of the compression coil spring 12 when the rotational fluctuation occurs between the rotating bodies 2 and 3. It rolls so as to allow the relative rotation between the rotating bodies 2 and 3, and when a large rotational fluctuation occurs due to overload, it overcomes the peak 16a and absorbs the overload. The height H of the peak portion 16a is set to 2 to 5 mm. If the height H of the peak portion 16a is less than 2 mm, the ability to absorb overload is insufficient, and if it exceeds 5 mm, the overload is absorbed. This is because the compression displacement of the compression coil spring 12 increases and the durability life of the compression coil spring 12 decreases.

  FIG. 5 shows a modification of the spherical guide surface 16. In this modification, the slope 16d on the opposite side to the rotational direction of the mountain portion 16a with respect to the rotational direction of the first rotary body 2 and the second rotary body 3 indicated by arrows in the drawing is more than the slope 16c on the rotational direction side. It is also a gentle slope. Therefore, when the rotation of the ball guide plate 9 fixed to the first rotator 2 becomes faster due to a large rotation fluctuation that causes the rotation of the first rotator 2 on the input side to become faster due to overload, Since the sphere 10 that has climbed over the mountain portion 16a from the slope 16c gently descends the slope 16d on the opposite side to the rotation direction, which is a gentle slope, rapid torque fluctuations can be suppressed.

  6 to 8 show a second embodiment. In the same manner as in the first embodiment, the damper pulley is configured such that the output-side second rotary body 3 is coaxially fitted on the inner diameter side of the input-side first rotary body 2 provided with the pulley 1, and a rolling bearing is provided. 4 is supported so as to be rotatable relative to the first rotating body 2, and as shown in FIG. 6, the annular sphere holding surface 17 is provided on the first rotating body 2 side and faces this in the axial direction. An annular ball guide surface 16 is formed on a ball guide plate 9 which is a separate member movable in the axial direction of the second rotating body 3, and the ball guide plate 9 is pressed toward the ball 10 by the compression coil spring 12. And the spheres 10 arranged between the sphere guide surface 16 and the sphere holding surface 17 are restricted from moving in the rotational direction by the sphere accommodating portions 15 provided in the first rotating body 2. It is different from the housed point. The other parts are the same as those in the first embodiment, and the ball accommodating portions 15 are provided at five locations in the rotation direction, and the five balls 10 are arranged in the rotation direction.

  The spherical guide plate 9 is pressed on the back side by a compression coil spring 12 via an annular backup member 18, and the backup member 18 can be slid in the axial direction by a spline 19 on the outer diameter surface of the second rotating body 3. The rotation direction is fixed to the second rotating body 3.

  As shown in FIGS. 6 and 7, the ball holding surface 17 is provided on the side surface of the inward flange portion 2a of the first rotating body 2, and the annular portion 2b projecting in the axial direction on the inner periphery of the flange portion 2a. A plurality of concave sphere accommodating portions 15 for accommodating the respective spheres 10 are provided on the outer diameter surface. Therefore, in this embodiment, the rotational torque input to the first rotating body 2 from the pulley 1 is controlled by the ball accommodating portion 15 of the first rotating body 2 in the rotational direction and the second rotating body. 3 is transmitted to the second rotating body 3 on the output side via a ball guide plate 9 whose rotational direction is fixed to 3.

  FIG. 8 shows the sphere guide surface 16 of the sphere guide plate 9. The spherical guide surface 16 has an inclined surface 16c on the rotational direction side of the mountain portion 16a with respect to the rotational direction of the first rotating body 2 and the second rotating body 3 indicated by arrows in the drawing. The slope is gentler than 16d. Therefore, when a large rotational fluctuation occurs in which the rotation of the first rotating body 2 on the input side becomes faster due to an overload, the ball 10 that has climbed over the mountain portion 16a from the slope 16d on the opposite side to the rotational direction is turned into a gentle slope. Since the slope 16c on the direction side is gently lowered, sudden torque fluctuations can be suppressed.

  9 to 11 show a third embodiment. As shown in FIG. 9, this damper pulley is coaxial with the output-side second rotating body 3 on the inner diameter side of the input-side first rotating body 2 provided with the pulley 1, as in the first embodiment. An annular ball guide plate 9 having a ball guide surface 16 provided on the first rotating body 2 side, which is inserted above and supported by the rolling bearing 4 so as to be rotatable relative to the first rotating body 2, is provided on the first rotating body 2 side. An annular sphere holding surface 17 facing in the direction is formed on a sphere holding plate 11 which is a separate member movable in the axial direction of the second rotating body 3, and the sphere holding plate 11 is compressed via a thrust bearing 14 to a compression coil. The spring 12 is pressed toward the sphere 10, and the sphere holding plate 11 is provided with a rearward annular portion 11 b that abuts the outer cylinder portion 6 a of the casing 6 and restricts the backward movement thereof. As will be described later, the shape of the spherical guide surface 16 is different. The other parts are the same as those in the first embodiment, and although not shown, the ball accommodating portions 15 are provided at five locations in the rotation direction, and the five balls 10 are arranged in the rotation direction. The vertical cross-sectional view of FIG. 9 combines and displays the steady rotation state in the upper half and the overload state in which the rotation fluctuation described later increases in the lower half, as in FIG.

  As shown in FIG. 10, in the spherical guide surface 16, the height H of each peak 16a is 2 to 5 mm, and the region between the adjacent peaks 16a extends from the deepest valley bottom 16b to the peaks 16a on both sides. It is formed by slopes 16c and 16d whose inclination angle increases toward. The inclined surfaces 16c and 16d are elliptical curved surfaces of two ellipses 20a and 20b having the same minor axis and different major axes, and the rotational directions of the first rotating body 2 and the second rotating body 3 indicated by arrows in the figure. Thus, the slope 16c opposite to the rotation direction from the valley bottom 16b is an elliptical curved surface of an ellipse 20a having a large major axis, and the slope 16d on the rotational direction side is an elliptical curved surface of an ellipse 20b having a small major axis.

  The ball 10 located at the valley bottom 16b in the steady rotation state causes the slopes 16c and 16d on either side of the sphere 10 against the pressing force of the compression coil spring 12 when the rotational fluctuation occurs between the rotating bodies 2 and 3. It rolls so that it may climb, and the relative rotation between the rotary bodies 2 and 3 is permitted. In this embodiment, when the annular portion 11 b of the sphere holding plate 11 abuts on the outer cylinder portion 6 a of the casing 6, the distance between the peak portion 16 a and the sphere holding surface 17 is set slightly smaller than the diameter of the sphere 10. Thus, the trip of the ball 10 over the mountain portion 16a is eliminated. Therefore, generation of noise and torque fluctuation due to the trip operation are prevented.

  The graph of FIG. 11 shows the relationship between the relative rotation angle θ between the rotating bodies 2 and 3 and the contact angle α (the inclination angle of the perpendiculars of the slopes 16c and 16d) with the slopes 16c and 16d of the ball 10. Show. In a steady rotation state where there is no relative rotation angle θ, the ball 10 is located at the valley bottom portion 16b, and the contact angle α is zero. On the positive load side where the rotation of the first rotating body 2 is accelerated, the ball 10 moves to the long slope 16c side, and the contact angle α gradually increases as the relative rotation angle θ increases, As the rolling speed approaches the peak 16a, the rolling speed is reduced, and when the ball holding surface 17 restricts the climbing of the peak 16a, the rolling speed is gently stopped. Further, on the negative load side where the rotation of the first rotating body 2 is decelerated, the ball 10 moves to the short slope 16d side, and the contact angle α increases rapidly as the relative rotation angle θ decreases to the negative side. It is decelerated as it approaches the opposite peak 16a.

  In this embodiment, assuming that a damper pulley is used for a rotation transmission portion from the crankshaft of the engine to the alternator, the short radius of each of the ellipses 20a and 20b is 4 mm, the long radius of the ellipse 20a is 18.5 mm, and the ellipse 20b. The major radius is 6 mm, and the ball 10 is designed to have a relative rotation angle θ of 50 ° and a contact angle α of 35 ° when the ball 10 climbs up the slope 16c. That is, the maximum transmission torque when the contact angle α is 35 ° on the plus load side is 15 Nm, and the contact angle shown in the graph is given in order to have an average damper characteristic of 0.3 Nm / deg from the engine characteristics. The slope 16c on the plus load side is an elliptic curved surface of the ellipse 20a having the above dimensions so that the relative rotation angle θ becomes 50 ° when α is 35 °, and the slope 16d on the minus load side in the remaining region. Is an elliptical curved surface of the ellipse 20b having the above dimensions.

  12 and 13 show a fourth embodiment. As shown in FIG. 12, this damper pulley is coaxial with the output-side second rotating body 3 on the inner diameter side of the input-side first rotating body 2 provided with the pulley 1, as in the second embodiment. An annular sphere that is inserted above and supported by the rolling bearing 4 so as to be rotatable relative to the first rotator 2, and the annular sphere holding surface 17 is provided on the first rotator 2 side, and is opposed to this in the axial direction. The guide surface 16 is formed on a spherical guide plate 9 that is a separate member that can move in the axial direction of the second rotating body 3, and the spherical guide plate 9 is moved by the compression coil spring 12 through the annular backup member 18 and the ball 10. The backup member 18 is provided with a rearward annular portion 18a that comes into contact with the outer cylinder portion 6a of the casing 6 and restricts the backward movement thereof, as will be described later. The shape of the spherical guide surface 16 is different. The other parts are the same as those of the second embodiment, and although not shown, the ball accommodating portions 15 are provided at five locations in the rotation direction, and the five balls 10 are arranged in the rotation direction.

  As shown in FIG. 13, the ball guide surface 16 has a height H of 2 to 5 mm for each peak 16a, and the region between adjacent peaks 16a extends from the deepest valley bottom 16b to the peaks 16a on both sides. It is formed by slopes 16c and 16d whose inclination angle increases toward. The inclined surfaces 16c and 16d are elliptical curved surfaces of two ellipses 20a and 20b having the same minor axis and different major axes, and the rotational directions of the first rotating body 2 and the second rotating body 3 indicated by arrows in the figure. Thus, the slope 16c opposite to the rotation direction from the valley bottom 16b is an elliptical curved surface of an ellipse 20b having a small major axis, and the slope 16d on the rotational direction side is an elliptical curved surface of an ellipse 20a having a large major axis.

  The ball 10 located at the valley bottom 16b in the steady rotation state causes the slopes 16c and 16d on either side of the sphere 10 against the pressing force of the compression coil spring 12 when the rotational fluctuation occurs between the rotating bodies 2 and 3. It rolls so that it may climb, and the relative rotation between the rotary bodies 2 and 3 is permitted. In this embodiment, when the annular portion 18 a of the backup member 18 abuts on the outer cylinder portion 6 a of the casing 6, the distance between the peak portion 16 a and the sphere holding surface 17 is set to be slightly smaller than the diameter of the sphere 10. The ball 10 is prevented from tripping over the mountain 16a. Therefore, similar to the third embodiment, the generation of noise and torque fluctuation due to the trip operation are prevented.

  Similarly to the graph shown in FIG. 11, on the plus load side where the rotation of the first rotating body 2 is accelerated, the ball 10 moves to the long slope 16d side, and as the contact angle α increases, As the rolling speed of the ball 10 approaches the peak portion 16a, the ball 10 is decelerated. When the ball holding surface 17 restricts the climbing of the peak portion 16a, the ball 10 gently stops. On the negative load side where the rotation of the first rotating body 2 is decelerated, the ball 10 moves to the short slope 16c side, and the contact angle α suddenly increases as the relative rotational angle θ decreases to the negative side, The closer to the opposite peak 16a, the slower the speed.

  In each of the above-described embodiments, the output-side rotator is inserted into the inner diameter side of the input-side rotator provided with the pulley, but the input-side rotator is inserted into the inner diameter side of the output-side rotator. A pulley can also be provided in the extension part to an axial direction. Also, the rotating body on the input side and the rotating body on the output side are opposed to each other in the axial direction, and the spherical guide plate, the sphere, the spherical holding plate, and the compression spring are sequentially arranged in the above-described configuration on the axial facing portions. You can also.

DESCRIPTION OF SYMBOLS 1 Pulley 2 1st rotary body 2a collar part 2b annular part 3 2nd rotary body 3a large diameter step part 4 rolling bearing 5 annular space 6 casing 6a outer cylinder part 7a, 7b slide bearing 8 nut 9 ball guide plate 10 ball 11 ball Holding plate 11a, 11b Annular portion 12 Compression coil spring 13 Bolt 14 Thrust bearing 15 Sphere receiving portion 16 Sphere guide surface 16a Mountain portion 16b Valley bottom portion 16c, 16d Slope 17 Sphere holding surface 18 Backup member 18a Annular portion 19 Spline 20a, 20b Ellipse

Claims (8)

The two rotating bodies on the input side and the output side are coaxially arranged so as to be rotatable relative to each other, a pulley is provided on the rotating body on the input side, and one of the two rotating bodies is periodically arranged in the rotation direction. An annular sphere guide surface formed with a plurality of peaks protruding in the axial direction is provided on the other side, and an annular sphere holding surface facing the sphere guide surface in the axial direction is provided on the other side. A plurality of spheres are arranged and held in the circumferential direction between the sphere holding surface, and the movement of the sphere arranged in the circumferential direction is restricted to the rotating body provided with the sphere holding surface. A sphere accommodating portion is provided, and one of the sphere guide surface and the sphere holding surface is formed as a separate moving member movable in the axial direction of the rotating body on the side where the surface is provided; And providing a compression spring that axially presses the separate member toward the arranged spheres ,
A damper pulley in which the spherical guide surface is provided on the rotating body side on the input side, and the slope on the opposite side to the rotational direction of the mountain portion is a gentle slope than the slope on the rotational direction side .   The two rotating bodies are arranged inside and outside so that one of them is inserted into the other, and in the annular space formed between the rotating bodies arranged inside and outside these, the spherical guide surface, the sphere, the spherical holding surface, and The damper pulley of Claim 1 which has arrange | positioned the compression spring.   In the axial movement of the moving member in the direction in which the distance between the sphere guide surface and the sphere holding surface increases, the distance between the peak portion of the sphere guide surface and the sphere holding surface is less than the diameter of the sphere. The damper pulley according to claim 1 or 2 regulated as described above.   The damper pulley according to claim 3, wherein a region between adjacent ridges of the spherical guide surface is formed by a curved slope whose inclination angle increases from the deepest valley bottom toward the ridges on both sides. 5. The damper pulley according to claim 4 , wherein a curved surface of an inclined surface whose inclination angle increases from a valley bottom portion between the mountain portions toward a mountain portion on both sides is an elliptical curved surface whose inclination is zero at the valley bottom portion. The elliptical curved surfaces on both sides of the valley bottom are two ellipses having the same minor axis and different major axes, and the spherical guide surface is provided on the rotating body side on the input side. The damper pulley according to claim 5 , wherein the inclined surface is an elliptical elliptical curved surface having a large major axis. The damper pulley according to any one of claims 1 to 6 , further comprising means for restricting movement in a radial direction of a sphere arranged between the sphere guide surface and the sphere holding surface. The said spherical guide surface is formed in the said separate member, The means which fixes a rotation direction to the rotary body by which this separate member is provided in the said spherical guide surface is provided in any one of Claim 1 thru | or 7. Damper pulley.

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