JP2016008652A - Planetary roller traction drive device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a planetary roller traction drive device capable of suppressing irregularities in a pressing force caused by roller machining errors or the like and improving transfer efficiency.SOLUTION: A planetary roller traction drive device comprises: a housing 10; an input shaft 20; a first ring roller 50 and a second ring roller 60; a plurality of rotation rollers 70 inscribed in the first ring roller 50; a plurality of planetary rollers 80 revolving about the input shaft 20 while being inscribed in the second ring roller 60 and rotating; a carrier 90 provided on the other side of the planetary rollers 80, supporting the planetary rollers 80 so that the planetary rollers 80 can rotate and revolve about the input shaft 20, and outputting revolution components of the planetary rollers 80 to outside; and relative movement mechanisms 3, 4 permitting one of the first ring roller 50 and the second ring roller 60 to move relatively to the other ring roller on a plane orthogonal to an axial direction of the input shaft 20 while rotation is transferred between the first ring roller 50 and the second ring roller 60 when the first ring roller 50 rotates in an opposite direction to a rotation direction of the input shaft 20.

Description

  The present invention relates to a planetary roller traction drive device in which a planetary roller is sandwiched between an input shaft and a ring roller.

  Conventionally, for example, a planetary roller traction drive device as described in Patent Document 1 is known. This planetary roller type traction drive device incorporates a rotating roller and a planetary roller that are in contact with both via an oil film between an input shaft and a ring roller. When the input shaft rotates, the revolution of the planetary roller is transmitted to the output shaft through the carrier while rotating the ring roller in the reverse direction by the rotation of the rotating roller.

JP 2013-217659 A

  By the way, in the planetary roller type traction drive device, when the input shaft is rotated, for example, due to backlash such as a processing error at the time of manufacturing each roller or a deviation of the shaft center at the time of roller assembly, the contact portion through the oil film between the rollers There was a variation in that the applied pressing force was excessive on the one hand and too small on the other. As a result, there was a problem that torque transmission was hindered due to an inability to obtain an appropriate pressing force, resulting in a decrease in transmission efficiency.

  The present invention was created in view of the above points, and an object of the present invention is to provide a planetary roller type traction drive device that suppresses variations in pressing force caused by a processing error of a roller and improves transmission efficiency. There is to do.

  The planetary roller traction drive device of the present invention includes a housing, an input shaft, a first ring roller, a second ring roller, a plurality of rotation rollers, a plurality of planetary rollers, a carrier, and a relative movement mechanism.

  The input shaft is rotatably supported by the housing. The first ring roller is an annular member that is provided on the radially outer side of the input shaft and provided on one side of the housing, and is rotatably supported by the housing.

  The second ring roller is an annular member that is provided on the outer side in the radial direction of the input shaft and provided in parallel with the first ring roller on the other side in the housing, and is rotatably supported by the housing.

  The rotation roller is inscribed in the first ring roller, and is rotated by being constrained to revolve around the input shaft between the input shaft and the first ring roller when the input shaft rotates. The planetary roller revolves around the input shaft while rotating in contact with the second ring roller. The carrier is provided on the other side of the planetary roller, supports the planetary roller so that it can rotate and revolves around the input shaft, and outputs the revolution component of the planetary roller to the outside.

  When the first ring roller rotates in the direction opposite to the rotation direction of the input shaft due to the rotation of the rotation roller, the relative movement mechanism transmits the rotation between the first ring roller and the second ring roller while rotating the one ring. The roller is allowed to move relative to the other ring roller on a plane perpendicular to the axial direction of the input shaft.

  In this configuration, the first ring roller that circumscribes the rotation roller and the second ring roller that circumscribes the planetary roller are individually provided, and during rotation, the rotation of the input shaft is transmitted while the rotation is transmitted between the ring rollers by the relative movement mechanism. Each ring roller can move relatively on a plane orthogonal to the direction.

  If the ring roller that circumscribes the rotating roller and the ring roller that circumscribes the planetary roller are configured so as to be immovable with respect to the housing as a common rigid body, for example, when machining errors or assembly of the rollers When there is a backlash such as a shift of the shaft center, there is a variation that the pressing force of each traction contact portion (the outer peripheral surface of the rotating roller and the planetary roller) is increased on the one hand and lowered on the other hand.

However, in this configuration, since the relative movement of the ring rollers is allowed by the relative movement mechanism, each ring roller is rotated on the plane orthogonal to the axial direction of the input shaft, that is, mainly in the radial direction and the rotation direction of the ring roller. The ring roller automatically moves to a suitable position. Thereby, each dimension error can be suitably absorbed by the autorotation roller side and the planetary roller side. In addition, variations in the pressing force such that the pressing force is increased on one side of each traction contact portion and the pressing force on the other side are reduced, and transmission efficiency is improved without excessively increasing the pressing force and preventing torque transmission. Can be improved. Further, since the wear of each traction contact portion is reduced, the life of each roller can be extended.
Here, in the present invention, “circumscribed” and “inscribed” mean a state in which an oil film is interposed so as to be able to transmit rotation.

The cut part end elevation which shows typically the whole planetary roller type traction drive device by a 1st embodiment of the present invention. The II-II line | wire cutting part end elevation of FIG. It is a figure corresponding to the II-II line cutting part end view of Drawing 1, and is a figure showing one mode at the time of rotation. It is a figure corresponding to the II-II line cutting part end view of Drawing 1, and is a figure showing one mode at the time of rotation. The perspective view of a 1st ring roller. The perspective view of a 2nd ring roller. The cut part end elevation which shows typically the whole planetary roller type traction drive device by a 2nd embodiment of the present invention. The VIII-VIII line | wire cutting part end elevation of FIG. The cut part end view which shows typically the whole planetary roller type traction drive device by other embodiment of this invention.

<First Embodiment>
[Constitution]
A first embodiment of the present invention will be described with reference to FIGS. As shown in FIG. 1, the planetary roller traction drive device 101 of this embodiment includes a housing 10, an input shaft 20 that is rotatably supported by the housing 10, and an input shaft 20 that is integrally formed with the outer periphery of the input shaft 20. First sun roller 30 and second sun roller 40 provided, first ring roller 50 provided radially outside first sun roller 30, and second ring roller 60 provided radially outside second sun roller 40. .

  Further, the planetary roller traction drive device 101 is inscribed in the first ring roller 50 and circumscribed to the first sun roller 30, and inscribed in the second ring roller 60 and circumscribed in the second sun roller 40. It has a plurality of planetary rollers 80 and a carrier 90 that supports the planetary rollers 80 so as to rotate and revolve.

  The central axes L of the sun rollers 30 and 40, the ring rollers 50 and 60, and the carrier 90 substantially coincide with each other. The rotation center axis when the rotation roller 70 and the planetary roller 80 rotate is substantially parallel to the center axis L of the sun roller. The plurality of rotation rollers 70 and the planetary rollers 80 are arranged at substantially equal intervals with respect to the circumferential direction of the sun rollers 30 and 40.

  The first sun roller 30, the rotation roller 70, and the first ring roller 50 constitute the reversing mechanism 1, and the second sun roller 40, the planetary roller 80, and the second ring roller 60 constitute the planetary mechanism 2. The reversing mechanism 1 and the planetary mechanism 2 are disposed to face each other with an interval in the axial direction, and the reversing mechanism 1 is disposed on one side (left side shown in FIG. 1) of the planetary mechanism 2. Further, the first ring roller 50 and the second ring roller 60 are connected by relative movement mechanisms 3 and 4 that allow relative movement of the ring rollers 50 and 60 while transmitting power.

  The input shaft 20 is connected to, for example, a motor (not shown) and is driven to rotate. A part of the input shaft 20 and the rollers 30, 40, 50, 60, 70, 80 are accommodated in the housing 10. Hereinafter, each member will be described in detail.

  The first sun roller 30 has a truncated cone shape, and its outer peripheral surface is formed in a tapered shape in which the outer diameter gradually decreases from one side in the axial direction to the other side (left side to right side in FIG. 1). The rotation roller 70 has a truncated cone shape, and its outer peripheral surface is formed in a tapered shape in which the outer diameter gradually increases from one side to the other side in the axial direction. The taper angles of the tapered shape of the first sun roller 30 and the respective rotation rollers 70 are substantially equal.

  A rotation roller support shaft 71 is press-fitted into the rotation roller 70, and the protruding one side end portion of the rotation roller support shaft 71 is supported by the housing 10 via the bearing 11. The projecting one end of the support shaft 71 for the rotation roller is press-fitted into the inner ring of the bearing 11, and the rotation roller 70 can rotate in a state in which the revolution around the input shaft 20 is restricted. Further, the other end portion of the bearing 11 is engaged with a step portion of the housing 10, and when the rotating roller 70 receives an axial force during rotation, the rotating roller 70 falls off the housing 10 together with the bearing 11. Is preventing. Further, the outer ring of the bearing 11 is coupled to the housing 10 by a clearance fit, and the rotation roller 70 is slightly movable relative to the housing 10 in the radial direction.

  The first ring roller 50 has an annular shape, and an inner peripheral surface thereof is formed in a tapered shape in which the inner diameter gradually increases from one side to the other side in the axial direction. The outer peripheral surface of the first ring roller 50 is formed substantially parallel to the central axis L. A bearing 12 is provided on the outer peripheral surface of the first ring roller 50, and the first ring roller 50 is rotatably supported by the housing 10 via the bearing 12. Further, the inner ring of the bearing 12 is coupled to the first ring roller 50 with a gap fit, and the first ring roller 50 is slightly moved in the radial direction with respect to the housing 10 on a plane orthogonal to the axial direction. Relative movement is possible.

  When the input shaft 20 rotates, traction is generated on the outer peripheral surface of the first sun roller 30 and the outer peripheral surface of the rotation roller 70, and on the inner peripheral surface of the first ring roller 50 and the outer peripheral surface of the rotation roller 70. . The structure of the opposed end surface 54 (see FIG. 5) which is the other end surface of the first ring roller 50 facing the second ring roller 60 will be described later as relative movement mechanisms 3 and 4.

  The second sun roller 40 has a truncated cone shape, and its outer peripheral surface is formed in a tapered shape in which the outer diameter gradually increases from one side to the other side in the axial direction. The planetary roller 80 has a truncated cone shape, and its outer peripheral surface is formed in a tapered shape in which the outer diameter gradually decreases from one side to the other side in the axial direction. The taper angles of the tapered shape of the second sun roller 40 and each planetary roller 80 are substantially equal. A planetary roller support shaft 81 is press-fitted into the planetary roller 80, and the other end of the planetary roller support shaft 81 protrudes toward the carrier 90.

  The second ring roller 60 has an annular shape, and an inner peripheral surface thereof is formed in a tapered shape in which the inner diameter gradually decreases from one side to the other side in the axial direction. The outer peripheral surface of the second ring roller 60 is formed substantially parallel to the central axis L. A bearing 13 is provided on the outer peripheral surface of the second ring roller 60, and the second ring roller 60 is rotatably supported by the housing 10 via the bearing 13. The inner ring of the bearing 13 is coupled to the second ring roller 60 by a clearance fit, and the second ring roller 60 is slightly moved in the radial direction with respect to the housing 10 on a plane orthogonal to the axial direction. Relative movement is possible.

  When the input shaft 20 rotates, traction is generated on the outer peripheral surface of the second sun roller 40 and the outer peripheral surface of the planetary roller 80, the inner peripheral surface of the second ring roller 60, and the outer peripheral surface of the planetary roller 80. . In addition, the structure of the opposing end surface 64 (see FIG. 6) that is the one end surface facing the first ring roller 50 in the second ring roller 60 will be described later as the relative movement mechanisms 3 and 4.

  The carrier 90 is disposed on the other side of the planetary roller 80 and includes an output shaft 91 and a flange portion 92. The other end of the protruding planetary roller support shaft 81 is supported by the flange portion 92 via the bearing 14. The projecting other end of the planetary roller support shaft 81 is press-fitted into the inner ring of the bearing 14, and the carrier 90 supports the planetary roller 80 in a rotatable manner and supports the planetary roller 80 in a revolving manner around the input shaft 20. ing. Thereby, the revolution component of the planetary roller 80 is output to the output shaft. Further, one end of the bearing 14 is engaged with a stepped portion of the flange 92, and when the planetary roller 80 receives an axial force during rotation, the planetary roller 80 falls off the carrier 90 together with the bearing 14. To prevent that. Further, the outer ring of the bearing 14 is coupled to the flange portion 92 by a clearance fit, and the planetary roller 80 is slightly movable relative to the housing 10 in the radial direction.

  Here, as described above, each of the ring rollers 50, 60, the rotation roller 70, and the planetary roller 80 can be slightly moved relative to the housing 10 in the radial direction. "Means about several tens of micrometers, for example. Further, a plurality of springs 15 and 16 are provided between one end face of the first ring roller 50 and the housing 10 and between the other end face of the second ring roller 60 and the housing 10. 50 and 60 are urged in a direction approaching each other.

  Next, the relative movement mechanisms 3 and 4 which are the principal part of this embodiment are demonstrated with reference to FIGS. FIG. 2 is an end view taken along the line II-II in FIG. 1 and shows only the first ring roller 50 and the second ring roller 60. As shown in FIGS. 2 and 5, the first ring roller 50 has a first step portion 51 and a second step in order on the other end surface facing the second ring roller 60 in the circumferential direction around the left as shown in FIG. 2. The portion 52 and the third step portion 53 are formed so as to protrude toward the second ring roller 60 at substantially equal intervals in the circumferential direction. Each step 51, 52, 53 is part of a cylinder with a central angle of about 60 degrees. By forming each step 51, 52, 53, the second ring roller 60 of the first ring roller 50 is formed. The opposing end face 54 that faces is formed in an uneven shape along the circumferential direction.

  Furthermore, a first convex portion 55 is formed so as to protrude in the axial direction of the first step portion 51 at a substantially central portion in the radial direction of the side surface in the circumferential direction of the second step portion 52 of the first step portion 51. Yes. The protruding tip of the first convex portion 55 is formed as a convex curved surface. A first concave portion 56 having a concave curved surface is formed so as to be recessed in the axial direction of the third step portion 53 at a substantially central portion in the radial direction of the side surface in the circumferential direction of the second step portion 52 of the third step portion 53. ing. The first convex portion 55 and the first concave portion 56 are formed at positions that are symmetric with respect to the axis of the first ring roller 50.

  As shown in FIGS. 2 and 6, the fourth step portion 61 and the fifth step portion 61 are arranged in order in the counterclockwise circumferential direction shown in FIG. 2 on the one end surface of the second ring roller 60 facing the first ring roller 50. The stepped portion 62 and the sixth stepped portion 63 are formed so as to protrude toward the first ring roller 50 at substantially equal intervals in the circumferential direction. Each step portion 61, 62, 63 has a part of a cylindrical shape with a central angle of about 60 degrees, and the first ring roller 50 of the second ring roller 60 is formed by forming each step portion 61, 62, 63. The opposing end face 64 that faces is formed in a concavo-convex shape along the circumferential direction.

  Furthermore, a second convex portion 65 is formed to protrude in the axial direction of the fifth step portion 62 at the substantially central portion in the radial direction on the side surface in the sixth step portion 63 side of the fifth step portion 62. Yes. The protruding tip of the second convex portion 65 is formed as a convex curved surface. A second concave portion 66 having a concave curved surface is formed so as to be recessed in the axial direction of the fourth step portion 61 at the substantially central portion in the radial direction of the side surface in the sixth step portion 63 side of the fourth step portion 61. ing. The second convex portion 65 and the second concave portion 66 are formed at positions that are axially symmetric with respect to the axis of the second ring roller 60.

  The first relative movement mechanism 3 is configured by the first concave portion 56 and the second convex portion 65, and the second relative movement mechanism 4 is configured by the first convex portion 55 and the second concave portion 66. The first relative movement mechanism 3 and the second relative movement mechanism 4 are positions that are axially symmetric with respect to the axis of the first ring roller 50 or the second ring roller 60 and are opposite to the input shaft 20. It is formed in the position which becomes the side.

  Furthermore, as shown in FIGS. 2 to 4, the concave portions 56 and 66 have a predetermined degree of freedom in the rotational direction and the radial direction with respect to the convex portions 55 and 65, and the concave portions 56 and 66 have the convex portions. When the input shaft 20 rotates in the rotational direction with respect to the portions 55 and 65, the convex portions 55 and 65 and the concave portions 56 and 66 are relatively movable in an engaged state. Further, during rotation, the second step portion 52 of the first ring roller 50 has a gap in the circumferential direction in the recess formed in the circumferential direction by the fourth step portion 61 and the fifth step portion 62 of the second ring roller 60. Have and engage. Furthermore, the sixth step portion 63 of the second ring roller 60 has a gap in the circumferential direction in the concave portion formed in the circumferential direction by the first step portion 51 and the third step portion 53 of the first ring roller 50. Engage.

  Further, the first ring roller 50 and the second ring roller 60 are configured such that the step portions 51, 52, 53 of the first ring roller 50 and the step portions 61, 62, 63 of the second ring roller 60 are in the axial direction. Engage so that they partially overlap. At this time, as shown in FIG. 1, a gap s is formed between the opposed end surfaces 54 and 64 facing each other in the axial direction of the first ring roller 50 and the second ring roller 60. Note that the planetary roller traction drive device 101 of the present embodiment functions as a speed reducer that reduces the rotational speed between the input shaft 20 and the output shaft 91 to transmit power.

[Action]
Next, the operation of the planetary roller traction drive device 101 according to the present embodiment will be described. First, when the input shaft 20 rotates in the clockwise direction as viewed from the input shaft 20 side as indicated by an arrow in FIG. 1, the input shaft 20 is rotated through the first sun roller 30 that rotates integrally with the input shaft 20. The rotation roller 70 to which the rotation is transmitted rotates in a state where the revolution around the input shaft 20 is restricted, and rotates the first ring roller 50 in the direction opposite to that of the input shaft 20. Further, planetary rollers 80 are caused by traction generated between the second sun roller 40 integrated with the input shaft 20 and the second ring roller 60 to which the rotation is transmitted from the first ring roller 50 via the first relative movement mechanism 3. Revolves around the input shaft 20 in the same direction as the input shaft 20 while rotating.

  FIG. 3 shows a mode in which the second ring roller 60 is positioned on the upper side in the radial direction relative to the first ring roller 50 as compared with the mode shown in FIG. 4 shows a mode in which the second ring roller 60 is positioned on the lower side in the radial direction relative to the first ring roller 50, as compared with the mode shown in FIG. At the time of rotation, the concave portions 56 and 66 and the convex portions 55 and 65 constituting the relative movement mechanisms 3 and 4 are configured such that the tips of the convex portions 55 and 65 slide with respect to the inner surfaces of the concave portions 56 and 66. The engagement state is maintained by moving to. Each ring roller 50 transmits the rotation between the first ring roller 50 and the second ring roller 60 by the contact between the first concave portion 56 and the second convex portion 65 in the first relative movement mechanism 3. , 60 move relatively on a plane orthogonal to the input shaft 20 within the range shown in FIGS.

  Further, following the relative movement of the ring rollers 50 and 60, the rotation roller 70 and the planetary roller 80 move relative to the housing 10 mainly in the radial direction and the rotation direction. When the input shaft 20 rotates in the counterclockwise reverse direction when viewed from the input shaft 20 side, the engagement between the first convex portion 55 and the second concave portion 66 in the second relative movement mechanism 4 causes the above-described operation. Similarly, the ring rollers 50 and 60 relatively move on a plane orthogonal to the input shaft 20 while transmitting rotation between the first ring roller 50 and the second ring roller 60.

[effect]
For example, if the ring roller circumscribing the rotation roller 70 and the ring roller circumscribing the planetary roller 80 are configured to be immovable with respect to the housing 10 as a common rigid body, the rollers 30, 40, 50, 60 , 70, 80, there is a backlash such as a processing error at the time of manufacture or a deviation of the shaft center at the time of assembling the roller. And on the other hand, there will be variations such as lowering.

  However, in the present embodiment, each of the ring rollers 50 and 60 is suitable by the relative movement mechanisms 3 and 4 on a plane orthogonal to the axial direction of the input shaft 20, that is, mainly in the radial direction and the rotational direction of the ring rollers 50 and 60. Automatically move to the correct position. Further, the autorotation roller 70 and the planetary roller 80 automatically move to suitable positions following the ring rollers 50 and 60. Thereby, each dimension error can be suitably absorbed by the reversing mechanism 1 side and the planetary mechanism 2 side.

  In addition, variations in the pressing force such that the pressing force is increased on one side of each traction contact portion and the pressing force on the other side are reduced, and transmission efficiency is improved without excessively increasing the pressing force and preventing torque transmission. Can be improved. Further, since the wear of the contact portion is reduced, the life of each roller can be extended.

  Further, since the two relative movement mechanisms 3 and 4 are provided at positions which are axially symmetric with respect to the axis of each of the ring rollers 50 and 60, the present invention can be applied to both the forward and reverse rotations of the input shaft 20. Can do. Furthermore, since each convex part 55,65 which comprises the relative movement mechanisms 3 and 4 has a convex curved surface, and each recessed part 56,66 has a concave curved surface engaged with a convex curved surface, each concave part 56,66. Each of the convex portions 55 and 65 can move so as to slide, and the relative movement of the ring rollers 50 and 60 can be made smoother.

  In the present embodiment, step portions having substantially the same shape are formed at equal intervals in the circumferential direction in each of the ring rollers 50 and 60, the balance of weight is uniform in the circumferential direction, and the center of gravity is at the substantially central position. For this reason, the vibration at the time of rotation of each ring roller 50 and 60 can be suppressed. Moreover, since each convex part 55,65 and each concave part 56,66 which comprise the relative movement mechanisms 3 and 4 are formed in the circumferential direction side surface of the step parts 51,53,61,62, it is the structure strong in strength. can do.

  Further, since the gap s is formed between the opposed end surfaces 54 and 64 facing each other in the axial direction of the first ring roller 50 and the second ring roller 60, the first ring roller 50 and the second ring roller 60 are opposed to each other during rotation. Friction generated between the end surfaces 54 and 64 can be eliminated, and wear on the opposed end surfaces 54 and 64 of the ring rollers 50 and 60 can be suppressed. In the present embodiment, the ring rollers 50 and 60 have a tapered shape, and the ring rollers 50 and 60 are biased toward each other by the springs 15 and 16 in order to obtain a suitable pressing force at the contact portion. Therefore, when the gap s is not formed, there is a concern about friction between the opposed end surfaces 54 and 64, but such a problem can be avoided.

Second Embodiment
Next, the planetary roller traction drive device 102 of the second embodiment will be described with reference to FIGS. In addition, about the structure similar to 1st Embodiment, it shows with the same code | symbol and abbreviate | omits description. This embodiment is the same as the first embodiment in that two relative movement mechanisms 5 and 6 are provided at positions that are axially symmetric with respect to the axis of each ring roller 50 and 60. Step portions are not formed on the rollers 50 and 60, and the configurations of the relative movement mechanisms 5 and 6 are different from those of the first embodiment. Hereinafter, parts different from the first embodiment will be described.

  A plurality of (two in the present embodiment) annular projections 57 and 58 on the other end surface of the first ring roller 50 facing the second ring roller 60 are provided on the second ring roller 60 side. It is formed at a position that protrudes and is axially symmetric with respect to the axis. Further, the outer diameters of the annular protrusions 57 and 58 are substantially equal to the thickness of the other end face of the first ring roller 50.

  A plurality of (in the present embodiment, two) pins 67 and 68 on the one end face of the second ring roller 60 facing the first ring roller 50 project toward the first ring roller 50 side. Further, it is formed at a position that is axially symmetric with respect to the axis. The diameters of the pins 67 and 68 are smaller than the inner diameters of the annular protrusions 57 and 58. The annular projections 57 and 58 engage with the pins 67 and 68 in the rotational direction, and the annular projections 57 and 58 have a predetermined degree of freedom in the rotational direction and the radial direction with respect to the pins 67 and 68. When the input shaft 20 rotates, the inner peripheral portions of the annular protrusions 57 and 58 and the outer peripheral portions of the pins 67 and 68 are relatively movable in contact with each other.

  In addition, the inner peripheral part of the annular projections 57 and 58 corresponds to a “concave portion” having a concave curved surface described in the claims, and the pins 67 and 68 have a convex curved surface described in the claims. Corresponds to “projection”. The annular projection 57 and the pin 67 constitute the first relative movement mechanism 5, and the annular projection 58 and the pin 68 constitute the second relative movement mechanism 6.

  Next, the operation of the planetary roller traction drive device 102 according to the present embodiment will be described. FIG. 8 is a sectional view taken along line VIII-VIII in FIG. 7 and shows only the first relative movement mechanism 5. As shown in FIGS. 8A to 8C, when the input shaft 20 rotates, the annular projections 57 and 58 and the pins 67 and 68 keep the engagement in contact with each other. The relative movement to a desired position is possible. That is, each ring roller 50, 60 is connected to the input shaft 20 while transmitting rotation between the first ring roller 50 and the second ring roller 60 by contact between the annular projections 57, 58 and the pins 67, 68. Relative movement is allowed on a plane perpendicular to.

  According to this embodiment, the same effect as that of the first embodiment can be obtained. Furthermore, in this embodiment, since the inner peripheral portions of the annular projections 57 and 58 function as “concave portions” in which the pins 67 and 68 are engaged over 360 degrees, one relative movement mechanism can be used for the input shaft 20. It can correspond to forward rotation and reverse rotation. In addition, by providing two relative movement mechanisms 5 and 6 at positions that are axially symmetric with respect to the axis of each of the ring rollers 50 and 60, it is possible to balance the weight in the circumferential direction of each of the ring rollers 50 and 60. , Can be rotated stably.

<Other embodiments>
In each of the above-described embodiments, the relative movement mechanisms 3, 4, 5 and 6 are constituted by the convex portions 55 and 65 and the concave portions 56 and 66 or the annular projections 57 and 58 and the pins 67 and 68, but as shown in FIG. In addition, springs 17 and 18 as elastic members are provided between opposing end surfaces of the first ring roller 50 and the second ring roller 60, and the first ring roller 50 and the second ring roller 60 are connected to each other by the springs. The moving mechanisms 7 and 8 may be configured.

  The shapes of the convex portions 55 and 65 and the concave portions 56 and 66 of the first embodiment can be changed as appropriate. For example, the convex portions 55 and 65 may be formed in a hemispherical shape, and the concave portions 56 and 66 may be formed in a hemispherical shape corresponding to the shape of the convex portions 55 and 65. In addition, various shapes are possible as long as the convex portion can move so as to slide while maintaining the engaged state with respect to the concave portion.

  In each of the above embodiments, the inner rings of the bearings 12 and 13 are fitted with gaps. Instead of this, for example, a gap may be provided between the outer rings of the bearings 12 and 13 and the housing 10. A radial internal clearance between the bearings 12 and 13 may be used.

  Alternatively, a cylindrical member made of an elastic member such as rubber is provided between the inner rings of the bearings 12 and 13 and the ring rollers 50 and 60, and the rollers 50 and 60 are deformed by elastic deformation of the cylindrical member. It is good also as a structure which accept | permits the relative movement to the radial direction with respect to the housing 10. FIG.

  Further, instead of press-fitting the rotation roller support shaft 71 into the rotation roller 70, the rotation roller 70 can be moved relative to the housing 10 in the radial direction by being inserted with a slight gap. Anyway. Similarly, the planetary roller 80 is inserted into the planetary roller 80 in a radial direction with respect to the housing 10 by inserting the planetary roller support shaft 81 into the planetary roller 80 with a slight gap therebetween. It may be possible to move relative to each other. In addition, each roller 50, 60, 70, 80 may be configured to be slightly movable relative to the housing 10 mainly in the radial direction and the rotational direction on a plane orthogonal to the axial direction of the input shaft 20. Various changes can be made to the configuration.

In each of the above-described embodiments, two relative movement mechanisms 3, 4, 5, and 6 are provided.
In the above embodiments, the sun rollers 30 and 40 that rotate integrally with the input shaft 20 are provided. However, the sun rollers 30 and 40 are not provided, and the planetary roller 80 or the rotation roller 70 is configured to be in direct contact with the input shaft 20. May be.

  In each of the above-described embodiments, each of the rollers 30, 40, 50, 60, 70, and 80 has a tapered shape. However, the outer circumferential surface or the inner circumferential surface shape that does not have a tapered shape and is parallel to the central axis L is used. It may be configured.

In each of the above embodiments, the springs 15 and 16 are provided in parallel to the axial direction between the ring rollers 50 and 60 and the housing 10, but instead of this configuration, the springs are pushed by a spring through a thrust bearing. Alternatively, rubber, hydraulic pressure, or other actuators may be used.
The present invention is not limited to the embodiments described above, and can be implemented in various forms without departing from the spirit of the invention.

3 First relative movement mechanism (relative movement mechanism)
4 Second relative movement mechanism (relative movement mechanism)
10 Housing 20 Input shaft 50 First ring roller (ring roller)
51 1st stage (weight adjustment part)
52 Second Step (Weight Adjuster)
53 3rd stage (weight adjustment part)
54 Opposing end face 55 First convex portion (convex portion)
56 First recess (recess)
60 Second ring roller (ring roller)
61 4th stage (weight adjustment part)
62 5th step (weight adjustment unit)
63 6 steps (weight adjuster)
64 Opposing end face 65 Second convex part (convex part)
66 Second recess (recess)
70 Rotating Roller 80 Planetary Roller 90 Carrier 101 Planetary Roller Traction Drive Device s Clearance

Claims (6)

A housing (10);
An input shaft (20) rotatably supported by the housing;
A first ring roller (50), which is an annular member provided on the radially outer side of the input shaft and provided on one side of the housing, and is rotatably supported by the housing;
A second ring roller that is provided on the radially outer side of the input shaft and is provided in parallel with the first ring roller on the other side of the housing, and is rotatably supported by the housing. 60)
A plurality of rotation rollers (70) which are inscribed in the first ring roller and rotate while being constrained to revolve around the input shaft between the input shaft and the first ring roller when the input shaft rotates;
A plurality of planetary rollers (80) revolving around the input shaft while rotating in contact with the second ring roller;
A carrier (90) provided on the other side of the planetary roller, rotatably supporting the planetary roller and revolving around the input shaft, and outputting a revolution component of the planetary roller to the outside;
One ring while transmitting rotation between the first ring roller and the second ring roller when the first ring roller rotates in a direction opposite to the rotation direction of the input shaft by rotation of the rotation roller. A relative movement mechanism (3, 4, 5, 6) that allows the roller to move relative to the other ring roller on a plane orthogonal to the axial direction of the input shaft;
A planetary roller traction drive device (101, 102) comprising: The relative movement mechanism is
Convex portions (55, 65) provided on one of the first ring roller and the second ring roller;
Concave portions (56, 66) provided on the other ring roller not formed with the convex portions and engageable with the convex portions;
When the input shaft rotates, the convex portion and the concave portion are relatively movable in a state of being engaged in a rotation direction of the first ring roller. Item 4. The planetary roller traction drive device according to Item 1. There are two relative movement mechanisms,
3. The planet according to claim 1, wherein the first relative movement mechanism is provided at a position opposite to the second relative movement mechanism with respect to the input shaft. Roller traction drive device.   The planetary roller according to claim 2 or 3, wherein the convex portion is formed with a convex curved surface, and the concave portion is formed with a concave curved surface that engages with the convex curved surface. Traction drive device.   The first ring roller and the second ring roller include weight adjusting portions (51, 52, 53, 61, 62, and the like) for adjusting a circumferential weight deviation due to the formation of the convex portion or the concave portion. 63) The planetary roller type traction drive device according to any one of claims 2 to 4, wherein the planetary roller type traction drive device is provided.   The said 1st ring roller and the said 2nd ring roller form the clearance gap (s) between the opposing end surfaces (54, 64) which oppose in an axial direction, The 1st-Claim 5 characterized by the above-mentioned. The planetary roller traction drive device according to any one of the above.

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